Primer on Flat Rolling Primer on Flat Rolling Second Edition
John G. Lenard
Department of Mechanical and Mechatronics Engineering University of Waterloo Waterloo, Ontario, Canada
AMSTERDAM • BOSTON • HEIDELBERG • LONDON • NEW YORK • OXFORD PARIS • SAN DIEGO • SAN FRANCISCO • SINGAPORE • SYDNEY • TOKYO Elsevier The Boulevard, Langford Lane, Kidlington, Oxford, OX5 1GB, UK 225 Wyman Street, Waltham, MA 02451, USA First edition 2007 Second edition 2014 Copyright © 2014, 2007 Elsevier Ltd. All rights reserved No part of this publication may be reproduced or transmitted in any form or by any means, electronic or mechanical, including photocopying, recording, or any information storage and retrieval system, without permission in writing from the publisher. Details on how to seek permission, further information about the Publisher’s permissions policies and our arrangement with organizations such as the Copyright Clearance Center and the Copyright Licensing Agency, can be found at our website: www.elsevier.com/permissions. This book and the individual contributions contained in it are protected under copyright by the Publisher (other than as may be noted herein). Notices Knowledge and best practice in this field are constantly changing. As new research and experience broaden our understanding, changes in research methods, professional practices, or medical treatment may become necessary. Practitioners and researchers must always rely on their own experience and knowledge in evaluating and using any information, methods, compounds, or experiments described herein. In using such information or methods they should be mindful of their own safety and the safety of others, including parties for whom they have a professional responsibility. To the fullest extent of the law, neither the Publisher nor the authors, contributors, or editors, assume any liability for any injury and/or damage to persons or property as a matter of products liability, negligence or otherwise, or from any use or operation of any methods, products, instructions, or ideas contained in the material herein. British Library Cataloguing-in-Publication Data A catalogue record for this book is available from the British Library Library of Congress Cataloging-in-Publication Data A catalog record for this book is available from the Library of Congress ISBN: 978-0-08-099418-5
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For Elisa-Chaya, whose smile makes my day Preface to the Second Edition
In the first edition of this book, I wrote that the process of flat rolling has not changed for centuries, not since Leonardo da Vinci rolled soft metals on his hand-driven mill. While the process hasn’t changed in the last few years, either, there have been numerous, important innovations. The first edition was intended to present the basic ideas of flat rolling and that objective also has not changed in the second edition. Several chapters have been added, however, expanding on the fundamental concepts. In Chapter 1, various rolling processes À not only flat rolling, exclusively À have been described. In a new Chapter 2, Don Adair, the manager of Flat Rolling Operations at Quad Engineering of Toronto and Edwin B. Intong, former technical manager for Electrical & Automation, US Steel Engineers and Consultants, present a history of the development of different generations of hot strip mills. The changes are highlighted and their importance is pointed out. In an interesting section, the innovations, introduced in recent times, are listed. Another new addition, Chapter 3, prepared by Dr J.B. Tiley, hot rolling consultant, discusses current trends of roll design, focusing on the development of new materials for work rolls and back-up rolls with the objectives of reducing roll wear and enhancing roll life. Chapter 4, unchanged, describes the basic ideas of flat rolling. Chapter 5 deals with mathematical modelling of the process. Section 3.8 in the first edition, dealing with Neural Networks, has been removed. While the use of neural networks created some excitement some years ago, this didn’t continue, as engineers prefer to use statistical methods for control and predictions. Chapter 6, Advanced Finite Element Modelling is new. It is the result of the cooperative research of Dr G. Krallics, Z. Be´zi, M. Szucs˝ of the University of Miskolc, Miskolc, Hungary and the present author. It is acknowledged that finite element modelling of flat rolling has often been dealt with in the literature. Details of some of these models are given and a new model that accounts for all three components of the flat rolling system À the roll, the rolled strip and its interface À is introduced. Its predictive ability is pre- sented by comparing its computations to experimental results. Chapter 7, Simulation and Reduction of Local Buckles in Cold Rolling, goes somewhat beyond the basics. It was prepared by Dr Yuli Liu, chief process engineer, manager of Process Engineering and Development of Quad Engineering Inc. An advanced mathematical model, consisting of several modules, is given in some detail. The chapter is of some importance as it deals with problems of shape and dimensional inaccuracies in the rolling process. However, using the model is neither easy nor immediate. A potential user must refer to the original publications. xii Preface to the Second Edition
Chapter 8 is unchanged. A new section, Nanotribology, is now included in Chapter 9, Tribology. The topic is briefly described. Chapter 10 is unchanged, as well. Most of the first edition dealt with steels. In the second edition, a presentation of hot rolling of aluminium alloys (Chapter 11) broadens the scope of the book. This portion has been prepared by Dr Mary Wells of the University of Waterloo. The rest of the first edition is repeated. None of Chapters 12À15 has been changed. A well-acknowledged chapter in the first edition presented problems and their solutions; this chapter has been repeated unchanged.
Advice for Instructors
There are several topics mentioned in this book, the thorough understanding of which needs a broad and varied background. The instructor should be aware of the prepara- tion of the audience and make sure that the following subjects are understood well before starting on the presentations of the book’s contents. A brief quiz during the first lecture and the discussion of the results are often helpful in finding out what needs to be reviewed. In the present writer’s experience with rolling mill engineers, this background may have been there in the listeners’ college or university days but if such knowledge has not been used daily for some considerable time, gaps are certain to exist. It is strongly recommended that at least the first six lectures be devoted to a review of the following. The ideas involved with the strength of materials should be mastered first. These include the theory of elasticity and the analysis of stress and strain; the idea of equilibrium, static and dynamic. Principal directions, principal stresses and strains also need to be appreciated. Boundary conditions, surface and body forces should be clarified and it may be helpful to assign, and then discuss in class, some esoteric examples such as the free-body diagram of a tooth while it is being extracted or the forces and torques acting on a rail car wheel in motion. Identifying and sketching the loads on a bullet in flight would also pose a challenge. If these are well understood, their application during the course should become easy. The difference between engineering and true stresses and strains should be made clear. Strain rates and the conditions under which they remain constant in a test need to be mentioned. The theory of plasticity is used throughout the book without developing the basic ideas. ElasticÀplastic boundaries, the yield and the flow criteria, the associated flow rules, the constancy of volume and the compatibility equations should be presented as part of the review. The stress and strain tensors should be mentioned in addition to the tensor invariants. Basic ideas from the field of metallurgy are needed. The grain structure of metals, the carbon equilibrium diagram, the hardening and restoration mechanisms and the hot and cold response of metals to loading are all used in many of the developments in the course. It would be helpful for the students to have actually mounted, polished and etched a piece of metal for metallographical examination. Preface to the Second Edition xiii
Some time should be devoted to a discussion of Tribology as well. Viscosity, Reynold’s equation, lubricant and emulsion chemistry are all necessary here. As a last comment to the instructors, nothing replaces the actual hands-on exper- imentation. Having a well-instrumented rolling mill and conducting some carefully designed experiments would lead to immeasurable benefits. Some care needs to be exercised in assigning the problems from Chapter 11. Many of them are fairly straightforward and require the application of the ideas presented in the text. Many of them, however, require extensive reading and may well lead to some frustration. A discussion of the solution in class is often highly appreciated. Seminars or class discussions are suggested when dealing with Chapters 7À10. These may require advance preparation so the discussions would not become pro- fessorial presentations. State-of-the-art reviews have been found helpful. John G. Lenard, 2013 Preface to the First Edition
I have been dealing with problems of the flat rolling process for the last 30 years. This included mathematical modelling, experimentation, consulting, publishing in technical journals and presenting my research at conferences and in industry, as well as lecturing on the topic at levels, appropriate for second- and third-year undergraduate students, graduate students and practicing engineers and technolo- gists of aluminium and steel companies. The present book is a compilation of my experience, prepared for use by practitioners who work with metal rolling and who want to know about the “whys”, the “whats” and the interdependence of the mate- rial and process parameters of the rolling process. The book may also be useful for graduate students researching flat rolling. My interest in the process began while I spent a year at Stelco Research as an NSERC Senior Industrial Fellow, shortly after starting my academic career. I became aware of the tremendous complexity underlying the seemingly very simple process of metal rolling. I realized that while the process of flat rolling À that of two cylin- ders rotating in opposite directions and reducing the thickness of a strip as it passes in between them À has not changed for centuries, its current sophistication places it at the top of the “high-tech” activities. On return to academia and as soon as research funds allowed, I designed and built a simple two-high experimental rolling mill and instrumented it to measure the important variables. The mill has been in use ever since to roll various metals À mostly aluminium and steel alloys À under a large variety of conditions. These conditions included dry and lubricated passes, use of neat oils and emulsions, high, low and intermediate temperatures, heated and non- heated rolls and speeds and reductions as high and low as the mill allowed. During these experiments my students and I used smooth and rough roll surfaces, prepared by grinding or sand blasting. In each of the tests the roll separating forces, the roll torques, the entry and exit thickness, the rolling speed, the forward slip, the entry and exit temperatures of the strip, the roll’s surface temperature, the amount of the lubricant, the flow rate and the temperature of the emulsion, the droplet size in the emulsion, the change of the width and the reduction of the strips were measured. In addition to the experiments performed by myself, by academic visitors from China, Egypt, Germany, Hungary, India, Israel, Japan, Poland and South Korea, and by my graduate students, twice each year my undergraduate classes, typically 80À100 students strong, performed flat rolling tests, providing me with a very respectable collection of data. xvi Preface to the First Edition
Mathematical modelling of the process proceeded parallel to the experimental studies. The attention was on establishing the predictive abilities of the available models of the flat rolling process. The assumptions made in the derivation of the traditional 1D models were critically examined and were improved on by developing an advanced 1D model which makes use of as few arbitrary assumptions as possible. The use of finite-element models was also explored in cooperation with Prof. Pietrzyk (University of Mining and Metallurgy, Krakow, Poland) and his colleagues and students. During my academic career I offered, once or twice a year, a specialist course on rolling, designed for technologists and engineers who work in the metal rolling industry. The educational level of the audience varied broadly from those who had completed high school to those with doctoral degrees. Each year I found two unchanging phenomena. The first was the shaky background my listeners pos- sessed, essentially regardless of their education. When asked about the difference between engineering strains and true strains, the difference between the plane- stress and plane-strain conditions, the difference between static and dynamic recrystallization and so on, the large majority of them betrayed serious ignorance. The second was the lack of a textbook that included all I needed to develop the ideas in the course. The present book, resulting from the notes I used in these courses, attempts to compile, present and explain the disparate components needed for a clear understanding of the topic. The book contains 11 chapters. The first 10 of these deal with various aspects of the flat rolling process and the 11th presents a set of assignments and incomplete solutions, formulated to test the understanding of the reader of the material presented. Each chapter ends with a set of conclusions. The flat rolling process is defined in Chapter 1, the Introduction. The objectives are to give a very brief overview of the process. Details of the hot rolling process, using hot strip mills, are given. Continuous casting is described. The cold rolling process and cold mill configurations are presented next. A general discussion of the rolling process is presented in Chapter 2. The compo- nents of a metal rolling system are defined. Reference is made to the rolling mill, designed by Leonardo da Vinci, and the scale model, built following his drawings. A description of the physical and metallurgical events during the process is given, including the events as the strip to be rolled is ready to enter the roll gap, as it is partially reduced and as the process becomes one of steady state. The independent variables of the system À the mill, the rolled metal and their interface À are listed. The minimum value of the coefficient of friction, necessary to commence the rolling process, is given. Some of the simplifying assumptions that are usually made in mathematical models of the process of flat rolling are critically discussed: these include the idea of “plane-strain plastic flow” and “homogeneous compression of the strip”. Microstructures of a fully recrystallized Nb steel, an AISI 1008 steel and a cold-rolled low carbon steel are presented. Mathematical modelling of the rolling process is the topic of Chapter 3. Traditional and more advanced models are discussed in terms of their capabilities as far as their predictions are concerned. Models for both mechanical and metallurgical Preface to the First Edition xvii events are included. The chapter ends with the identification of three parameters necessary for efficient, accurate and consistent modelling: the coefficients of heat transfer and friction and the resistance of the material to deformation. Chapters 4 and 5 treat these in turn: material behaviour and tribology, respectively. In both, the emphasis is on how the concepts are to be used when combined with the models, presented in the previous chapter. The objectives in preparing Chapter 6 are somewhat different. The chapter is entitled “Sensitivity Studies” and in spite of some examination of the sensitivity of the predictions in previous chapters, some more calculations and applications are added. Temper rolling is considered in Chapter 7. The differences between the usual flat rolling process and temper rolling are pointed out. Several mathematical models are given and the assumptions made in their development are discussed. The components that should make up a complete model of the process are listed. The tenor of the book changes at that point. In each of Chapters 8, 9 and 10 À accumulative roll bonding, flexible rolling and cold roll bonding, respectively À a review of the literature is followed by the detailed descriptions of experimental work. Chapter 11 contains two sections. In the first, problems are listed for each of the chapters. Some of these require the direct application of the expressions and the for- mulas presented in the book. Some answers require Internet searches. Some require development of computer programs. Some are suggested topics for seminars or class discussions. In the second part the solutions are given. Again, this is done in a variety of ways: in some cases detailed solutions are given, while in some others only the numerical answers are indicated. As well, in some instances, only a set of hints and recommended approaches are suggested. I would like to acknowledge the contributions of my undergraduate and graduate students without whom my research would not have progressed. Also, I would like to thank the visiting scientists with whom cooperation was always most enjoyable. This book couldn’t have been produced without the active encouragement of my wife Harriet and my daughter Patti. I am deeply grateful for their continuing support. John G. Lenard, 2007 Contributors
G Krallics University of Miskolc, Institute for Materials Science, Hungary
Edwin B. Intong Former Technical Manager for Electrical & Automation, US Steel Engineers and Consultants
Yuli Liu Manager, Process Engineering and Development, Quad Engineering Inc., Toronto, Ontario, Canada
John Tiley Hot Rolling Consultant
Donald Richard Adair Flat Rolling Manager, Quad Engineering Inc, Toronto, Ontario, Canada
M. Wells Department of Mechanical and Mechatronics Engineering, University of Waterloo, Waterloo, Ontario, Canada Acknowledgements
The cooperation by Prof. Wells, Dr. Krallics, Dr. Liu, Dr. Tiley, Mr. Adair and Mr. Intong is greatly appreciated. 1 Introduction
1.1 The Flat Rolling Process
The mechanical objective of the flat rolling process is simple. It is to reduce the thickness of the work piece from the initial thickness to a pre-determined final thickness. This is accomplished on a rolling mill, in which two work rolls, rotating in opposite directions, draw the strip or plate to be rolled into the roll gap and force it through to the exit, causing the required reduction of the thickness. As these events progress, the material’s mechanical attributes change. These in turn cause changes to the metallurgical attributes of the metal, which, arguably are of more importance as far as the product is concerned. A schematic, three-dimensional dia- gram of the back-up rolls and the work rolls is shown in Figure 1.1 where a single- stand, four-high mill is depicted; this may be a single-stand roughing mill. Figure 1.1 shows the back-up rolls, the much smaller work rolls, the strip being rolled and the roll separating forces acting on the journals of the back-up roll bear- ings, keeping the centre-to-centre distance of the bearings as constant as possible1. As will be demonstrated in Chapter 10, the energy requirements of the process may be decreased when small diameter work rolls are used. The drawback of that step is the reduced strength of the work roll which necessitates the use of the massive back-up rolls to minimize the deflections of the work roll.
1.1.1 Hot, Cold and Warm Rolling While the rolling process may be performed at temperatures above half of the melt- ing point of the metal, termed hot rolling, or below that temperature, in which case one deals with cold rolling, the division into these two categories should not be considered as being cast in stone. There is a temperature range, beginning below and ending above the dividing line between hot and cold rolling, within which the process is termed warm rolling and in some specific instances and for some materi- als this is the preferred process to follow. These processes lead to mechanical and metallurgical changes of the attributes of the work piece, which are not possible to achieve in either the cold or the hot flat rolling regimes.
1Mill stretch will be discussed in Chapter 5.
Primer on Flat Rolling. DOI: http://dx.doi.org/10.1016/B978-0-08-099418-5.00001-9 © 2014 Elsevier Ltd. All rights reserved. 2 Primer on Flat Rolling
1.2 The Hot Rolling Process
Hot rolling of metals is usually carried out in an integrated steel mill, on a “Hot Strip Mill”, or since some changes were introduced in the last couple of decades, on mini-mills2. Both have advantages and disadvantages, of course, such as capital costs, flexibility, quality of the product and danger to the environment. A schematic diagram of a traditional hot strip mill is depicted in Figure 1.2, showing the major components. There are several basic components in the traditional hot strip rolling mill. In what follows, these are discussed briefly3.
Roll force
Back-up roll Work roll
Work piece
Figure 1.1 A schematic diagram of a single-stand, four-high set of rolls.
Edge rollers Pyrometers Descaler
Reheating Transfer Runout table furnaces table Finishing mill and Coilers Roughing Flying Cooling banks shear mill X-ray
Figure 1.2 The schematic diagram of a traditional hot strip mill.
2See Section 1.4 for a brief discussion of mini-mills. Also, see Section 2.8 for a discussion of compact strip production. 3See Chapter 2 where the development of various configurations of hot strip mills is described. Introduction 3
1.2.1 Reheating Furnace The reheating furnace constitutes the first stop of the slab after its delivery from the slab yard. The slab is heated up to 1200À1250C in the furnace to remove the cast dendrite structures and dissolve most of the alloying elements. The deci- sions to be made in running the reheat furnace in an optimal fashion concern the temperature and the environment within. If the temperature is higher than necessary, more chemical components will enter into solid solution but the costs associated with the operation become very high and the thickness of the layer of the primary scale will grow. If the temperature is too low, not all alloying ele- ments will enter into solid solution, affecting the metallurgical development of the product, and the likelihood of hard precipitates remaining in the metal increases. As well, thinner layers of scale will form, a fairly significant advan- tage. A judicial compromise is necessary here and is usually based on financial consideration. The cost savings associated with a one-degree reduction of the temperature within the furnace can be calculated without too many difficulties; the changes to the formation of solid solutions may be estimated but the annual savings may well be significant. Primary scales of several millimetres thickness form on the slab’s surface in the reheat furnace. The thickness of the scale may be reduced by providing a protective environment within the furnace, albeit at some increased cost. As the furnace doors open and the hot slab slides down on the skids to the con- veyor table, the instant chilling, caused by the water-cooled skids, causes marks that are often noticeable on the finished product. As well, fast cooling of the surfaces and especially of the edges is also immediately noticeable, indi- cating a non-uniform distribution of the temperature within the slab and lead- ing to possibly non-homogeneous dimensional, mechanical and metallurgical attributes.
1.2.2 Rough Rolling Before the rolling process begins, the scale is removed by a high-pressure water spray and/or scale breakers. The slab is then rolled in the roughing stands in which the thickness of the slab is reduced from approximately 200À300 mm to about 50 mm in several passes, typically four or five. The speeds in the rougher vary from about 1 m/s to about 5 m/s. In the roughing process the width increases in each pass and is controlled by vertical edge rollers. The vertical edgers compress and deform the slab somewhat, causing some thickening which is corrected in the subsequent passes. A large variety of roughing mill configurations is possible, from single-stand reversing mills to multi-stand, one-directional mills, referred to as roughing trains. These usually have a scale breaker as the first stand where the mill deforms the slab sufficiently just to loosen the scale, which is then removed by the high-pressure water jets. Roughing scale breakers are usually vertical edgers, capa- ble of reducing the width of the slab by up to 5À10 cm and causing stresses at the steel surface-scale layer interface which then separate the scales. Roll diameters are 4 Primer on Flat Rolling near 1000 mm. The rolls are usually made of cast steel or tool steel4. Roughing stands are either of the two- or four-high configurations. At the end of the rough rolling process, the strip is sent to the finishing mill along the transfer table where it is referred to as the “transfer bar”. The temperature of the slab in the roughing stands is high enough so that the transfer bar is fully recrystallized, containing strain free, equiaxed grains. In general, though, the grain structure at the end of the rough rolling process seems to have little influence on the structure by the time the strip has passed through several stands of the finishing mill.
1.2.3 Coil Box Not shown in Figure 1.2 is a device À an invention by the Steel Company of Canada and first installed in the early 1970s in Stelco’s Hilton Works À called the coil box5, placed between the roughing mill and the finishing train, in place of the transfer table. Since that time, several integrated steel companies have installed the coil box in their hot strip mills. A photograph of the coil box is shown in Figure 1.3. When the words “Coil Box” are entered into Google6, a plethora of information is found, including the possibility of watching a video of the coil box in motion. A detailed description of the events when the steel arrives to the coil box and when it is within the coil box are also available on-line. The transfer bars, exiting from the roughing stand are formed into coils at the coil box, a patented design of the Steel Company of Canada. The coil box consists of two entry rolls, three bending rolls, a forming roll, two sets of cradle rolls, coil stabilizers, peeler, transfer arm and pinch rolls. The adoption of a coil box configu- ration has several advantages:
G it reduces the overall length of the mill line; G it increases the productivity; G it enlarges the strip width and the length to be rolled and G it eliminates the thermal rundown along the strip length when compared to the conven- tional HSM. Thus, uniform temperature and constant rolling speed conditions are maintained. On uncoiling from the coil box, the transfer bars are end-cut, processed through high-pressure descaling sprays, and then they are ready to enter the finishing stands. With the introduction of advanced high-strength steels such as Hot Roll Dual Phase steels7, the benefits of the coil box are even more significant in provid- ing uniform mechanical properties throughout the length of the coil8.
4See Chapter 3 for a description of roll materials. 5See Chapter 2 for a description of the coil box. 6It is acknowledged that the contents of websites on the Internet are changed and updated regularly. 7To be discussed in Chapter 8. 8The first coil box was installed in the Hilton Works shortly before the writer spent a year as a Senior Industrial Fellow at the Research Department of the Steel Company of Canada. At that time the infor- mation concerning the coil box was proprietary and so carefully guarded that no permission was obtained to read any of the reports written on the performance or the analysis of the equipment. Introduction 5
Figure 1.3 The coil box. Source: Courtesy The Steel Company of Canada.
1.2.4 Finish Rolling When the transfer bar, now coiled up in the coil box, reaches the appropriate tem- perature, it is uncoiled and is ready to enter the last several stands of the strip mill, the finishing train. The crop shear prepares the leading edge for entry and the trans- fer bar enters the first stand, assisted by edge rollers. Its velocity is in the range of 2.5À5 m/s9. The finishing train in the strip mill is traditionally composed of five to seven tandem stands. The roll configuration is usually four-high, employing large diameter back-up rolls and smaller diameter work rolls. The entry of the strip into the first stand is carefully controlled and is initiated when the temperature is deemed appropriate, according to the draft schedule, which is prepared using sophisticated off-line mathematical models. These determine the reductions and the speeds at each mill stand as well as predicting the resulting mechanical and metal- lurgical attributes of the finished product. After entry into the first stand, the strip is continuously rolled in the finishing mill. At the entry to the finishing mill, the temperature of the strip is measured and at the exit, both temperature and thickness are measured; the thickness at the exit from each intermediate stand is estimated
9When the present author was working in the Research Department of the Steel Company of Canada, some consideration was given to increasing the entry speed of the transfer bar into the first stand of the finishing mill. The project was abandoned when the possibility of the steel becoming airborne was realized. 6 Primer on Flat Rolling using mass conservation10. In some modern mills there are several optical pyrom- eters placed along the finishing train. The Automatic Gauge Control (AGC) system uses the feedback signals from several transducers to control the exit thickness of the strip. The finishing temperature may also be controlled by changing the rolling speed. However, only small variations of the rolling speed are possible without causing tearing, if the speed of the subsequent mill stand is too high, or buckling, referred to as “cobble” of the strip11, when the speed there is too low. On some newer and more modern strip mills, interstand cooling and/or heating devices have been installed, which minimize the temperature variation across the rolled strip and thereby increase the homogeneity and the quality of the product. As the thickness is reduced the speed must increase, as demanded by mass conservation, and the speeds in the last stand may be as high as 10À20 m/s. The rolls of the finishing mill are cooled by water jets strategically placed around the rolls. Without cooling, the surface temperature of the work rolls would rise to unacceptable levels. It has been estimated that when in contact with the hot strip, the roll surface temperatures could rise to as high as 500C at a very fast rate. Of course, the roll surface would cool during its journey as it is turning around and is subjected to water cooling, but the thermal fatigue it experiences accelerates roll wear and is, in fact, one of the major contributors to it. It is possible to measure roll surface temperatures by ther- mocouples embedded in the roll, with their tips positioned close to the surface12. A mathematical model would then be necessary to extrapolate the temperatures to the surface. There are usually scale breakers before the first stand of the finishing train, consisting of one or two sets of pinch rolls, exerting only enough pressure on the strip to break off the scale. The strip exits from the finishing train at a thickness of 1À4 mm. The Hylsa steel mill in Monterrey, Mexico produces hot rolled strip of 0.91 mm thickness. Bobig and Stella (2004) describe the semi-endless rolling and ferritic rolling processes. These, introduced in the thin slab rolling plant EZZ Flat Steel in Egypt, produce 0.8 mm-thick coils. The ferritic rolling leads to reduced scale growth and lower roll wear. During the last decade the materials used for the rolls on the hot strip mill were changed from chill cast to tool steels, reducing roll wear in a most significant manner13. There have also been reports of significant changes of the coefficient of friction in the roll gap after the switch of roll materials. Tool steels rolls, once implemented correctly, do provide benefits that offset their higher costs. The impact of lubricant interactions with these new roll chemistries has not been fully explored (Nelson, 2006).
10The lack of pyrometers along the finishing train often causes difficulties when the events at the mill stands are modelled. 11See Chapter 7 for a mathematical model, simulating the formation of buckles. 12This would not, of course, be permitted in a production mill. Results on the rise of the surface tempera- ture of the roll, obtained using eight thermocouples embedded in the work roll of a laboratory mill, are presented in Chapter 9. 13Roll wear will be discussed in Chapter 3 and in Chapter 9. Roll materials are described in Chapter 3. Introduction 7
1.2.5 Cooling After exiting the finishing mill, the strip, at a temperature of 800À900C, is cooled further under controlled conditions by a water curtain on the run-out table. The run-out table may be as long as 150À200 m. Cooling water is sprayed on the top of the steel at a flow rate of 20,000À50,000 gpm; and on the bottom surface at 5000À20,000 gpm (1 gpm 5 4.55 l/min). The purpose of cooling is, of course, to reduce the temperature for coiling and transportation, but also to allow faster cool- ing of the finished product, resulting in higher strength. The cooling process plays a major role in the thermalÀmechanical schedule, designed to affect the micro- structure of the product.
1.2.6 Coiling At the exit of the run-out table, the temperature of the strip is measured and the strip is coiled by the coiler. After further cooling, the steel coils are ready for shipping.
1.2.7 The Hot Strip Mill A photograph of a hot strip mill of Dofasco Inc. is shown in Figure 1.4. A pair of work rolls is visible, stored in the foreground of the figure and ready to be placed in the stands14.
1.3 Continuous Casting
Irwing (1993) describes the history of the development of continuous casting and identifies Mannesmann AG, where a production plant went into operation in 1950. A continuous casting plant was installed at Barrow Steel in Great Britain in 1951. The essential idea of the process is simple: molten steel is poured into a water- cooled, oscillating mould. The cooled copper wall of the mould solidifies the outer layer of the steel and as the steel is moving vertically downward, the solidified skin thickens. As the steel leaves the mould, it is cooled further by water sprays. The solidifying steel is supported by rollers, which prevent outward bulging. The continuous casting process replaced the ingot casting several decades ago and succeeded in increasing productivity. The complete continuous casting process is shown in Figure 1.5. The figure shows the ladle into which the molten steel is poured. From the ladle the steel is metered into the tundish and from there it enters the water-cooled, oscillating mould. As the steel strand exits the mould, it is solidi- fying further; an indication of the solidification front is also shown in Figure 1.5.
14The rolls are changed at regular intervals in the hot strip mill. The change takes place very fast, such that the mill need not be shut down. 8 Primer on Flat Rolling
Figure 1.4 The seven-stand finishing mill of Dofasco Inc. Source: Courtesy Dofasco Inc.
Using the withdrawal rolls and the bending rolls, the now solid but still very hot strand is straightened and cut to pre-determined sizes by the cut-off torch. There are two possible subsequent activities at this point. The slabs may be allowed to cool and are then stored in the slab yard, retrieved as needed by custo- mers and reheated in the reheat furnaces and rolled, in the hot strip mill, as depicted in Figure 1.3. Alternatively, they may be rolled directly, as shown in Figure 1.6.
1.4 Mini-Mills (See Also Chapter 2)
The American Iron and Steel Institute’s website gives the following definition for mini-mills:
Normally defined as steel mills that melt scrap metal to produce commodity pro- ducts. Although the mini-mills are subject to the same steel processing require- ments after the caster as the integrated steel companies, they differ greatly in regard to their minimum efficient size, labour relations, product markets, and man- agement style. Introduction 9
Ladle
Molten steel Tundish Mold flux Submerged entry nozzle Water-cooled mold Molten steel Solidified steel Guide rolls Water spray
Cooling chamber
Withdrawal rolls
Bending rolls Slab straightening rolls Cutoff torch Continuous slab Slab
Figure 1.5 Continuous slab casting. Source: Groover (2002); reproduced with permission.
Entry from
the caster Tunnel Descaler Five-stand hot mill Spray zone Fine zone Trim zone Coiler
Figure 1.6 Continuous casting and direct rolling. Source: Following Pleschiutschnigg et al. (2004).
Currently in the United States 52% of the steel is rolled by 20 integrated steel mills and 48% by more than 100 mini-mills. The integrated mills roll approxi- mately 400 tons/h while the mini-mills are capable of 100 tons/h. Information is also available from Wikipedia, a web-based encyclopaedia. It identifies mini-mills as secondary steel producers. Also, it mentions NUCOR as one of the world’s largest steel producers, which uses mini-mills exclusively. A very impressive number (79%) of mini-mill customers expressed satisfaction with their suppliers15.
152001 Customer Satisfaction Report, Jacobson & Associates. 10 Primer on Flat Rolling
The website www.environmentaldefense.org gives information regarding the recycling activities of mini-mills, stating that they conserve 1.25 tons of iron ore, 0.5 tons of coal and 40 lbs of limestone for every ton of steel recycled.
1.5 The Cold Rolling Process
The layers of scales are removed from the surfaces of the strips by pickling, usually in hydrochloric acid. This is followed by further reduction of the thickness, pro- duced by cold rolling. Essentially there are three major objectives in this step: to reduce the thickness further, to increase the rolled metals’ strength by strain hard- ening and to improve the dimensional consistency of the product. An additional objective may be to remove the yield point extension by temper rolling, in which a small reduction, typically 0.5À5%, only is used16.
1.5.1 Cold Rolling Mill Configurations A large variation of configurations is possible in this process. An example of a modern cold rolling mill, for aluminium, is shown in Figure 1.7. The mill is six- high, having two small diameter work rolls of 470 mm diameter and two sets of back-up rolls. The diameter of the intermediate back-up roll is 510 mm and the third back-up roll is of 1300 mm diameter. The mill is capable of producing strips of 0.08 mm thickness at speeds up to 1800 m/min. Mill types, design details and configurations are so numerous that it is impossi- ble to list them all in a brief set of notes. Mill frames, bearings and chucks, screw- down arrangements, loopers, control systems, number of stands, drive systems, spindles, lubricant or emulsion delivery, roll cooling, roll bending devices, shears and coilers may have practically infinite variations in design. Roll materials may also vary, and as recent literature indicates, the chill cast or high chrome rolls are being replaced by tool steel rolls. In what follows, only a set of figures indicating various roll arrangements is presented. Figure 1.8 shows the simplest two-high version in which two work rolls of fairly large diameters are used. The simplicity À low number of components À is out- weighed by the disadvantage of the need for massive rolls to minimize roll bending. A more advanced and significantly more rigid arrangement is the six-high configuration, in which the bending of the work rolls is reduced substantially by the large back-up rolls. Also, advantage is taken of the lower energy requirements, needed when the work rolls are of smaller diameters. The accuracy and consistency of the strip dimensions increase as the number of back-up rolls increases, resulting in a significant reduction of the deflections of the small work-rolls. The stiffness of the complete rolling mill also increases. Figure 1.9 shows a photograph of a
16Temper rolling is discussed in Chapter 12. Introduction 11
Figure 1.7 A schematic diagram of a modern cold rolling mill for aluminium (Hishikawa et al., 1990).
Two - high mill Six-high mill
Figure 1.8 A two- and a six-high mill. 12 Primer on Flat Rolling
Figure 1.9 A 20-high mill, for rolling copper and copper alloys, built by SUNDWIG GmbH.
20-high mill, built by SUNDWIG GmbH. The progressively increasing roll dia- meters, starting with the very small work rolls, are clearly observable. Bill and Scriven (1979) describe the details of the Sendzimir mill À which is used for both hot and cold rolling À and show various designs and configura- tions. They describe the advantages and the disadvantages of using small diame- ter work rolls, and the history of how engineers attempted to overcome this problem. Tadeusz Sendzimir, a Polish engineer and inventor, designed the clus- ter mill, which, named after him, was built as an experimental rolling mill in 1931 in Du¨sseldorf, Germany. In one of the designs, a type 1-2-3-4 arrangement shown in Figure 1.10, similar to the 20-high mill, illustrated above, the work rolls are driven through friction contact. This mill, and the other versions of it, are capable of producing very high reduction in one pass and can roll a strip to very low thickness. Backofen (1972) writes that the work roll may well have a diameter under 1v (25.4 mm) and the exit thickness may be as low as one- thousandth of an inch (0.025 mm). Further, since the small work rolls flatten less, they can continue to roll metal even after significant strain hardening with no need for intermediate annealing. The work rolls are often made of tungsten carbide, resulting in much longer roll life and producing a mirror finish on the rolled surfaces. The ridges, sometimes created by the small work rolls, are smoothed by subse- quent operations. The Platzer planetary mill, shown in Figure 1.11, is also capable of very high reductions. In some of the versions, the mill has two back-up beams which are sta- tionary. Around these are the intermediate and the work rolls. Feed rolls force the strip into the roll gap. The work roll diameters range from a low of 75 to 225 mm, Introduction 13
Figure 1.10 Sendzimir mill (Bill and Scriven, 1978).
depending on the width, much larger than in the Sendzimir mill of Figure 1.10. Fink and Buch (1979) indicate that 98% reductions are achievable on the Platzer mill, in one pass. It is interesting to note that the small work rolls rotate in a direc- tion opposite the rolling direction. The number of roll contacts may be as high as 40À60 s21.
1.6 The Warm Rolling Process
The temperature range for this process is not defined very closely; it starts some- what below half of the homologous temperature17 and ends somewhat above that. In the process both the strain and the rate of strain affect the mechanical and metal- lurgical attributes of the rolled metal and in process design these need to be accounted for carefully. The energy requirements are, of course, higher than those for hot rolling but lower than for cold rolling. The strength of the resulting product is higher than what can be achieved by hot rolling. While there is an accumulation of scales of the surfaces, the amount is significantly less than in the hot rolling pro- cess. The ferrite rolling, mentioned above, may be considered a warm rolling process, although this suggestion may be somewhat controversial.
17The homologous temperature range is defined such that one of the end points is absolute zero while the other is the melting temperature of the particular metal. Figure 1.11 The Platzer planetary mill (Fink and Buch, 1979). Introduction 15
1.7 Further Reading
A large number of books dealing with the rolling process are available. Among these the excellent books of Roberts Cold Rolling of Steel Hot Rolling of Steel and Flat Processing of Steel (Roberts, 1978, 1983, 1988), stand out. These are emi- nently readable, giving the history of the processes, detailed description of the equipment and the mathematical treatment. Rolling of shapes as well as flats is considered. Rolling of metals is considered exclusively by Underwood (1950), Starling (1962), Larke (1965), Tarnovskii et al. (1965), Tselikov (1967), Wusatowski (1969), Pietrzyk and Lenard (1991), Ginzburg (1993) and Lenard et al. (1999). Books dealing with the theory of plasticity or metal forming have chapters devoted to the rolling of metals. These include the books of Hill (1950), Hoffman and Sachs (1953), Johnson and Mellor (1962), Avitzur (1968), Backofen (1972), Rowe (1977), Lubliner (1990), Mielnik (1991), Hosford and Caddell (1983) and Wagoner and Chenot (1996). It may be necessary to review the background to plastic forming of metals. The reader may then refer to textbooks dealing with the mathematical theory of plastic- ity, theory of elasticity as well as continuum mechanics. Perusing books dealing with the metallurgical phenomena of hot and cold metal forming may also be use- ful. The list of technical publications dealing with various aspects of the rolling process is prohibitively long to be included here.
1.8 Conclusion
The concerns of the present book, strips and plates, were defined according to their geometry, such that the ratio of their width to thickness is much larger than unity. The flat rolling process, capable of producing strips and plates, was described in general terms. The integrated steel mill and hot strip mill, including its compo- nents, were described in some detail. Hot, warm and cold rolling were mentioned and the temperature ranges for each were given. A brief presentation of some mill configurations was also given, including two-, four- and six-high arrangements. The Steckel mill, the Sendzimir mill and the planetary mill were discussed, accom- panied by several illustrations. Mini-mills were presented and some comparisons of their capabilities to integrated steel mills were demonstrated. Material for further reading was also included, classified into two sections. In one, texts dealing with a general treatment of plastic deformation of metals are listed. These include the nec- essary theory of plasticity in addition to the application of the theories to the analy- sis bulk and sheet metal forming problems. The second category includes specialist books, dealing with the process of rolling. 2 History of Hot Strip Mills1
2.1 Hot Strip Mill Evolution
Hot strip mills have evolved in various steps from original tinplate and sheet rolling mills. The development of semi-continuous and continuous multi-stand mills fol- lowed, producing small-diameter and eventually large-diameter steel coil products. Low-, medium- and high-carbon steels, high-strength low alloy steels, X grade pipe steels, silicon steels and stainless steels were rolled. The early hot strip mills were first constructed in 1924. They were of low capacity, producing 300,000À900,000 short tons per year with low specific coil weights. Shortly after the advent of the early hot strip mills, reduced cost and lower capacity single- stand reversing hot strip mills, known as Steckel mills, were developed and placed in operation. These mills employed a heated coiling furnace on each side of the mill stand. Higher capacity Steckel mills were also developed. These included an upstream reversing rougher for slab reduction to transfer bar for finishing in the Steckel mill. By 1961, the early hot strip mills had been upgraded or replaced by larger capacity semi-continuous and continuous Generation I hot strip mills with capaci- ties of about 400,000À3,000,000 short tons per year. These mills employed rela- tively small slab reheating furnaces and continued to produce low specific coil weights. Generation I mills also utilized a reversing rougher to roll discrete plates which were removed by plate transfer before the finishing mill. In some of these cases the reversing rougher was wider than the finishing mill in order to produce the desired maximum plate width. Some other Generation I mills utilized the fin- ishing mill to roll discrete plates which were removed by a plate transfer either before or after the down coilers. The practice of rolling discrete plates on some of the Generation I mills was discontinued in most Generation II mills, many of which produced coiled plate products. Prior to the development of continuous casting of slabs, first introduced in the 1950s, cast ingots were reheated in soaking pits and rolled on slabbing mills to pro- duce slabs for reheating and rolling to a finished strip on the hot strip mills. Often the maximum strip width to be produced was greater than the maximum slab width that could be provided by the slabbing mill. In these cases the first roughing stand of the hot strip mill was a broadside mill with entry and delivery slab turning tables or slab lift and turn mechanisms which were used to rotate the slabs 90.
1Contributed by Donald R. Adair, flat rolling manager, Quad Engineering Inc. and Edwin B. Intong, for- mer technical manager for Electrical & Automation, US Steel Engineers and Consultants.
Primer on Flat Rolling. DOI: http://dx.doi.org/10.1016/B978-0-08-099418-5.00002-0 © 2014 Elsevier Ltd. All rights reserved. 18 Primer on Flat Rolling
The broadside mill then cross-rolled the slab in a single pass to increase the width, as required. Eventually the development of continuous slab casting eliminated the use of slabbing mills except for a few specialty steel mills. Most hot strip mills today roll only continuous cast slabs. For energy conservation and increased slab reheating capacity, continuous slab caster hot strip mill installations ideally are arranged to permit the direct charging of hot slabs into the hot strip mill reheat furnaces. From 1961 through 1970, 11 new Generation II hot strip mills were built in the United States (Ess, 1970). These mills were of heavier design, higher power and higher speed with increased annual capacities of 2,000,000À3,800,000 short tons per year and produced larger coil unit weights of 16.8À22.3 kg/mm. Many other Generation II type mills have been built throughout the world from 1961 to date. The finished strip thickness ranged from 1.2 to 12.7 mm for the initial Generation II mills and from 1.2 to 25.4 mm for upgraded and newer Generation II mills. In actual practice the Generation II mills don’t roll much below 1.7 mm due to strip threading and shape problems. In the 1970s, the Steel Company of Canada (Stelco) developed the hot strip mill coil box (See Figure 1.3; also the web-site www.hatch.ca/technologies/Coilbox/ 80FLDR002_Coilbox-en.pdf) and the concept of Generation III hot strip mills by installing a prototype coil box in the Stelco 56v hot strip mill in Hamilton, Ontario, Canada. The transfer bar from the reversing rougher was coiled in the coil box and uncoiled into the finishing mill, thus retaining the transfer bar heat for more uniform finish mill strip entry temperature, resulting in improved strip quality and reduced motor power during finish mill rolling. It was also recognized that the coil box con- cept would permit larger coil unit weights to be produced on shorter new mills or increased coil unit weights to be produced on existing space-limited older mills. Since 1978, when the first commercial coil box was installed in a new hot strip mill at John Lysaght in Australia, many Generation III coil box hot strip mills, including new or upgraded existing mills, have been operating throughout the world. Finished strip thickness ranges from 1.0 to 25.4 mm for coil box hot strip mills. In the 1980s, the compact strip production (CSP) type of hot strip mill was developed by SMS consisting of an electric arc furnace and a thin slab caster which produced a slab thickness of 50 mm and a direct coupled hot strip mill for rolling the thin slab to finished coils. Since 1989 when the first commercial CSP plant was started up at Nucor in Crawfordsville, IN, there have been many CSP hot strip mills operating throughout the world. Mannesmann Demag (now part of SMS), Danieli and Sumitomo have also developed thin slab caster-direct rolling hot strip mills. Mitsubishi-Hitachi has also provided thin slab caster hot strip mills in coop- eration with Mannesmann Demag and using the Sumitomo thin slab casting tech- nology. In addition to thin slab caster hot strip mills in which the slabs are parted for rolling to coils, Arvedi Cremoni/Siemens VAI has developed an endless thin slab casting and rolling process, ESP (endless strip production), wherein the cast slab is directly rolled to finished strip, which is then parted prior to coiling. Finished strip thickness ranged from 0.8 to 25.4 mm for the thin slab caster type hot strip mills. History of Hot Strip Mills 19
2.2 Early Hot Strip Mills
By 1940, the early hot strip mills of wide strip category, considered to be 914 mm or wider, included five mills located outside the United States (a 1676-mm mill in the Soviet Union, a 1270-mm mill in Germany, a 1092-mm mill in Japan, and 1422-mm and 1372-mm mills in England) and 28 mills located in the United States (Ess, 1941). The US mills were equipped with five, six or seven finish stands and except for a few semi-continuous mills which had single reversing roughing mills, most were of the fully continuous type with four or five roughing stands2. The nominal annual capacities of the US mills totalled 17,616,000 short tons. The nomi- nal capacities were considered by American Iron and Steel Engineers (AISE) at that time to be conservative and the actual total annual capacity was estimated to be at least 22,500,000 short tons. The finish mill work-roll and back-up roll dia- meters of the US mills were relatively small, ranging from 546 to 699 mm for the work rolls and 1118 to 1372 mm for the back-up rolls. The mills were limited to producing relatively small specific coil weights, ranging from 5.8 to 11.6 kg/mm, except in the case of Weirton’s mill with 14.8 kg/mm. The early US mills are listed in the Appendix, including year built, mill width, maximum coil unit weight (PIW) and nominal annual capacities in short tons (TPY) totalling 17,616,000 TPY.
2.3 Early Steckel Mills
In 1925, the inventor Abraham P. Steckel in Youngstown, OH, first introduced the steel industry to the concept of a single-stand reversing hot rolling mill with entry and delivery coiling furnaces to reduce steel slabs into hot rolled coils. The first trial Steckel mill was 914 mm wide and began operation in 1931 at the Youngstown Sheet and Tube Co. in Briar Hill, OH. This mill was relocated to Indiana Harbor, Indiana, where it operated until 1935. It was then moved to Dominion Foundry and Steel Company (Dofasco) in Hamilton, Ontario, Canada, where it operated for 20 years before being replaced by a 1676-mm-wide Steckel mill. Some of the early Steckel mills are listed in the Appendix, including the year built, mill width and four- or two high type of mill stand.
2.4 Generation I Hot Strip Mills (USA)
By 1961, there were 30 hot strip mills operating in the United States of wide strip category (Ess, 1970). These mills were 914 mm or wider that had replaced, upgraded or added to the early hot strip mills and as the immediate forerunners to the Generation II hot strip mills, generally classified as Generation I hot strip mills.
233 Data Handbook, published by 33 Magazine in 1970, Newark, NJ. 33 Magazine is not published any longer. 20 Primer on Flat Rolling
The Generation I mills were a mixture of the semi-continuous and continuous types. The semi-continuous mills had single reversing roughing stands and the con- tinuous mills had four or five roughing stands. All had five or six finishing stands (33 Magazine, 1970). The nominal annual capacities of the 30 Generation I mills were much higher than the early hot strip mills, totalling 55,809,000 short tons (Ess, 1970). The finish mill work-roll and back-up roll diameters of the Generation I mills ranged from 546 to 762 mm for the work rolls and 1118 to 1499 mm for the back- up rolls, not too different from the dimensions of the rolls of the early hot strip mills. The coil unit weights were also similar to the early hot strip mills in the range of 5.8À12.0 kg/mm. The total finish mill power ranged from 17,158 to 21,261 kW. The maximum delivery speed ranged from 595 to 710 m/min. The fin- ish mill power indexes K, the total finish mill kilowatt per millimetre of mill width per 1000 m/min maximum finish mill speed, ranged from 9.5 to 23.0. The US Generation I hot strip mills are listed in the Appendix, including year built (year rebuilt), mill width, maximum coil unit weight (PIW) and nominal annual capacities in short tons (TPY) totalling 55,809,000 TPY.
2.5 Generation II Hot Strip Mills (USA)
Between 1961 and 1970, 11 new hot strip mills were built in the United States (Ess, 1970) and a 12th new mill was added in 1974. These mills resulted from cus- tomer requirements for closer strip tolerances which required larger, stiffer mill stands, and for larger coils also desired by the steel producers for increased operat- ing efficiency. The work-roll and back-up roll diameters ranged from 635 to 724 mm and 1372 to1575 mm, respectively (Ess, 1970). The larger roll sizes and mill housing sections were designed to accommodate increased rolling forces and torques. For improved quality and increased productivity, most of the Generation II Mills included newly developed quick work-roll change systems instead of slower, less safe crane-operated porter bar work-roll changing. The US Generation II hot strip mills were relatively wide with widths ranging from 2032 to 2184 mm except for the first mill and the last mill which were 1473 and 1727 mm wide, respectively. The mills were equipped with six or seven finish stands. Two of the mills were semi-continuous with single reversing roughing stands and one or two non-reversing roughing stands. The remaining 10 mills were fully continuous with 4À6 roughing stands (Ess, 1970). For improved thickness tolerance using uniform temperature control and increased production rates using higher rolling speeds, the finish stands of these mills were more highly powered than the earlier mills in order to incorporate the new development of “zoom rolling”. With zoom rolling technology, the strip head end is threaded from the last finish stand to the coiler at a constant speed up to about 610 m/min, and then the finishing mill is accelerated to higher rolling speeds History of Hot Strip Mills 21 as permitted by the finish mill speed cone and power up to about 1220 m/min. Prior to the development of zoom rolling, the entire coil was rolled at the particular product coiler thread speed, which contributed to limited production capacities of the earlier mills. In these mills the maximum slab dimensions ranged from 203 to 305 mm thick- ness, 1346 to 2032 mm width and 8.5 to 12.2 m length with maximum weights of 18À47 short tons. The minimum slab widths ranged from 356 to 711 mm. The fin- ished strip thickness ranged from 1.2 to 12.7 mm and the width from 356 to 2032 mm. The total finish mill power ranged from 23,364 to 62,664 kW and the maximum delivery speed ranged from 738 to 1280 m/min (Ess, 1970). The finish mill power indexes K ranged from 14.2 to 23.5. The original annual rated capacities of the first 11 Generation II mills were approximately 2,000,000 to 3,800,000 short tons and the coil unit weights were increased from those of the earlier mills to 16.8À22.3 kg/mm (Ess, 1970). The original annual rated capacity of the 12th Generation II mill is assumed to have been 2,400,000 short tons and the maximum coil unit weight of 18.6 kg/mm. The original annual rated capacities for the 12 US Generation II mills totalled 34,700,000 short tons. Most of these mills have been significantly upgraded with annual capacities increased to as high as 6,300,000 short tons, as in the case of US Steel, in Gary, IN, one of the world’s highest producing hot strip mills. The current annual rated capacities of the US Generation II mills range from 1,500,000 to 6,300,000 short tons and total 45,000,000 short tons3 excluding J&L Cleveland, which has been removed. The 12 Generation II hot strip mills are listed in the Appendix.
2.6 Other Generation I and II Hot Strip Mills
Between 1961 and 1979, many other Generation II type hot strip mills and a few Generation I type mills were built outside the United States. The Generation II mills were equipped with six to nine finish stands (including future provisions). The mills were semi-continuous with one to four roughing stands (known as 3/4 continuous mills, where there is one reversing rougher and three non-reversing roughing stands, followed by the finishing stands) or fully continuous with four to seven roughing stands. Of interest regarding the semi-continuous mills is the Iscor mill in South Africa which was originally provided with a single reversing rougher. Provisions for the addition of a second tandem reversing rougher were also made and this was subsequently installed. Further, the Erdemir mill in Turkey was designed for future conversion to a continuous mill. It was originally provided with a reversing rougher preceded by a non-reversing horizontal scale breaker. The latter was subsequently replaced with a second reversing rougher, therefore providing
3Hot Strip Mill Roundup, Association for Iron and Steel Technology, November 2012; Warrendale, PA. 22 Primer on Flat Rolling two independent reversing roughing mills in lieu of conversion to a continuous mill. The total finish mill power for these Generation II mills ranged from 22,380 to 101,531 kW. The maximum delivery speed ranged from 694 to 1851 m/min and the finish mill power indexes K ranged from 15.0 to 25.9. Other Generation I and II hot strip mills are listed in the Appendix, including year built, mill width, maximum coil unit weight (PIW), and Generation I or II type. Mills with maximum coil unit weight capability in excess of 1500 PIW are indicated as Generation II Super.
2.7 Generation III À Coil Box Hot Strip Mills
In the 1970s, Stelco of Canada developed the hot coil box designed for installation in hot strip mills ahead of the finish mill for coiling the transfer bar from the roughing mill and uncoiling it into the finishing mill. The coil box reduced the distance between the roughing mill and the finishing mill while retaining the transfer bar heat during finish mill rolling. In this way the entire transfer bar would enter the finish mill at approximately the same temperature and the entire strip could be rolled at thread speed without acceleration thereby reducing finish mill power requirements and improving finished strip thickness tolerance and metallurgical uniformity. In 1978, the first commercial coil box was installed in a new hot strip mill at John Lysaght in Australia. Stelco then sold numerous licenses to other steel producers for the application of coil boxes to existing or new hot strip mills. Stelco eventually transferred the coil box technology to Hatch Steel Technologies of Canada, who con- tinue to provide coil box technology throughout the world. The original coil box con- cept, which permitted large unit weight coils to be rolled without zoom rolling, generally resulted in somewhat lower mill capacities in the area of 2À2.5 million short tons per year as compared to the Generation II mill capacities. Some of the newer coil box mills of today, such as Colakoglu in Turkey, are equipped with a very high-powered reversing roughing mill and finishing mill designed for higher speed zoom rolling from the coil box. Inter-stand water cooling is employed for strip tem- perature control, increasing the coil box mill production capacities while at the same time retaining the coil box advantage of a shorter mill layout. Most of the world- wide coil box hot strip mills are listed in the Appendix, including year built, mill width, new or existing mill, and annual capacities in metric tons4.
2.8 Thin Slab Hot Strip Mills
In the early 1980s, SMS Siemag (SMS) developed a pilot plant for a new type of hot strip mill process known as CSP in which thin slabs of approximately
4Coil Box Users, 1978À2007, by Hatch Steel Technologies, 2012. History of Hot Strip Mills 23
2v (50 mm) thickness are continuously cast and directly rolled in a rolling mill, which includes tunnel furnace(s), multiple rolling stands, strip cooling and down coilers. The CSP hot strip mills provided by SMS, beginning with Nucor at Crawfordsville, IN, in 1989, are listed in the appendix, including year built, maxi- mum strip width and annual capacities in metric tons5. Other thin slab casting and direct rolling hot strip mill processes have been developed, including the ISP (in line strip production process) by Mannesmann Demag (now part of SMS); FTSC (flexible thin slab casting) by Danieli; QSP (quick ship program) by Sumitomo and ESP by Arvedi Cremoni/Siemens VAI. The Mannesmann Demag and some of the Danieli thin slab caster hot strip mills are listed in the Appendix, including year built, maximum strip width and annual capacities in metric tons. Thin slab caster hot strip mills referenced by Mitsubishi-Hitachi, some of which were provided with Mannesmann Demag ISP or Sumitomo QSP thin slab casting technology, are listed in the Appendix, including year built, maximum strip width and annual capacities in metric tons6. The Arvedi Cremoni/Siemens ESP thin caster Hot strip mill (HSM) is listed in the Appendix including year built, maximum strip width and annual capacity in metric tons. The introduction of the thin slab hot strip mills has relegated Generation I, II and III hot strip mills to be referred to as conventional slab hot strip mills.
2.9 Newer Generation II Hot Strip Mills
From 1980 to date, newer Generation II hot strip mills were built almost exclu- sively as semi-continuous mills, essentially eliminating the previous classical and costly continuous roughing mill configuration. The 1727-mm Dofasco hot strip mill, built in 1982, is unique in that it includes a single reversing mill that is actually a 1372-mm two-high universal slabbing mill. It initially rolled ingots from soaking pits to finish mill transfer bar when the mill started up in 1982 with only five finish stands. Subsequently Dofasco installed slab casters eliminating ingot rolling and the current mill annual production is 4,600,000 short tons with the slabbing mill and seven finish stands. Several of these newer semi-continuous mills include slab sizing presses to reduce slab caster width change requirements and all include single or multiple roughing stands which in some cases have sufficient capacity to achieve yearly ton- nages equivalent to or greater than the older continuous roughing train Generation II mills. Some of the newer Generation II hot strip mills are listed in the Appendix, including year built, mill width and annual capacities in metric tons7.
5Siemens AG, Compact Strip Production, 2010. 6Mitsubishi-Hitachi Machinery Inc., Hot Strip Mills, 1954À2010. 7SMS Siemag, Hot Rolling Mills Division, Reference List of Conventional Hot Strip Mills, 2010. 24 Primer on Flat Rolling
2.10 Modern Steckel Mills
The development of modern Steckel mills has included many items of improved design including more effective descaling, hydraulic automatic gauge control (HAGC), work-roll bending control, larger coiling furnaces and coiling drums, quick work-roll change, retractable furnace tables, higher speed rolling, combina- tion strip and discrete plate, coiled plate Steckel mills and twin-stand Steckel mills. A number of the more modern Steckel mills throughout the world are listed in the Appendix, including year built, maximum strip width and annual capacities in met- ric tons. Twin-stand Steckel mills are indicated by an asterisk8.
2.11 Hot Mill Electrical Systems
2.11.1 Power System
Integrated steel plants usually provide a part of their electric power requirements with their own generating equipment, the power being produced using by-product fuels. Due to the large amount of power required by the mills and the concentration of this load, electrical power may be furnished by plant generation, by purchase from outside utilities or by a combination of the two. Where the plant generates its own power, it is usually that of the plant distribution system which then feeds the various load centres. With purchased power, incoming lines are often at the high transmission voltage which is stepped down to a suitable plant distribution voltage in a nearby outdoor station. This reduced voltage may tie into the plant general power system, forming a combined system. The basic connected electrical load for hot rolling mills varies widely, ranging from 32 to 70 MVA, depending on the size of the mill and the extent of operations. In the conventional layout of the hot strip mill, the motor room is usually paral- lel to the mill and lies between the hot mill building and the slab yard. The main mill drive motors are located in this area together with their respective gear reducers, switching and control equipment, motor generator sets, etc.
2.11.2 Motors and Drive Systems
The original prime movers used in rolling mills were reciprocating steam engines, designed for low pressure steam. Later, gas engines using blast furnace gas as fuel were developed and were used as prime movers for electric generators to drive the mills. Nowadays, virtually all mill stands and auxiliary equipment are powered by electric motors. Where the stand can operate at constant speed in one direction, the alternating current motor is generally used. For variable speed and reversible drives, the more expensive direct current motor is commonly employed. Since the early nineteenth century, the desired range of speed has increased and closer speed
8SMS Siemag, Hot Rolling Mills Division, Reference List of Steckel Mills, 2010. History of Hot Strip Mills 25 regulation has been required. This was responsible for the adoption of variable speed direct current motors for the main drives. Motor selection is based on the heaviest schedules after investigating the requirements of the various schedules. Two factors of importance in motor selec- tion are the peak loads imposed and the motor heating or root-mean-square loads. The motors driving the roughing mill stands are usually of equal power. The motors driving the first five or six stands of the finishing mill are of equal power while that at the last stand is about 370À740 kW less. In the case of a continuous hot strip mill, due to the fact that the slab is in one roughing stand at a time as it passes through the mill, the motors driving these stands may be of constant speed. These motors are generally of the wound rotor induction type, controlled by slip regulators with torque motors to reduce power peaks. Since the duration of passes in a roughing stand is short and the time that the steel is in the rolls is only a small percentage of the total time, induction motors with flywheels make an ideal application. Synchronous motors offer the advantage of power factor corrections, simplification of control, low-cost and high electrical efficiency. As the strip passes through the finishing train, it is in all finishing stands at the same time and the finishing drives must be of variable speed. The mill speeds are determined from the rolling schedules and the speeds determine the related values of reduction gear ratios and motor speeds. For DC motors the speed is controlled by the potential applied to the armature until the base speed is attained. To achieve higher speeds, usually up to two or three times the base speed, the field current is decreased. The motor speed is accu- rately regulated by means of a speed regulator system using reference either from operator settings or from a computer system. AC type motors include synchronous and wound rotor induction motors, the former usually being less expensive if an exciter is not required. The synchronous motor has the stator wound with core and coils in the same manner as the squirrel cage and wound rotor type. Apart from being less expensive, a synchronous motor has the added advantages of high efficiency and the ability to correct the power factor. In the late 1960s, AC drive technology progressed to the point that AC motors could be controlled by a combination of power converters (e.g. cyclo converters with use of thyristors) or the newly developed solid-state power transistors. The lat- ter benefitted with technologies, such as GTO, IGBT and IEGT power devices9. These allowed the AC power to be inverted to DC and then converted back to AC to drive the AC motors. Such technological advancement allowed the stringent regulation of the AC motors, not possible before. In modern mills, the drive of choice is AC motors with DC systems relegated to upgrades of existing mills having such drives.
9GTO, gate turn-off thyristor; IGBT, insulated gate bipolar transistor; IEGT, injection-enhanced gate transistor. 26 Primer on Flat Rolling
2.11.3 Computer Control
The automation of hot rolling mills has matured such that the control system has been organized in hierarchical levels. At the topmost is what is known as level 3, which has the production planning and control function. This level is responsible for setting the optimized production for production orders and feeds the raw mate- rial and target product information to the next lower level of control. Level 3 also collects product information resulting from the rolling process and saves it in data- bases for future retrieval. The next lower level of control, level 2, is known as process automation, where each product is rolled and tracked individually in the plant. This function also con- tains mathematical models which calculate the optimum rolling set-ups for the mill (e.g. gap, speed, force, temperatures). The next lower level of control, level 1, is the basic automation which controls the basic sequences and automation functions of the individual equipment in the hot mill. These may include dedicated technological functions, such as automatic gage control, width control, temperature control, in the laminar flow system and others. The lowest level, level 0, includes the basic drive equipment regulators and controls.
2.12 Hot Strip Mill Innovations
Over the years many important hot strip mill innovations have been developed, a selection of which is listed below. Walking beam slab reheat furnaces in place of pusher furnaces for improved slab heating and reduced slab skid marks Furnace slab extractors in place of furnace dropout chutes for reduced equipment damage and slab defects Slab descale boxes with higher pressure headers in place of vertical and horizontal scale breakers for removal of furnace scale Slab sizing press (slab squeezer) to reduce slab caster width change requirements Vertical motor-driven roughing mill edgers in place of horizontal motor bevel gear- driven edgers for reduced maintenance Edger rolls with box pass to contain slab corner bulging for reduction of slab width spread Hydraulic automatic width control (AWC) edger adjustment in place of fixed edger screws for more uniform slab width control Two-stand tandem reversing rougher for increased roughing capacity with reduced mill length Direct motor table roller drives in place of bevel gear table roller group drives for reduced maintenance Delay table heat retention covers to reduce transfer bar temperature run-down History of Hot Strip Mills 27
Hot coil box addition to eliminate transfer bar temperature run-down, reduce finish mill power requirements, increase coil unit weight on existing mills or reduce mill length on new mills Mandrel-less coil box to eliminate coil transfer mandrel temperature effect High-pressure finishing mill entry descaling units to replace two high roll finish scale breakers M stand (named after its original developer, Nippon Steel, Muroran Works) addition in front of an existing small crop shear for thicker transfer bar up to 60 mm from the rough- ing mill, in order to increase coil unit weight, increase reversing mill capacity, reduce transfer bar temperature run-down and reduce finish mill power and zoom rolling requirements Heavy crop shear and F0 stand addition close coupled in front of finish stand F1 for thicker transfer bar up to 60 mm from the roughing mill in order to increase slab/coil unit weight, increase reversing mill capacity, reduce transfer bar temperature run-down and reduce finish mill power and zoom rolling requirements Finish mill quick work-roll change instead of porter bar for shorter and safer work-roll change for increased productivity and improved product quality Direct transfer of finish mill work rolls to and from the roll shop to reduce roll handling by overhead crane and roll transfer car Finish mill gear spindles and universal joint spindles to replace slipper spindles for reduced maintenance and smoother, safer operation Finish mill rolling lubrication application for reduced work-roll wear and reduced rolling power requirements Finish mill work-roll bending for work-roll crown and strip shape control Finish mill HAGC for more uniform thickness control Finish mill zoom (accelerated) rolling for reduced transfer bar temperature run-down and higher mill production Conventional slab hot strip mill-finish mill endless rolling for reduced head end thread- ing, improved yield and higher productivity Thin slab hot strip mills Thin slab endless rolling hot strip mills Hydraulic finish mill loopers to replace motor-operated loopers for faster looper response for more uniform strip width control and reduced strip necking Finish mill continuous variable crown (CVC) work-roll shifting control for improved strip shape Finish mill work-roll shifting for reduced roll wear and extended rolling campaign Work-roll pair cross-rolling for improved strip shape On-line work-roll grinding for extended rolling campaign Six-high finish stands for reduced strip edge drop and increased roll bending capacity Tool steel, high-chrome iron and high-speed steel finish mill work rolls for reduced roll wear and extended roll campaigns Finish mill long stroke HAGC cylinders to eliminate mill screw-down maintenance requirements Finish mill inter-stand laminar strip cooling to permit higher speed zoom rolling on Generation II and Generation III mills for higher production Finish mill fume suppression sprays to eliminate the need for fume exhaust systems Finish mill delivery profilometers (fixed and traversing X-ray gauges) for on-line strip profile measurement 28 Primer on Flat Rolling
Finish mill delivery shapemeters Finish mill delivery multi-functional temperature, thickness, shape, profile and width gauges Finish mill delivery in line strip surface inspection Individual motor-driven close-centred run-out table rollers without aprons for thin-gauge higher speed coiler threading Water curtain strip cooling headers for increased strip cooling efficiency Three-stage strip cooling system for production of dual phase and transformation induced plasticity (TRIP) steels Servo valve position-controlled hydraulic cylinders for down coiler entry-side guards, pinch rolls and wrapper rolls jump control in place of air cylinders for improved strip coiling quality Down coiler double step mandrel expansion to tighten coil inner wraps Down coiler mandrel improvements for longer mandrel campaigns Eye horizontal coil handling to eliminate coil eye vertical chain conveyor maintenance and coil edge damage.
2.13 Revamped Hot Strip Mills
Many hot strip mills have been upgraded in order to increase mill productivity, yield and quality, and to reduce maintenance. An example of a US Generation II hot strip mill to be significantly upgraded is the US Steel 84v continuous hot strip mill in Gary, IN. This mill was originally built in 1967 with an estimated annual capacity of 3.5 million short tons. The mill has undergone productivity and quality improvements including new computer con- trol, digital drives and automation, CVC roll shifting, work-roll bending, HAGC, in line strip inspection, hydraulic down coilers and other improvements that have raised the current annual capacity to 6.3 million short tons. In the case of Generation I mills, some have been modified to a new configura- tion in order to increase the coil unit weight capability, improve strip quality, expand product range and increase mill production. A few examples of modified Generation I Hot strip mills are listed below. British Steel, Port Talbot, UK: 2032 mm fully continuous mill started up in 1953, capable of producing 9 kg/mm coils, was upgraded in place over the period of 1984À1986 includ- ing new furnaces, new single reversing rougher, new coil box, repowering for existing six stand finishing mill, new finish stand F7 and new down coilers capable of producing 18 kg/mm coils. Nippon Steel, Muroran Works, Japan: 1422 mm semi-continuous mill started up in 1957, capable of producing 7 kg/mm coils with an annual capacity of 790,000 metric tons, was upgraded in place over the period of 1965À1979 including new furnaces; new heavy reduction M stand with entry edger for introducing the 60 mm maximum transfer bar into existing crop shear; repowered, upgraded, higher speed six finishing stands and repower- ing of existing two down coilers capable of producing 21.4 kg/mm coils with annual capacity of 3,000,000 metric tons. History of Hot Strip Mills 29
Pittsburgh Steel, Allenport, PA: 1676 mm semi-continuous mill started up in 1953, capa- ble of producing 9 kg/mm coils with a yearly capacity of 900,000 short tons, was disman- tled, rebuilt, modernized and relocated over the period of 1989À1993 by National Steel Corporation (NSC) in Iligan City, Philippines with the addition of a new furnace, heavy reversing rougher with a new edger, new heavy crop shear for 60 mm maximum transfer bar into the F0 stand (original Allenport reversing rougher) close coupled in tandem with modernized and repowered six existing finishing stands and new down coiler capable of producing 18 kg/mm coils with annual mill capacity of 2,500,000 short tons with addition of second furnace and down coiler. 3 Roll Design1
3.1 Introduction
The stock surface, under rolling conditions, is a mirror image of the roll surface, which erodes with time because the contact area between the roll and stock suffers wear. This erosion depends on a large number of factors, including the loads, and hence the stresses, they experience. As well, it depends on the roll grade, the chem- ical composition and the microstructure. Loads in an industrial rolling mill are not clearly and precisely defined. There are mathematical models to calculate the maxi- mum stress in rolls, determined by design limits for maximum separation force, torque, Hertzian pressure, etc. These criteria are valid only under normal rolling conditions À meaning no non-standard events occur, such as cobbles2 (see also Chapter 7 for a mathematical model of the mechanisms of the formation of cob- bles). They also change continuously with progressive wear in the contact zone. During normal rolling conditions, for example a stable operating period, mills expe- rience changes in the rolling conditions. After a roll change or a mill stop, rolls need some time to return to stable thermal conditions. Sometimes there are severe rolling accidents, due to faults by operators or weak rolled materials with internal defects, or because of other problems in a mill such as a power cut, mechanical problems or issues in the water cooling system. While problems of this kind can never be predicted, they have a detrimental effect on all rolling schedules, including stresses in the roll. During abnormal rolling conditions, for example a cobble or torn-off tail end of the strip, roll damage often occurs with consequences for the mill and the rolled product. The rolls experience local over-stressing, due to double or even triple strip thickness in the roll bite, which they are not capable of resisting. They must be checked for damage before returning to service.
3.2 General Overview
While casting and forging are old technologies going back more than 3000 years, rolling assumed major importance in the industrialized world only during the nineteenth century. Initially, steel was rolled to profiles (rails, beams, channels,
1Contributed by Dr. John B. Tiley, hot rolling consultant. 2Cobbles are sudden changes in the thickness of the rolled strip. They are mechanical marks formed dur- ing localized overloads where the resultant stress imparted exceeds the yield strength of the rolled material.
Primer on Flat Rolling. DOI: http://dx.doi.org/10.1016/B978-0-08-099418-5.00003-2 © 2014 Elsevier Ltd. All rights reserved. 32 Primer on Flat Rolling rounds), but since about 1930 flat products (sheet and strip) have become increas- ingly dominant. Profiles and flats are hot rolled (the latter to a minimum size). Thin, flat products are finished by cold rolling for various reasons À for example, to achieve a better shape and profile, or because of mechanical properties or surface conditions. In the recent past (,20 years), rolling technology has improved and changed dramatically. Rolls have always remained the critical part of rolling mills. The development of roll qualities and roll-making technology followed the development of rolling technology. Product dimensional and surface quality requirements continued to tighten as the resolution of the measuring instruments improved. Rolling mill industries followed the evolution of the automotive indus- try. The demand for rolled products continued to grow. While the need for rolls decreased due to improved rolling technology and better roll qualities, the market situation for rolls is continuously undergoing changes.
3.3 Historical Development of Rolls for Rolling Mills
The quality of the strip and the productivity of the hot rolling mills are two of the most important concerns in the steelmaking plants. The quality of the strip is evalu- ated mainly by means of its shape, roughness and dimensional tolerances, all of them depending strongly on the shape, profile and surface quality of the work roll. The productivity of the rolling mill is directly related to the length of campaigns of the rolls, the essential aim being to maintain, over time, the initial surface rough- ness, shape and strip profile, which are affected by wear. Saving costs with minimum roll grinding is also important, since rolls are responsible for 5À15% of overall production costs. In most cases, work rolls for the finishing stands of hot rolling mills are cast-composite components made of an outer shell of wear-resistant material and a core of ductile iron or steel. For the work rolls of the early finishing train (stands 1 to 4), the development of materials for the outer shell has enjoyed rapid advances beginning in the early 1980s, culmi- nating in the application of cast alloys of the FeÀCÀCrÀWÀMoÀV system which gradually replaced high-chromium cast iron and Ni-hard cast iron with better per- formance (Hashimoto et al., 1995; Sano et al., 1992; Savage et al., 1996). These alloys are generically termed “high-speed” steels or multi-component white cast iron (Ziehenberger and Windhager, 2007; Garza-Montes-de-Oca, 2011). The idea of using these alloys for manufacturing work rolls for hot strip mills resulted from an insight into the requirements involved in this type of application: fundamentally, the capacity to retain a high level of hardness even when experiencing high temperatures, and also strong wear resistance. Thus, although alloys have been specifically designed to meet the operational conditions of each hot-strip mill plant, their chemical compo- sitions generally fall into the following ranges: 1.5À2.5% C; up to 6% W; up to 6% Mo; 3À8% Cr and 4À10% V. In the nineteenth century, unalloyed grey iron, modified only by various carbon equivalents and different cooling rates (grey iron chill moulds or sand moulds), and Roll Design 33 forged steel were used for rolls. The cast iron grades varied from “mild-hard” to “half-hard” to “clear chill”, where the roll barrel showed a white iron layer surface (free of graphite) and grey iron core, due to reduced cooling rate. This type of roll was used for flat rolling without any roll cooling in “sheet mills”. In the twentieth century, cast steel rolls were developed with a carbon content of up to 2.4%, with and without graphite, and are still produced today. Around 1930, Indefinite Chill Double Poured (ICDP) rolls were invented for hot rolling, especially for work rolls in the finishing train of hot strip mills. These were also used for many other applications such as roughing stands of hot strip mills and work rolls in plate mills. This grade was to become the world standard for many years with very limited variation. For some time, no other material could replace this grade for several applications. In the late 1990s, ICDP rolls enhanced with car- bides improved roll performance and started a new phase for this grade which is still successfully in use today in work rolls for early finishing stands and for plate mills. Around 1950, nodular iron was invented and introduced into roll manufacturing, unalloyed as well as frequently alloyed using Cr, Ni and Mo, giving good wear resistance and strength at the same time. The use of “high chromium iron” (2À3% C, 15À20% Cr) and later on “high chromium steel” (1À2% C, 10À15% Cr) brought new materials, with high wear resistance and “forgiveness”, into rolls. This was a major step towards greater productivity in the industry. In 1985, High Strength Tool Steel3 (HSS) materials were introduced into rolls and evolved to “Semi-Tool-Steel” grades. After initial problems, these changes brought new opportunities for better roll performance. After the introduction of new grades to the mills it was often necessary to change rolling conditions. All of these roll grades are currently used for flat and long products. Forged steel rolls were also improved for cold rolling to give higher hardness penetration after heat treatment by increasing the content of alloying elements. The chromium content was increased from 2% to 5% and induction hardening was used to achieve the desired surface hardness. Chromium plating of work rolls after grinding and shot blasting also helped maintain the necessary surface roughness. In reality, rolls are tools for metal forming. Therefore the development of suitable roll materials goes hand in hand with the development of other cutting and non-cutting tools in metal industries. Rolls are relatively large tools with an extended life, but ultimately, they are only tools.
3.4 Roll Wear
Work roll wear is a complex process characterized by the simultaneous operation of several surface degradation phenomena. The essential target of the rolling mill plant is to keep the shape, profile and surface roughness as close as possible to the initial
3High-Speed Tool Steels are FeÀCÀX multi-component alloy systems where X represents chromium, tungsten, molybdenum, vanadium or cobalt. 34 Primer on Flat Rolling ones that existed at the last roll change. The better performance of the HSS rolls, in comparison to the forerunner work roll materials, is related to its microstructure char- acteristics: the presence of great amounts of very hard (2800À3000 HV), fine and discontinuous metallic carbide, eutectic carbides and a matrix hardened by secondary precipitated carbides. The microstructure of the high-chromium cast iron, for instance, consists of the softer M7C3 eutectic carbide (1100À1800 HV) and a less high-temperature-resistant matrix (Maratray, 1970; Boccalini and Goldenstein, 2001; Lee, 1997; Webber, 2011). The degradation of the work rolls for the early finishing stands involves, at least, abrasion, oxidation, adhesion and thermal fatigue (Park et al., 1999; Spuzic, 1996; Ryu et al., 1992). Thermal fatigue results from stresses developed by cyclic heating and cooling of a very thin boundary layer close to the work roll surface, no thicker than 1% of the work roll radius (Chang, 1999). This layer is repeatedly heated by the hot strip, the work of plastic deformation and the roll/strip friction in the roll bite and cooled by water during the remaining portion of its rotation. The boundary layer is thus subjected to compressive stresses during the heating cycle, since its thermal expansion is constrained by the bulk roll which remains at approximately constant temperatures during the operation. If the compressive stresses are high enough to plastically deform the layer (softened by the high tem- perature), residual tensile stresses in excess of the rupture strength may develop during the cooling cycle and cracking will take place (Debarbadillo and Trozzi, 1981). The primary crack pattern is related to thermal and mechanical stresses imposed on the roll and not to the microstructure of the shell material. Eutectic carbides4 play a decisive role in the nucleation and propagation of the secondary cracks (Chang, 1999; Caithness et al., 1999). Thermal fatigue experiments show that sec- ondary cracks nucleate at eutectic carbides, caused by the stress concentration induced by the difference between the thermal coefficients of expansion of the car- bide and the matrix, and propagate along the carbide/matrix interface (Lee et al., 1997; Wisniewski et al., 1991). Since the presence of eutectic carbides, and thus crack nucleation, is unavoidable, improving thermal fatigue resistance requires their refining and homogeneous distribution so as to avoid the formation of easy crack propagation paths, like inter-dendritic or inter-cellular coarse M7C3 or M2C carbides. The combination of thermal fatigue and mechanical stresses, inherent to the roll- ing process, progressively extends and branches the cracking network through the sub-surface thickness. This process may lead to a catastrophic deterioration in which large segments of the roll surface, containing the oxide layer built up during rolling together with portions of the roll material, are peeled off. The peeling, known as “banding”, leaves a roughened roll surface, unsuitable for further rolling. Adhesion is a consequence of the micro-welding regions of the strip metal into roll metal in the sticking zone of the roll gap, mostly where there is no relative motion between the strip and roll surfaces (Hashimoto, 1995). Resultant wearing
4Eutectic carbides are carbides formed during freezing in ferrous alloys. Roll Design 35 takes place when the interfaces in contact are made to slide and the micro-welded regions must separate, hot shearing the roll material (Werquin et al., 1990; Ludema, 1992; Lanteri et al., 1998). The formation of large pores in the surface of the rolls, commonly named “comet tails”, is attributed to the intense occurrence of adhesion (Werquin et al., 1990). Adhesion resistance of the roll materials is improved by increasing the vol- ume fraction of eutectic carbides. Werquin et al. (1990) explained this behaviour, indicating that the hot hardness of the eutectic carbides is higher than that of the matrix, allowing for higher hot shear strength. Hence, within the same concept, he suggested that adhesion resistance can be further improved through increasing the hot hardness of the matrix by means of secondary hardening heat treatment. It is noted that adhesion is primarily controlled by the physico-chemical interaction between the materials of the roll and the strip.
3.5 Friction and Wear
Work rolls in hot strip mills wear due to friction between the roll surface and hot strip. (Back-up rolls wear as well, but under pressure with elastic deformation, the friction is much less, except for the high work roll roughness in the last stand of a sheet rolling tandem cold mill). The wear is uneven from one end of the barrel to the other. A shining, dark oxide layer always covers the roll surface, from the beginning to the end of a campaign, as long as there is no banding/peeling. Friction and wear occur whenever materials move and slide relative to each other. In rolling mills, wear takes place mainly at the areas of highest friction; that is between a roll and the rolled material. (There is, of course, also wear in mills on other parts with almost no friction. For example, the barrel of back-up rolls in four high hot mills is subject to wear as well, but the amount is not as high). Wear nor- mally is not equally distributed on the barrel from one end to the other because strip conditions vary over the strip width and the edges of rolls are never in contact with rolled material at all. In hot rolling mills the roll surface is also influenced by changing temperatures during each rotation, which may create fire-cracks, influenc- ing friction and wear. A third factor of the impact on wear is roll/strip cooling. Cooling agents may be water or a water/emulsion mixture. These may be clean or not and may contain lubricants and chemical additives, potentially causing damage to the roll surface. Wear and fire-cracks increase progressively during the rolling campaign. After each campaign, rolls are redressed and reground to re-establish the correct original shape and surface roughness. In this process the diameter of a roll is reduced by grinding until all visible signs of wear and fire-cracks have been removed, often under the control of eddy current testing equipment, which is required for HSS rolls. Additionally, some amount of stock may be removed for safety reasons, to reduce the risk of problems due to undetected sub-surface damage. 36 Primer on Flat Rolling
Bakelite
Scale layer
Substrate
Figure 3.1 Cross-section of oxide flake, pressed into the substrate (2003 magnification). Source: Reproduced from Tiley (2006).
If the roll surface is damaged from a mill accident, for example, by local over- stressing or fire-cracks, then these have to be eliminated immediately by further grinding, otherwise the roll will fail catastrophically. This is a new discipline which operators need to follow to be successful when converting to HSS work rolls (Figure 3.1). At the end of roll life the total rolled material (in terms of tons or length of product) is related to total stock-removal for normal rolling, excluding stock- removal for accidents. This results in a figure for productive or effective roll per- formance. If stock-removal for accidents is included, then this figure is called “total roll performance”. These figures are the most important ones for evaluating the performance of the roll, allowing a comparison with other grades, and in making a distinction between various roll suppliers. During the last 50 years different roll grades were used for work rolls of hot strip mills and for some time up to four different grades were used simultaneously in different stands. All these grades weremanufacturedinthesamerangeofhard- ness. However, wear performance differed widely. With the realization that roll wear decreases when extremely hard carbides are used, the development of carbide-enhanced ICDP rolls followed this strategy using carbides of higher hard- ness in a strong martensitic structure. The performance of these ICDP rolls was improved in many mills, by a minimum of 20%, maximum beyond 100%. Other grades will likely follow the same direction, bearing in mind that wear resistance is just one required property. For the same roll grade, the little increase in wear resistance that might theoreti- cally exist is often over-compensated for by the risk of unproductive loss of roll Roll Design 37
Figure 3.2 Progressive build-up of the oxide layer(s) on an HSS work roll. Source: Reproduced from Kerr (1999); with permission. life following rolling accidents. By increasing hardness, the ductility of the material is reduced and for all materials there is an optimum of useful hardness. Unfortunately it is not easy to find general rules for the best wear-resistant mate- rials for all applications because the wear conditions vary too widely (Figure 3.2). 4 Flat Rolling A General Discussion
4.1 The Flat Rolling Process
The essential concept of the flat rolling process is simple and it has been in use for centuries to produce sheets and strips, or in other words, flat products. Leonardo da Vinci employed it to roll lead, utilizing a hand-cranked mill, depicted in Roberts’ book, Cold Rolling of Steel (1978). The Leonardo museum, located in the medieval Castello Guidi, built between 1100 and 1200 AD in the city of Vinci about 30 km from Firenze, contains some interesting examples of Leonardo’s plans for a rolling mill, shown in the website of the museum (http://www.leonet.it/comuni/ vinci/). Two figures, reproduced from that website, are given below. Figure 4.1 is a page of Leonardo’s plans on which the handwriting is, unfortunately, indecipher- able. The scale model, built according to these plans and shown in Figure 4.2,is able to roll a sheet of tin 30 cm wide. The basic idea for the production of flat pieces of materials by rolling has not changed since the process was introduced. Dimensions, materials, precision, speed, the mechanical and metallurgical quality of the product and most importantly the mathematical analysis and the control of the process have evolved; however, and as a result, the flat rolling process may truly be considered one of the most success- ful “high-tech” processes, since for modern, efficient and productive applications, the theories and practice of metallurgy, mechanics, mechatronics, surface engineer- ing, automatic control, continuum mechanics, mathematical modelling, heat trans- fer, fluid mechanics, chemical engineering and chemistry, tribology and, encompassing all, computer science are absolutely necessary.
4.1.1 Hot, Cold and Warm Rolling The rolling process may, of course, be performed at low and high temperatures, in the cold rolling mill or in the hot strip mill, respectively, as already mentioned in Chapter 1. The formal distinction between what is low and what is high tempera- ture, and in consequence, what are the cold and hot rolling processes, is made by considering the homologous temperature, in which the low end is at absolute zero and the high end is at the melting point of the metal to be rolled, Tm. When the pro- cess is performed at a temperature below 0.5Tm, it is usually termed cold rolling, while above that limit, hot rolling occurs. In addition to the above strict definitions of hot and cold rolling, there is the warm rolling process as well. The temperature range for this phase is not defined very precisely but it starts somewhat below
Primer on Flat Rolling. DOI: http://dx.doi.org/10.1016/B978-0-08-099418-5.00004-4 © 2014 Elsevier Ltd. All rights reserved. 40 Primer on Flat Rolling
Figure 4.1 Leonardo’s plans for a simple rolling mill.
Figure 4.2 The scale model of Leonardo’s mill.
0.5Tm and changes to hot rolling at some temperature above that. Each of these processes has advantages and disadvantages, of course. At the high temperatures at which hot rolling is performed the metal is softer so less power may be needed for a particular reduction. Further, understanding the effects of the process parameters Flat Rolling A General Discussion 41 of the rolling process on the mechanical and metallurgical attributes allows the development of metals with specific, engineered properties; the process is termed thermal-mechanical treatment. The disadvantage of rolling at high temperatures concerns the development of a layer of scale on the surface and its effect on the process and the quality of the resulting product. All of these need to be clearly understood, such that they may be controlled with confidence. Cold rolling follows the pickling process in which the layer of scale is removed. Here the control of dimensional consistency and surface quality is the most important objective. Strict thickness and width tolerances must be maintained for the product to be commer- cially acceptable. During warm rolling some of the disadvantages of the hot rolling process are minimized as scale formation is less intense. The energy requirements increase, however, as the metal’s resistance to deformation is now higher.
4.1.2 Mathematical Modelling Use of sophisticated on-line and off-line mathematical models allows these activities to proceed. A number of models have been developed, some simple and some making use of the availability of the finite-element method. Among the latter, the model developed by the American Iron and Steel Institute (Hot Strip Mill Model, HSMM) stands out. A quotation from the AISI website is given below:
HSMM is one of several commercially licensed technologies developed under AISIs advanced process control programme, a collaborative effort among steelmakers and the U.S. Department of Energy to create breakout steel technologies. HSMM simulates the steel hot rolling process for a variety of steel grades and products, and forecasts final microstructure and properties, allowing the user to achieve a deeper insight into operations while optimizing product properties. Prior to its commercial release, it was used for several years by steel companies that helped develop the technology.
In each of these models the ideas of equilibrium, material behaviour and tribol- ogy are used to describe the physical phenomena. The first of these three is based on Newton’s laws. The latter two require experimentation and the translation of the experimental data into mathematical expressions for use in the models. The traditional and simplest approach when mathematical analyses of metal forming processes are considered is to allow the material’s resistance to deforma- tion to be exclusively strain-dependent in the cold forming regime and to be exclu- sively strain-rate-dependent in the hot range. In the warm forming range the metal’s strength is usually both strain- and strain-rate-dependent. It is acknowl- edged, of course, that these are much simplified and in Chapter 8, dealing with the attributes of the metals, other more inclusive and more sophisticated material mod- els are presented. In advanced mathematical treatment, by finite difference or finite-element techni- ques, the metals’ constitutive relation should be described in terms of several inde- pendent variables, including, at the very least, the strain, strain rate, temperature and 42 Primer on Flat Rolling metallurgical parameters, one of which is the Zener Hollomon parameter, used extensively (see Chapter 4 on material attributes for the definition). In some instances the metal’s chemical composition is also included in the equations. The tribological events at the contact of the work roll and the rolled metal are also to be described in terms of parameters and variables.
4.1.3 The Independent and Dependent Variables The discussion above leads to the consideration of both the dependent and indepen- dent variables of the flat rolling process. It is first necessary to identify the bound- aries of the domain under consideration. For the arguments presented in what follows, these define a single stand of a two- or four-high mill, such that they are used in most laboratories during the development of the data on forces, torques, energy requirements and the resulting microstructures. Under industrial conditions, a full-size mill stand, regardless of being the roughing mill or the finishing train, is being considered. It is a metal rolling system that is, fact, being defined and, in the same sense as any metal forming system, is divided into three essentially indepen- dent but interconnected components: the rolling mill, the rolled metal and their interface. The significant dependent variables depend on what the objectives of the industry, of the engineers operating the rolling process, of the researcher develop- ing a mathematical model or of the customers happen to be. There may be three separate but interdependent objectives. One of these is the design of the rolling mill. Another objective is the design of the rolled strip while the third potential objective is the design of the interface between the rolls and the rolled strip. The essential components of the rolling mill are the work rolls and the back-up rolls, the bearings, the mill frame, the drive spindles, the inter-stand tensioning devices, the heating and cooling equipment, the lubricant delivery apparatus and the driving motor. Their attributes, which affect the rolling process, include their dimensions in addition to roll material, crowning, roll surface hardness, roll rough- ness and its orientation, mill frame load-carrying area, mill stiffness and hence, mill stretch. In choosing the driving motor, its power and speed are to be deter- mined. Mill dynamics is also a significant contributor to mill performance and is a function of all of the above in addition to the process variables, such as the reduc- tion, the speed and the dimensional consistency of the as-received metal. All of these affect the quality of the rolled metal. All may be considered as the indepen- dent variables. The variables associated with the rolled metal include its mechanical, surface, metallurgical and tribological attributes: yield strength, tensile strength, strain and strain rate sensitivity, bulk and surface hardness, ductility and formability, fatigue resistance, chemical composition, weldability, grain size and distribution, precipi- tates, surface roughness and roughness orientation. Since the transfer of thermal and mechanical energy is accomplished at the interface of the work roll and the rolled strip, and the efficiency of that transfer is Flat Rolling A General Discussion 43 one of the most critical parameters of the process, the attributes of the contact are, arguably, the most important when the quality dimensional accuracy, consistency and uniformity of the surface parameters of the product is designed. The surface roughness of the rolls and their directions have already been mentioned. The attri- butes of the lubricant are to be considered here and among these are the viscosity and its temperature and pressure sensitivity, density, chemical composition and droplet dimensions if an emulsion is used. While environmental friendliness of the lubricant and the manner of its disposition after use are other, most important, con- siderations, they do not affect the quality of the product. While all of these variables should be considered when the rolling process is designed and/or analysed, they rarely, if ever, are. Engineers simplify the task and consider only what is absolutely necessary. The rolling mill, its capabilities, its driving system and its peculiarities are, of course, given and will be changed only when forced by industrial competition or the development of processes that lead to increased productivity and/or reduced costs. The metal to be rolled must, in usual circumstances, be one in the product mix offered by the particular company. In unusual circumstances, if the customer requires a chemical composition or mechan- ical and metallurgical attributes different from those available, either the request would be refused and another metal among the company’s products similar to the customer’s prescription would be offered or the costs of the development of the new metal would form a major part of the complete process costs. This second pos- sibility would, of course, be prohibitively expensive. The choice of the lubricant, its volume flow and the lubrication system are often considered to be no more than a maintenance issue and in the opinion of the present writer, it is an uninformed and a highly mistaken view. The most significant independent variables usually considered in the analyses of the flat rolling process are listed below, classified according to the three components of the metal rolling system. These will be dealt with in what follows, in some considerable detail.
The rolling mill Roll diameter and length Roll material Roll surface roughness Roll toughness and hardness The metal Chemical composition Prior history grain size, precipitates Constitutive relation Initial surface roughness The interface Lubricant attributes chemical compositions, viscosity, temperature and pressure sensitivity, density; droplet size if an emulsion is used The rolling process Reduction Speed Temperature 44 Primer on Flat Rolling
4.2 The Physical Events Before, During and After the Pass
These events have been mentioned by Lenard et al. (1999). In the discussion that follows the earlier presentation has been enlarged and some more important ideas have been included. The first consideration is that in the presentation, the shapes of the work roll and the rolled strip are considered to be highly idealized. The work roll’s cross section is taken to be a perfect circle at the start and that makes the roll a perfect cylinder. The line connecting the roll centres is taken to be perpendicular to the direction of rolling and it remains so during the pass. The distance between the roll centres is considered to remain unchanged in most analyses, ignoring mill stretch1. The rotational speed of the work rolls is and remains constant, even after the loads on it increase and the inevitable slowdown under high torque loads is ignored. The strip to be rolled is straight, its sides make right angles to one another and the thickness and the width are uniform as is the surface roughness. The following events occur when the process of rolling a flat piece of metal starts, continues and is completed. As mentioned above, the work rolls are consid- ered to be rotating at a constant angular velocity. The strip or the slab is moved towards the entry and is made to contact the rotating work rolls, either by vertical edge rollers or by a conveyor system or both. When contact is made, the leading edge of the strip enters the deformation zone because of the friction forces exerted by the work rolls on it and it is not difficult to show that the minimum coefficient of friction, necessary for successful entry is given by:
μ 5 φ ð : Þ min tan 1 4 1 φ where 1 is the bite angle. In most analytical accounts of the entry, the first contact is assumed to be along a straight line, across the whole length of contact with the work roll. In reality, there must be a significant amount of deformation of both the edges of the strip and the roll, suggested by common sense as well as by the loud noise always heard on entry to the roll gap of an industrial mill. The leading edge of the strip must be thickened somewhat on contact and the roll must be flattened, but the present author is familiar with surprisingly very little research concerning the geometrical changes at the instant of entry. In one of the early attempts Kobasa and Schultz (1968) used high-speed pho- tography which allowed some, albeit limited, visualization of the entry conditions and the length of contact in the rolling process. The published photographs do not allow a clear, close look at the deformation at the initial contact, however. The stresses in the metal increase, and the limit of elasticity of the strip is reached soon after entry, followed by permanent, plastic deformation. One usually assumes that the flat strip rolling process can be described in terms of one independent vari- able, taken in the direction of rolling, and that the stresses do not vary across the strip thickness. This assumption in turn is based on the usual homogeneous compression
1Ignoring the mill stretch in the control software would, of course, lead to significant errors; mill stretch is accounted for in the set-up programs used for rolling mills. Flat Rolling A General Discussion 45 assumption and the often-employed statement that “planes remain planes”. With these assumptions, the elastic plastic boundary becomes a plane perpendicular to the direction of rolling and on that plane the criterion of yielding is satisfied first. When the process is treated as a two-dimensional problem, as in many finite-element analyses, the elastic plastic boundary may be quite different from that described above. When strip rolling is considered and the roll diameter/strip thickness ratio is large in industrial settings this ratio varies from about 25 30 at the first stand of the finishing train of the hot strip mill to as high as 400 1000 in the last stand the one-dimensional treatment is perfectly adequate, and yielding and the beginning of plastic flow are taken to occur on a plane, parallel to the line connecting the roll cen- tres, as just described. The permanent deformation regime then remains in existence through most of the roll gap region, followed by the elastic unloading regime which starts when the converging channel of the roll gap begins to diverge. Often, the yield- ing process is simplified further, and rigid plastic material behaviour is assumed to exist, ignoring the elastic deformation completely. With this assumption, the rolled metal is taken to satisfy the yield criterion and to begin full plastic flow as soon as it enters the roll gap. The assumption of rigid plastic behaviour is usually acceptable when hot rolling is analysed. It has often been shown that treating the cold rolling process requires the use of elastic plastic material models. These events are illustrated in Figure 4.3A C, which show a schematic diagram of a two-high mill and a strip ready to be rolled, rolled partway through and rolled continuously, in a steady-state condition. As well, the free-body diagram of the roll is indicated, showing the pressures, forces and torques acting on it. The conditions shown describe either a laboratory situation where no front and back tensions exist or a single stand reversing mill, such as a roughing mill. Three stages of the rolling process are shown in Figure 4.3A C, respectively. In Figure 4.3A the strip is about to make contact. The strip velocity at this point is dependent on the edge rollers or the conveyor system but it is usually significantly less than the surface velocity of the work rolls. If the coefficient of friction is larger than the tangent of the bite angle, as indicated by Eq. (4.1), a relationship that is often used to determine the minimum friction necessary to start the rolling process, the strip enters the deformation zone. In a laboratory mill, the usual practice is to carefully and lightly push the strip2, placed on the delivery table, towards the work rolls and allow the friction forces to cause entry. Under certain circumstances, when viscous lubri- cants are used or the roll speed is high, it is necessary to mill a shallow taper on the leading edge of the strip to facilitate the bite. Care must be exercised in this case con- cerning the placement of the lubricant. In an experiment in the writer’s laboratory, a highly viscous lubricant was used and to ensure bite, the tapered leading edge was left dry. Entry was achieved but when the rolls encountered the portion covered with the oil, the strip tore into two, in a violent fashion; sudden changes of the tribological conditions along the length of the strip to be rolled should be avoided.
2Caution is highly recommended here. The strip should never be pushed by hand but by a long piece of wood or another strip; this practice will eliminate the danger of rolling a few of the operator’s fingers. 46 Primer on Flat Rolling
Figure 4.3 (A) Schematic diagram of the strip’s entry into the roll gap Entry is imminent Work roll (Lenard et al. (1999) reproduced with permission). (B) The strip is Force of friction partially in the deformation zone (Lenard et al. (1999) reproduced with permission). (C) Free-body Strip diagram of the work roll. Roll flattening Source: Lenard et al. (1999) Thickening of reproduced with permission. the strip
(A)
Roll separating force
The strip is partially in the roll gap Roll torque
Elastic region Plastic region
(B) Elastic–plastic interface
Roll separating force
Shear stresses Roll torque on the roll surface
Roll pressure (C) distribution
In a hot strip mill, vertical edge rolls force the strip into the roll gap in the first stand and the momentum of the strip exiting from there carries it into the deforma- tion zone of the next stand. In either case, entry creates some longitudinal compres- sion of the strip and there will be some initial thickening as well, more than in cold rolling. This is accompanied by local, elastic deformation of the work rolls, indicat- ing that the usual simplification about the entry point located where the perfectly straight edge of the strip encounters the undeformed, perfectly cylindrical roll does not represent reality very well. In a cold mill the strip is often threaded through the stationary mill and attached to the coiler on the exit side. The rolls Flat Rolling A General Discussion 47 then close and gradually reach the pre-determined roll gap and the mill is started, so no bite is required. Figure 4.3B shows the strip about halfway through the deformation zone. As previously mentioned, the unloaded metal first experiences elastic deformation, and when and where the yield criterion is first satisfied, plastic flow is observed. These two regimes are separated by an elastic plastic boundary, the shape and the loca- tion of which should be determined by the mathematical analysis of the rolling pro- cess. In the elastic region, the theory of elasticity governs the deformation of the metal. In the permanent deformation region, the criterion of yielding, the appropri- ate associated flow rule, the condition of incompressibility and the appropriate compatibility conditions describe the situation in a satisfactory manner. The rolls are further deformed they bend and flatten. The magnitude of the roll stresses should not exceed the yield strength of the roll material. The theory of elasticity is to be used to determine the roll distortion and the corresponding changes of the length of contact. In Figure 4.3C, the leading edge of the rolled metal has exited and the rolling process is continuing, essentially as a steady-state event. The figure shows the pres- sures, the forces and the torques acting on the roll and on the strip. These include the roll pressure distribution and the interfacial shear stress, the integrals of which over the contact length lead to the roll separating force and the roll torque. These are the dependent variables the mathematical models are designed to determine. If front and back tensions are present, as would be the case under industrial condi- tions in the finishing mill stands, their effect on the longitudinal stresses at the entry and exit should be included in the definitions of the boundary conditions. The roll separating force and the roll torque may be used to study the metal flow in the roll gap. As well, they may be used to design the rolling mill itself. Knowledge of the magnitude of the roll separating force is needed to size the mill frame, the roll neck bearings and the roll dimensions, including roll crowning and roll flatten- ing. The roll torque is necessary to establish the dimensions of the spindles, the power required of the driving motor and the couplings. The surface velocities of the roll and the strip should also be considered. It may be assumed that the driving motor is of the constant torque variety and that the rolls rotate at a constant angular velocity, even though there may be some slowdown under high loads. The strip usually enters the roll gap at a surface velocity less than that of the roll. The friction force always points in the direction of the relative motion, and on the entering strip it acts to aid its movement. As the compression of the strip proceeds, its velocity increases3 and approaches that of the roll’s surface. When the two velocities are equal, the no-slip region is reached, often referred to as the neutral point4. At that location, the strip and the roll move together, and their relative velocity vanishes. If the neutral point is between the entry and the exit, the strip experiences further compression beyond it, and its surface velocity surpasses
3Recall that the assumption of plane-strain flow implies no width changes. Hence, incompressibility implies that the sum of thickness and the length strains should vanish. 4The ideas of the “neutral point” and the “neutral region” will be discussed in more detail in Chapter 12. 48 Primer on Flat Rolling that of the roll. Several researchers suggest that reference should be made to a neutral region instead of a neutral point, hypothesizing that the no-slip condition extends over some distance. In that region, between the neutral point and the exit, the friction force on the strip has changed direction and is now retarding its motion. The site between the entry and the neutral point is often referred to as the region of backwards slip. The location between the neutral point and the exit is called the region of forward slip. The forces shown are the external loads acting on the work rolls. The rolls are in equilibrium, of course, and the surface forces at the contact must be balanced by other, external forces. These originate at the bearings that exert the forces on the rolls to keep them in equilibrium, in a relatively stationary position. There are two types of loads at the roll bearings. One is a vertical force, minimizing the possibility of the roll moving upwards, called the roll separating force. The other is a turning moment, originating from the drive spindle, referred to as the roll torque. In a two-high mill, these are the loads acting on the work roll, balancing the effects of the loads originat- ing at the interface: the pressure of the strip on the roll and the interfacial frictional forces. If a four-high configuration is studied, the forces normal and shear at the back-up roll and the work roll contact need to be included as part of the free- body diagram. The picture changes somewhat when front and back tensions are also consid- ered, as would have to be done to account for the effects of the preceding and the subsequent mill stands and the effects of the loopers these are devices between the mill stands that keep some tensile forces in the strips. These forces act in the direction of rolling, of course, and would have an effect on the magnitudes of both the roll separating forces and the roll torques. It is possible and simple to include the effect of inter-stand tensions in the mathematical models of the process. Knowledge of the roll separating force and torque is necessary for three possible purposes: 1. to design the mill its frame, bearings, drive systems, lubricants and their delivery; 2. to determine the dimensions and the properties of the rolled metal; 3. to allow the development of control systems for on-line control of the process.
4.2.1 Some Assumptions and Simplifications In dealing with the process of flat rolling, it is advantageous to consider two assumptions frequently made when mathematical models are developed. The first is to acknowledge the almost true fact that the width of the flat product is practi- cally unchanged: the plane-strain flow phenomenon. The second, again almost true, which allows the use of ordinary differential equations in the models, is the planes remain planes simplification.
4.2.1.1 Plane-Strain Flow The flat rolling process is usually taken to be essentially two-dimensional in the sense that the width of the product does not change much during the pass when Flat Rolling A General Discussion 49 compared to thickness and length changes and this makes the assumption of plane- strain plastic flow5 quite realistic. When one is to study roll bending and the atten- dant changes of the shape of the rolled metal in addition to the changes of the field variables across the width stress, strain, strain rate, temperature, grain distribu- tions a change from the 2D mathematical formulation to 3D is unavoidable. Of course, the width changes in the flat rolling process and this and its effect on the resulting product have been considered in numerous publications. As long as the width to thickness ratio is over 10, however, this change is not taken to be very significant. In rolling experiments, using strips of about 1 mm thickness and 10 25 mm width, the strain in the width direction is rarely over 2 3%.
4.2.1.2 Homogeneous Compression A discussion of the homogeneous compression assumption is also necessary here. This phenomenon has been studied experimentally by visio-plasticity methods in addition to observing the deformation of pins inserted into the rolled metal. Figure 4.4 shows in part (A) that the originally straight lines bend, while in (B) they do not and the original planes remain planes. In the second case, the compression of the strip during the rolling pass is referred to as “homogeneous compression”. Schey (2000) differentiates between the two possibilities, depending on the magnitude of the ratio of the average strip thicknesspffiffiffiffiffiffiffiffiffiffiffi in the pass, have 5 0:5ðhentry 1 hexitÞ, and the length of the contact, L 5 R0Δh, where R0 is the radius of the flattened but still circular work roll (this idea will be discussed later, in Chapter 5, dealing with mathematical modelling of the process) and Δh 5 hentry 2 hexit, of course. When have=L is larger than unity the deformation in inhomogeneous and the originally straight planes bend as shown in Figure 4.4A. When the ratio is under unity, the effects of friction on the rolling forces and torques are significant and the homogeneous compression assumption may be made with confidence. When strip rolling is discussed, whether hot or cold, the “planes remain planes” assumption is very close to reality, with one possible exception. This concerns metal flow in the first few passes of the slab through the roughing train of a hot strip mill where the strip thickness is in the order of 200 300 mm and the work rolls maybe 1 m or more in diameter, leading to a roll diameter/strip thickness ratio in the order of 3 5. In the finishing train this ratio increases by at least an order of magnitude and the plane-strain assumption becomes acceptable. Venter and Adb- Rabbo (1980) examined the effect of Orowan’s (1943) inhomogeneity parameter on the stress distribution in the rolled metal. They concluded that the effect is more significant when sticking friction is considered to exist, compared to sliding fric- tion6. The distributions of the roll pressure, with or without the inhomogeneity parameter differed by about 10%.
5The deformation is deemed “plane-strain” when the strains in two directions are very much larger than that in the third direction. 6While the sticking friction has been assumed to exist in hot rolling in past analyses, recent studies indi- cate that it rarely occurs in the flat rolling process; use of lubricants reduce the coefficient of friction. 50 Primer on Flat Rolling
(A) (B)
Figure 4.4 (A) Non-homogeneous compression. (B) Homogeneous compression.
Some further consideration of the term “the width doesn’t change by much” is necessary here, in light of a recent publication by Sheppard and Duan (2002) who used FORGE3s V3, a three-dimensional, implicit, thermomechanically coupled, commercially available finite-element programme to analyse spread during hot roll- ing of aluminium slabs. While the authors’ predictions correspond to experimental and industrial data very well, the slabs they examined cannot be considered to behave according to the plane-strain assumption. In their study the slabs measure 25 mm width and 25 mm entry thickness, rolled using a roll diameter of 250 mm. In the industrial example, the measurements are 1129 mm width and 228 mm entry thickness. The roll diameter is 678 mm. In both cases lateral spread, measured and calculated, is shown to be considerable. When one considers strip rolling, however, in which case the roll diameter to entry thickness ratio is large in comparison to unity in addition to the width/thickness ratio also being large, homogeneous compression planes remaining planes during the pass as well as the assumption of plane-strain flow are quite close to the actual events. In what follows, both assumptions will be made without any further reference. Further simplifications and assumptions will be detailed and discussed in Chapter 5, dealing with the details of mathematical modelling of the flat rolling process.
4.3 The Metallurgical Events Before and After the Rolling Process
The rolling process begins by continuous casting7, or if an older, not modernized steel plant is considered, by ingot casting. In the most modern mills continuous casting is followed directly by hot rolling. In all of these cases the pre-rolling
7See Figure 1.5, Chapter 1. Flat Rolling A General Discussion 51
Figure 4.5 (A) The microstructure of an Nb-carrying steel fully recrystallized after 55% deformation in five passes at 1100 1070 C. (B) The same steel, subjected to the same deformation pattern but at a lower temperature of 1000 960 C, shows significant grain elongation. The magnification is 1003. Source: Cuddy (1981). structure consists of dendrites which are subsequently removed in the reheat fur- naces in which most of the alloying elements enter into solid solution. It may be assumed, then, that at the start of the rough rolling process the sample is in the aus- tenite range and that it has been fully annealed and recrystallized before entry into the roughing mill stands8. The structure is made up of strain free, equiaxed grains. The steel is reduced in the rougher, in several steps, all performed at relatively high temperatures and not excessive rates of strain and it then passes on to the fin- ishing train. The grain structure at this stage depends on the pass schedule in the rougher, but, as has been mentioned above, the influence of the metallurgical struc- ture prior to entry into the finishing train has little influence on the final attributes. Two typical examples of the steel’s structure are shown in Figure 4.5A and B, reproduced from the publication of Cuddy (1981). The figures show the microstruc- tures obtained by subjecting the samples to several, sequential plane-strain com- pression tests9. The chemical composition of the microalloyed steel was also given; it contained 0.057% C, 1.44% Mn and 0.112% Nb. The steel was reheated to 1200 C and deformed by 55% in five passes. Figure 4.5A shows a fully recrystal- lized structure obtained at a deformation temperature of 1100 1070 C. The test shown in Figure 4.5B, which was conducted at a lower deformation temperature of 1000 960 C, indicates flattened grains and, as a result, some strain hardening.
8It is difficult to prove the validity of this assumption as it is impossible to interrupt the rolling process to remove a piece of the hot steel for metallography. Some of the micrographs that are shown have been obtained from various laboratory simulations. 9Use of sequential, multi-stage hot compression tests in simulating the multi-pass rolling process will be discussed in Chapter 8. 52 Primer on Flat Rolling
Figure 4.6 The structure of an AISI 1008 steel, finish rolled, coiled and then hot rolled from a thickness of 3 mm, reduced by 10%. The magnification is 2503. Source: ASM Handbook (1985) reproduced with permission.
Following rough rolling, the transfer bar enters the finishing train where the microstructure undergoes further changes, again depending on the draft schedule which is usually prepared off-line, using mathematical models that are able to pre- dict the expected metallurgical and mechanical attributes. There are prohibitively many possibilities to consider in one book so only a typical structure is shown in Figure 4.6, reproduced from the ASM Handbook (1985). The structure of a capped AISI 1008 steel is shown at a magnification of 250. The steel was finish rolled, coiled, then hot rolled from a thickness of 3 mm and reduced by 10%. The steel was then cooled in air, resulting in the fully ferritic microstructure. The next step that follows is the cold rolling process after the hot rolled, scaled surface is cleaned by pickling in hydrochloric acid. Several passes reduce the thick- ness further. The effects of progressively higher reductions are shown in Figure 4.7, demonstrating the resulting grain elongation.
4.4 Limitations of the Flat Rolling Process
There are several limits that designers of the draft schedule of flat rolling must con- sider. One of these, the minimum coefficient of friction necessary to initiate the process, has been mentioned above, see Eq. (4.1). Other limitations of the process include the minimum rollable thickness, alligatoring and edge-cracking. The first of these appears to be caused by the creation of a hydrostatic state of stress in the deformation zone. The latter two are also the consequence of the stress distribution, specifically the tensile stresses associated with the elongation of the rolled samples. Flat Rolling A General Discussion 53
Figure 4.7 Microstructure of a cold rolled, low-carbon steel sheet showing ferrite grains at (A) 30%, (B) 50%, (C) 70% and (D) 90% cold reduction. The magnification is 5003. Source: Benscoter and Bramfitt (2004) reproduced with permission.
4.4.1 The Minimum Rollable Thickness This phenomenon10 is observed to occur when a thin, hard strip is to be reduced in a single rolling pass using large-diameter rolls. In order to increase the reduction, the work rolls are progressively brought closer and closer in an attempt to reduce the roll gap. As the reduction is increased, the compression on the strip is also increasing and the work rolls deform more and more. After a certain gap dimension is reached, no further reductions of the thickness of the strip are possible; the mini- mum rollable thickness has been reached. A hydrostatic state of stress is supposed to have been built up within the strip in the deformation zone. Recalling that the material undergoing permanent plastic deformation retains its volume, no further change of the dimensions of the metal is possible. If the work rolls are forced to close still further, they flatten more, the mill frame stretches further and the mini- mum rollable thickness cannot be reduced any more. Further attempts are likely to
10The minimum thickness problem will be mentioned again in Chapter 12. 54 Primer on Flat Rolling cause damage to the mill. This thickness is a function of the material attributes of the metal as well as the elastic attributes of the work roll and of the mill frame. Early researchers estimated the magnitude of the minimum obtainable thickness in a rolling pass. Stone (1953) presented the formula
3:58Dμσ h 5 fm ð4:2Þ min E where the roll diameter is D, its elastic modulus is E, and σfm is the resistance of the rolled material to reduction (see Eq. (5.2)). Tong and Sachs (1957) also predict that the minimum rollable thickness is proportional to the same parameters as in Eq. (4.2). Johnson and Bentall (1969) hypothesize that the minimum rollable thick- ness does not actually exist in practice. Domanti et al. (1994) write that rolled thickness, beyond those predicted, was achieved in foil rolling mills. Nevertheless, the minimum rollable thickness is a real, actual limitation of the rolling process and its existence has been demonstrated in several instances. Researchers, using small scale laboratory rolling mills, are cautioned against attempting to demonstrate the existence of the minimum thickness. It is possible to force the work rolls together more and more, of course, but the chances of creating permanent damage to the mill and the attendant costs of replacing the cracked rolls are both usually prohibitively high.
4.4.2 Alligatoring and Edge-Cracking The rolled strip’s length grows while it is being reduced and the tensile strains in the direction of rolling often limit the reductions possible in a single pass. The stress distribution in the deformation zone may cause either alligatoring or edge- cracking. These were purposefully created while hot rolling aluminium strips with tapered edges (Duly et al., 1998), in order to examine the workability of the alloys. In each pass the work rolls were covered with a light coating of mineral seal oil. Severe edge-cracking is shown in Figure 4.8, rolled at a temperature of 505 C. Edge-cracking and alligatoring are demonstrated in Figure 4.9.
Figure 4.8 Edge-cracking of an aluminium alloy, hot rolled at 505 C to a strain of 0.6. Source: Duly et al. (1998). Flat Rolling A General Discussion 55
Figure 4.9 Alligatoring of an aluminium alloy, hot rolled at 497 C to a strain of 0.56.
Workability and the limits of the process during hot rolling of steel and alumin- ium were considered in some detail by Lenard (2003).
4.5 Conclusion
A brief, general presentation of the flat rolling process was given. Two assumptions the “planes remain planes” and “homogeneous compression” necessary for the understanding of the flat rolling process were critically examined. The physical and the metallurgical events experienced by the steel were discussed. These included the examination of the free-body diagram of the work roll, in three conditions: the strip is ready to enter the roll gap; it is partially through; and steady-state rolling has been reached. As far as the metallurgical phenomena are concerned, several micrographs were presented, each showing the microstructure of the rolled strips, undergoing various rolling schedules. The limits of the process were presented. 5 Mathematical and Physical Modelling of the Flat Rolling Process
The essential, basic ideas in mathematical modelling of the flat rolling process are presented first. Empirical and one-dimensional (1D) models, applicable for strip rolling, are described and their predictive capabilities are demonstrated. Extremum principles specifically the upper bound theorem are considered. The need whether or not to include the effect of inertia forces in 1D models is discussed. A model, employing the friction factor instead of the coefficient of friction, is derived and its predictive abilities are examined in detail. The development of the micro- structure as a result of the restoration and hardening phenomena during hot rolling and its effect on the resulting mechanical attributes are given. Thermal mechanical treatment is briefly discussed and the physical simulation of the flat rolling process is also included. In the last section, several phenomena, often ignored in mathematical modelling of the process, are given. These include the forward slip, mill stretch, roll bending, the lever arm and the effects of cumula- tive strain hardening. An approach that considers the difficulties associated with determining the relevant values of the coefficient of friction and the metals’ resis- tance to deformation for use in modelling is suggested.
5.1 A Discussion of Mathematical Modelling
Mathematical models of the flat rolling process are numerous and are easily avail- able in the technical literature. The publications date from the early days of the twentieth century to the present. Their complexity, mathematical rigour, predictive ability and ease of use vary broadly. In what follows, models applicable to strip and plate rolling only will be presented, such that the large-roll diameter to strip thickness ratios allow the application of the “planes remain planes” assumption, implying that nearly perfect homogeneous compression is present in the deforming metal. This step and the additional assumption of the plane-strain plastic flow con- dition1 ensure that there will be only one independent variable in the equations: the
1These two assumptions have been discussed in Chapter 4.
Primer on Flat Rolling. DOI: http://dx.doi.org/10.1016/B978-0-08-099418-5.00005-6 © 2014 Elsevier Ltd. All rights reserved. 58 Primer on Flat Rolling distance along the direction of rolling or the angular variable around the roll. Thus, ordinary differential equations will be obtained, the integration of which is consid- erably less difficult than that of partial differential equations that would be obtained without the two assumptions. The available models can be listed according to the objectives the authors had while devising them. They are applicable equally well to hot, warm or cold rolling. These objectives may include the following:
G a simple, fast calculation of the roll separating forces; G in addition to the roll separating force, the roll torque, the temperature rise and the required power are to be calculated; G in further addition to the above, the determination of the metallurgical parameters and the material attributes as a result of the hot and cold rolling are to be determined. A more extensive list of the use of mathematical models of the rolling process is given by Hodgson et al. (1993). The authors add set-up and on-line control of the rolling mills and the rolling process to the use of the models, in addition to the fol- lowing (the list is quoted directly from the reference):
G Minimize mill trials for product and process development. G Evaluate the impact of different mill configurations and new hardware on the process and the work piece. G Predict variables which cannot be easily measured (e.g. bulk temperature, temperature distribution, austenite grain size, post-cooling mechanical and metallurgical attributes). G Perform sensitivity analyses to determine which process variables should be measured and controlled to achieve the required quality, or final properties, of the product G Aid hardware design. G Further understand the physical process. Another comment needs to be mentioned in the context of using the models for predictions of rolling load, etc. The present author has been involved in the study of 1D models of the flat rolling process for quite some time. The studies involved experimentation as well as modelling and the predictive abilities of several 1D models were investigated. When the research studies began to appear in the techni- cal literature, using finite-element models to investigate the flat rolling process, the following suggestion was made to several authors: experimental data would be pro- vided and let us all compare our predictions. None took up the challenge. One com- ment was received: “Our analyses are performed to get insight into the mechanics of the process, not for predictions”. In what follows, some of the basic, classical 1D models2 are reviewed in addition to some of the more recent efforts. While the following list is not complete, it gives the most popular and well-known formulations. A model which includes an account of the variation of frictional effects along the roll/strip contact is also described, employing the friction factor instead of the coefficient of friction. Upper bound anal- ysis of the process is discussed. The development of the metallurgical structure of
2It is recognized that these models were published quite some time ago, yet they often form the bases of existing on-line models. Mathematical and Physical Modelling of the Flat Rolling Process 59 the rolled strips is then reviewed and empirical relations, allowing the calculation of these parameters, are listed. As well, relations that predict the attributes of the mate- rial after the rolling process are given. Further, the predictive abilities of the models are presented and compared to each other and to experimental data. Each of these models will be developed in more detail in subsequent sections, classified as follows. The empirical models. An example of these is presented by Schey (2000). These can be used with considerable ease. Manual calculations, spreadsheets or simple computer programs are sufficient while calculating the roll separating force. The major objective of the models is just that: a simple and fast but reasonably accurate prediction of the roll separating force. The roll torque, the power and the tempera- ture rise may also be obtained, but their accuracy is usually not quite as good as that of the force, no doubt because of the assumptions made in their determination; The 1D models. These are capable of predicting the roll separating forces as well as the roll torques quite well. The traditional models of these types are based on the classical Orowan approach, including the idea of the “friction hill” (Orowan, 1943) and its simplifications. For cold rolling the Bland and Ford (1948) technique and for hot-rolling Sims model (Sims, 1954) are often used in the steel industry, usually as a first approximation, often followed by adjusting the predictions to data taken on a particular rolling mill. Alternatively, the Cook and McCrum tables (1958), based on the 1D Sims model, may be employed. The predictive abil- ity here is enhanced by accounting for the flattening of the work roll under the action of the roll pressure. The well-known Hitchcock formula (1935) is used in these models to estimate the magnitude of the radius of the flattened but still circu- lar work roll while in a more refined 1D version (Roychoudhury and Lenard, 1984) the elastic deformation of the roll is analysed, using the 2D theory of elasticity. Interfacial frictional phenomena are modelled in two ways: mostly using the coeffi- cient of friction and sometimes the friction factor3. The objectives here are similar to those above: that of the calculation of the roll separating force and the roll tor- que. The models can also be used to estimate the dimensions of some components of the rolling mill, such as the cross-sectional areas of the load carrying columns of the mill frame, the dimensions of the bearings, the drive spindles and possibly the power of the driving motor4. In addition to the above, the empirical relations, describing the evolution of the metallurgical structure (the amount of static, dynamic and metadynamic recrystallization, recovery, precipitation, retained strain and vol- ume fraction of ferrite, as well as the mechanical and metallurgical attributes after hot forming and cooling) during and after hot rolling may be added to the 1D models. These equations are based on the studies of Sellars (1979, 1990), Roberts et al. (1983), Laasraoui and Jonas (1991a, b), Choquet et al. (1990), Hodgson and Gibbs (1992), Yada (1987), Beynon and Sellars (1992), Sakai (1995), Kuziak et al. (1997) and Devadas et al. (1991). The predictive abilities of the above relations,
3See Chapter 9 for the definitions. 4Note that the driving motor must have sufficient power to overcome friction losses and to compensate for the significantly less than 100% efficiency of the drive train. See Eqs. (9.8) (9.11). 60 Primer on Flat Rolling while combined with 2D finite-element mechanical models, were reviewed by Lenard, Pietrzyk and Cser (1999). A discussion of modelling the rolling process has been given in Chapter 16 of the Handbook of Workability and Process Design (2003). Extremum theorems.A model based on the extremum principles which, using the upper bound theorem, gives a conservative estimate of the power necessary for the rolling process. Finite-element models. These are discussed in some detail in Chapter 6, where an advanced version is presented. In addition to the care in the formulation of the models, the predictive ability of all of them depends, in a very significant manner, on the appropriate description of the rolled metal’s resistance to deformation and on the way the frictional resistance at the contact surfaces is expressed. Both of these phenomena are considered in detail in subsequent chapters. Material and metallurgical attributes are the topic of Chapter 8 while tribology is treated in Chapter 9. Caution is necessary when the choice of the most appropriate model in a partic- ular set of circumstances is made. Often there is the tendency among researchers to select an advanced model and expect superior predictive capabilities. This step usu- ally results in disappointment. The guiding principle should always be to make the complexity of the model match the complexity of the process and especially that of the objectives. Further, the mathematical rigour of all components, such as the material and the friction models, should match the rigour of the mechanical and the metallurgical formulations. A few comments, concerning the propensity of researchers to comment on the predictive capabilities of their models, are appropriate here. The usual tendency, when the predictions are compared to a few experimental results and the numbers compare well, is to proclaim that the model represents physical events very well. There are two concepts to consider, however, before good predictive ability is to be acknowledged. These are accuracy and consistency. A model that is accurate only sometimes and for which an error analysis has not been considered5 in the study is essentially useless. A model whose predictions may not be most accurate but are consistent, as demonstrated by the low standard deviation of the difference between calculated and measured data, is always useful as it can always be adjusted, a prac- tice often followed in industry. While mathematical models of the flat rolling process have been published regu- larly in the technical literature, a complete list of all of them is much too large to be included in the present volume. Several conferences have been held in the recent past, entitled “Modelling of Metal Rolling Processes”, and the issues involved with all aspects of the rolling process have been discussed at these gatherings. An interesting review of on-line and off-line mathematical models for flat roll- ing was recently published by Yuen (2003). He examined the models that account for the flattening of the work rolls as well as those that don’t include it. He also
5It is indeed rare to see the analysis of the magnitudes of possible errors in the mathematical models. Mathematical and Physical Modelling of the Flat Rolling Process 61 discussed the models available for foil and temper rolling. He concluded that more sophisticated models are expected to be adopted for on-line applications and added that there is an “urgent need for robust algorithms in order to implement these superior models”. Mathematical models of the rolling process are now also available commer- cially. One of the outstanding ones, mentioned already in Chapter 4, has been made available by the American Iron and Steel Institute, the details of which can be obtained from the website www.integpg.com/Products/HSMM.asp. A large collection of software for simulation and process control can also be found at the website www.mefos.se/simulati-vb.htm.
5.2 A Simple Model
A simple model, fast enough for on-line calculations of the roll separating force, has been presented by Schey in his text Introduction to Manufacturing Processes, 3rd edition (Schey, 2000). The model expresses the roll separating force per unit width in terms of the averagepffiffiffiffiffiffiffiffiffiffiffi flow strength of the rolled metal in the pass, the pro- jected contact length, L 5 R0Δh, a multiplier, identified by Schey as the pressure intensification factor, Qp, to accountpffiffiffiffiffi for the shape factor and friction, and a correc- tion for the plane-strain flow, ð2= 3Þ 1:15, in the roll gap. The radius of the work roll, flattened by the loads on it, is designated by R0 (see below for Hitchcock’s equation, Eq. (5.3)). For the case when homogeneous compression of the strip may be assumed and frictional effects are significant, e.g. L/have . 1, and have is the average strip thickness, the model is written
Pr 5 1:15QpσfmL ð5:1Þ where the mean flow strength of the metal, σfm, is obtained by integrating the stress strain relation over the total strain, experienced by the rolled strip:
ðε 1 max σ 5 σðεÞ ε ð : Þ fm ε d 5 2 max 0
The radius of the flattened roll, R0, is obtainable from Hitchcock’s relation (Hitchcock, 1935) 2 2 0 16ð1 v Þ R 5 R 1 1 Pr ð5:3Þ πEðhentry 2 hexitÞ
Hitchcock’s equation and the assumptions on which it is based have been contro- versial ever since it was published quite some time ago. While the critiques are valid the roll doesn’t remain circular in the contact zone and the roll pressure distribution is not elliptical Eq. (5.3) still enjoys widespread use. 62 Primer on Flat Rolling
Roberts (1978) examines the validity of Hitchcock’s equation6 and concludes that
the generally accepted Hitchcock equation, even considering elastic strip flattening, is not adequate to predict the length of the arc of contact between roll and strip.
Schey (2000) also presents an approach to deal with the rolling of thick plates where the assumption of homogeneous compression is not valid any longer. In these cases the shape factor is less than unity, L=have # 1. The plastic deformation is affected less by friction and a different pressure intensification factor is to be used7. The simplicity of the model of Eq. (5.1) is evident when one considers its rela- tion to simple compression, akin to open die forging, expressing the force needed by the product of the mean flow strength and the projected contact length. This is then adapted to that of flat rolling by the application of the multiplier and the cor- rection for plane-strain flow. In a rolling pass the total true strain is εmax 5 lnðhentry=hexitÞ and in cold rolling the stress strain relation is usually taken as σðεÞ 5 Kεn or σðεÞ 5 Yð11 BεÞn1 where K, n, Y, B and n1 are material constants. Other formulations for the metal’s resistance to deformation are also possible of course, and some of these will be pre- sented in Chapter 8. When hot rolling is analysed, the mean flow strength is expressed in terms of the average rate of strain, ε_ave:
m σfm 5 Cðε_aveÞ ð5:4Þ where the average strain rate is given, in terms of the roll surface velocity, v, the projected contact length and the strain by
v hentry ε_ave 5 ln ð5:5Þ L hexit
The material parameters C, m, K, n may be taken from the data of Altan and Boulger (1973) for a large number of steels and non-ferrous metals or may be determined in a testing program. Choosing more complex constitutive relations requires the use of non-linear regression analysis to determine the material con- stants, such as Y, B and n1. Care is to be taken when previously published material models are considered for use. Karagiozis and Lenard (1987) compared the predic- tive capabilities of several published constitutive relations, all claimed by their authors to be valid for low-carbon steels (see Figure 8.16). The recommendation therefore is, as follows: if there is any doubt about the accuracy of the material model that describes the resistance to deformation of the metal to be rolled, inde- pendent testing for the strength is necessary8.
6See also Section 5.4.1 where roll deformation is discussed in more detail. 7This problem is not dealt with in the present manuscript. If interested, refer to the original reference (Schey, 2000). 8Testing techniques are described in Chapter 8. Mathematical and Physical Modelling of the Flat Rolling Process 63
Finally, the multiplier Qp, the pressure intensification factor, is obtained from Figure 5.1 in terms of the coefficient of friction and the shape factor L/have, where have is the average of the entry and exit thickness. The torque to drive both rolls per unit width is then expressed, assuming that the roll force acts halfway between the entry and the exit:
M 5 PrL ð5:6Þ
The lever arm, the distance by which the roll separating force is to be multiplied to determine the roll torque, is thus defined as the projected contact length9. The power to drive the mill is determined using the torque, from Eq. (5.6), and the roll velocity. The relation gives the power in watts, provided the contact length is in m, the velocity in m/s, the roll radius in m, and the units of the width, w, match those of the roll separating force/unit width: v P 5 P wL ð5:7Þ r R0 Note that Eq. (5.7) gives only the power for plastic forming of the strip and thus, it is not to be confused with the power needed to drive the rolling mill, which is sig- nificantly larger. In order to develop the specifications for the power of the driving motor of the mill, friction losses and the efficiency of all drive-train components need to be considered. Rowe (1977) defines the overall power requirement in terms of these parameters, in the form
1 5 ð 1 Þð: Þ Ptotal η η 2P 4Pn 5 8 m t
6 Figure 5.1 The pressure intensification factor Qp. Source: Schey (2000); reproduced with 5 permission. Sticking μ = 02 4 0.15 f σ / p
p 3 =
p 0.1 Q 2 0.05 0 1
0 04812 16 20 L/h
9See Section 5.11.5 where the lever arm is discussed in some more detail. 64 Primer on Flat Rolling
η η where m is the efficiency of the driving motor and t is the efficiency of the trans- mission, including all of its components. Equation (5.8) supplies the power required for plastic deformation and the friction losses in the four roll-neck bearings (Pn) μ φ_ μ are given by nPrw d , where n is the coefficient of friction in the bearings, d is the bearing diameter and φ_ is the angular velocity of the roll. Roberts (1978) includes the resistance of the material in an equation that can also be used to pre- dict the mill power: 1 ðσ 2 σ Þð1 2 rÞ 5 σ 1 entry exit 1 ð : Þ Ptotal η hentrywv cr 2 : Pn 5 9 m 1 0 5r
2 where σc is the dynamic, constrained yield strength of the rolled strip in N/m , w is the width in m, v is the velocity in m/s and r is the reduction in fractions; the power then will be obtained in W. The yield strength at room temperature, in lb/in2, of the “softer” strip is given in terms of the reduction as10
σ 5 40000 1 1773r 2 29:2r2 1 0:195r3 ð5:10Þ where the reduction, r, is given again as a fraction. The constrained yield strength is then taken to depend on the rate of strain: σ 5 : σ 1 ε_ : c 1 155ð 4460 log10 1000 Þð5 11Þ
Roberts (1978) presents a set of calculations of the overall power required to cold roll hard and soft low-carbon steels through a six-stand rolling mill. The predicted and measured input motor powers varied by at most 20% and were under 10% in most cases. In the calculations, the efficiency of the driving motor was taken from a low of 76.7 88.7%, fairly reasonable values. In light of the successful predictive ability, the use of Eq. (5.9) is recommended. As an alternative, the upper bound method may be used to calculate the power necessary to roll the strip; as is well known, the upper bound method gives a conservative estimate of the power for plastic deformation11. In an unpublished study, a simple experiment to estimate the power losses due to friction and drive-train inefficiency was conducted in the present writer’s labora- tory. The work rolls were compressed to a certain magnitude of the roll separating force with no strip in between. The mill was turned on and the torque to drive the mill only was measured. The power thus obtained was in the order of 30% of the power when a strip was reduced in a similar fashion. The rise of the temperature of the strip in the pass due to plastic work may be estimated by P ΔT 5 ð5:12Þ gain mass flow 3 specific heat
10The conversion to SI units is 1 lb/in2 5 6.89476 3 1023 MPa. 11The upper bound approach is treated later in this Chapter; see Section 5.8.1. Mathematical and Physical Modelling of the Flat Rolling Process 65 where the power is to be expressed in J/s, the mass flow is to be in kg/s and the specific heat of the metal (cp) is to be in J/kg C. Equation (5.12) may be written in terms of the roll force, the geometry and the density in the form
0 PrL=R ΔTgain 5 1000 ð5:13Þ ρcphave
Note that while neither the speed of rolling nor the width of the strip appears in the equation, the strain rate would increase with increasing speeds and that would affect the magnitude of the roll separating force, and hence, the power. Note further that an error was knowingly committed in estimating the mass flow: the roll surface speed and the average strip thickness were used instead of the thickness at the no- slip point, which should have been used. While the location of the neutral point may be estimated, it is not known precisely, so the small error, no more than 10%, may be forgivable. Further, care must be exercised in the use of units. The roll sep- arating force is to be in N/m; the contact length is to be in m; the roll radius is to be in m; the density is to be in kg/m3; the specific heat is to be in J/kg C; and the average strip thickness is to be in m. Roberts (1983) also gives a useful expression to estimate the temperature rise of the strip in the pass, which simply takes the work done/unit volume and assumes that all of that is converted to heat. The temperature increase, due to reduction r, may then be calculated by
σfm 1 ΔTgain 5 ln ð5:14Þ ρcp 1 2 r
A numerical experiment illustrates the magnitude of the predicted rise of the tem- perature of a hot-rolled steel strip. For the example, consider a 30% reduction of an initially 10 mm thick strip, using 500 mm radius work rolls which rotate at 50 rpm. Assume that the coefficient of friction is 0.2, a reasonable magnitude when some lubrication is used. Let the density be 7570 kg/m3,takethespecific heat of the steel to equal 650 J/kg K and let the average flow strength in the pass be 150 MPa. The temperature rise is now predicted to be 20 C, by Eq. (5.12).The process and material parameters change drastically in the last stand of the finish- ing mill. Let the entry thickness there be 2 mm and the reduction to be 50%, so the final strip thickness will be 1 mm. The temperature of the strip is lower now, so the average flow strength is 250 MPa; this number includes the effect of the strain rate, caused by the increased rolling speed. The temperature rise is now much higher, calculated to be 135 C. The temperature loss in the pass, due to conduction only is obtained as suggested by Seredynski (1973) in terms of the pass parameters, the heat transfer coefficient12, the density and the specific heat of the rolled steel. Seredynski’s formula is
12The heat transfer coefficient will be discussed in detail in Chapter 9, Tribology. 66 Primer on Flat Rolling rffiffiffiffiffiffiffiffiffiffiffiffiffi r 21 ΔTloss 5 60α ðTstrip 2 TrollÞ½ð12rÞπρcpN ð5:15Þ hentryR where α is the heat transfer coefficient at the roll/strip interface (Seredynski gives its 2 value as 44 kW/m K); r is the reduction in fractions, hentry is the entry thickness, R is the original, undeformed roll radius, Tstrip and Troll are the temperatures of the strip and 3 the roll, respectively, ρ is the density (7570 kg/m ), cp is the specific heat (650 J/kg K) and N is the roll rpm13. The temperature loss in the above two examples may be estimated now, using Eq. (5.15). Most of the numbers are known except one: the temperature of the roll. Roberts (1983) shows the experimental results of Stevens et al. (1971) who used thermocouples embedded in a full-scale work roll to monitor the rise of the temperature of the surface. The results indicate that the roll surface temperature may rise by as much as 500 C14. With these numbers, the strip entering the roll gap at 1000 C may cool by as much as 19 C. In the second example, the loss of temperature is estimated to be 15.6 C, less than before because of the shorter con- tact time. The final temperature of the strip after rolling will be the algebraic sum of these two values15. Roberts (1983) also presents the analysis of Stevens et al. (1971) to estimate the rise of the surface temperature of the roll, in terms of the bulk temperature of the roll, the time of contact and the thermal properties of the roll material: its thermal conductivity, its thermal diffusivity and the conductance. The calculations pre- sented show that the rise of the surface temperature of the roll is somewhat less than those of the experiments of Stevens et al. (1971). The rise of the roll’s surface temperature may be estimated by the relation devel- oped by Stevens et al. (1971). The equation relates the roll’s surface temperature (Troll), the roll’s temperature some distance below the surface (T0), the strip’s temper- ature at the entry (Tstrip) to the time of contact (t), the density and to several thermal parameters of the roll material. The formula is written in the form (Roberts, 1983) rffiffiffiffiffiffiffiffiffi T 2 T t roll 0 5 α ð5:16Þ Tstrip 2 T0 kρcp where α is the heat transfer coefficient at the roll/strip interface in W/m2 Kandk is the thermal conductivity of the roll material in W/m K. Roberts (1983) writes that the magnitude of T0 used in the calculations is not a critical variable. Typical calculations may be performed to appreciate the validity of the assumptions made above concerning the rise of the temperature of the roll’s surface. The thermal
13The numbers are taken from Roberts (1983). 14The experiments of Tiley and Lenard (2003) on an experimental mill indicate that the roll’s surface temperature may rise by as much as 200 C. 15Note that in the example only two phenomena were considered: temperature rise due to plastic work done and temperature loss due to conduction. A more advanced thermal treatment needs to consider the temperature changes associated with radiation, convection and the metallurgical events. Mathematical and Physical Modelling of the Flat Rolling Process 67 conductivity, in W/m K, is dependent on the temperature, as indicated by Pietrzyk and Lenard (1991): 22:025T k 5 23:16 1 51:96 exp ð5:17Þ 1000 where T is in K. When the time of contact is 0.01 s, and the heat transfer coeffi- cient, the specific heat and the density are as in the example above, the conductiv- ity is calculated to be 28 W/m K by Eq. (5.17), the strip is at a temperature of 900 C, the roll’s bulk temperature is 100 C, and the roll’s surface is predicted to rise by 400 C, close to the measurements of Stevens et al. (1971).
5.3 1D Models
5.3.1 The Classical Orowan Model The 1D models are all based on the equilibrium method in which a slab of the deforming material is isolated and a balance of all external forces acting on it is used to develop a differential equation of equilibrium16. Since the original treat- ment, published by Orowan (1943), is often considered to be the industry standard and other models’ predictions are usually compared to its calculations, it is worth- while to review it in some detail. A detailed review and a thorough critical discus- sion of the method have also been given by Alexander (1972)17, who published a computer program in FORTRAN to analyse the flat rolling process. The model is based on the static equilibrium of the forces in a slab of metal undergoing plastic deformation between the rolls; see Figure 5.2. The forces due to the roll pressure, distributed along the contact arc, the interfa- cial shear stress and the stresses in the longitudinal and the transverse directions, form the force system, the equilibrium of which in the direction of rolling leads to the basic equation of balance. The assumption that planes remain planes allows this relation to be a 1D, ordinary differential equation of equilibrium in terms of the dependent variables: the roll pressure p, the strip thickness h, the radius of the deformed roll R0, the interfacial shear stress τ, the stress in the direction of rolling σx and the independent variable x, indicating the distance in the direction of rolling, measured from the line connecting the roll centres:
dðσ hÞ dh x 1 p 7 2μp 5 0 ð5:18Þ dx dx
16If inertia forces are expected to be significant contributors to the stresses, equations of motion need to be developed, equating the sum of all forces to the product of the mass and the acceleration. This con- cept is dealt with in Section 5.5. 17Note that Alexander indicated the existence of compressive stresses in the direction of rolling, acting on the isolated slab. In Figure 5.2 these stresses are shown as tensile and the boundary conditions are expected to determine if they are tensile or compressive. 68 Primer on Flat Rolling
y φ R'
pR' dφ Work roll τR' dφ
Rolled strip h+dhh (σ+dσ)(h+dh) σh x hexit h dx entry Slab
Figure 5.2 The schematic diagram of the rolled strip and the roll, showing the forces acting on a slab of the deforming material. where the 7 sign indicates that the equation above describes the conditions of equilibrium between the neutral point and the entry (when using the negative sign), as well as between the neutral point and the exit (when using the positive sign). In fact, Eq. (5.18) is composed of two independent, ordinary, first-order differential equations, containing four dependent variables, σx; p and h, all of which depend on R0 in turn in addition to the coefficient of friction. The interfacial shear stress has already been replaced by the product of the coefficient of friction and the normal pressure in Eq. (5.18), as suggested by the Coulomb Amonton formulation. The necessary additional independent equations are obtained from the theory of plasticity and the geometry of the deformation zone. These include the Huber Mises criterion of plastic flow, relating the stress components in the direction of rolling and perpendicular to it to the metal’s flow strength. With the assumption of plane-strain plastic flow, the criterion becomes:
σx 1 p 5 2k ð5:19Þ where k designates the metal’s flow strength in pure shear. The other variable, the strip thickness, can be obtained from geometry:
x2 h 5 h 1 2R0ð1 2 cos φÞ h 1 ð5:20Þ 2 2 R0 The approximate formula is valid as long as the angles are much smaller than unity, true in the case of thin plate and strip rolling. The radius of the flattened roll is obtained using the original Hitchcock equation, given above; see Eq. (5.3). In order to integrate Eq. (5.18), the metal’s resistance to deformation is to be described and the interfacial shear stress needs to be given, usually as a function of the coefficient of friction and the roll pressure
τ 5 μp ð5:21Þ Mathematical and Physical Modelling of the Flat Rolling Process 69 as was done already in Eq. (5.18). Substituting Eq. (5.19) into Eq. (5.18) leads to
dp p 2k dh dð2kÞ 6 2μ 5 1 ð5:22Þ dx h h dx dx which, with the use of Eq. (5.20) and an expression for 2k see Eqs. (5.23) and (5.24) is ready to be integrated. The computation to determine the roll separating force and the roll torque begins with the integration of the equilibrium equations for the roll pressure. Starting at 5 σ 2 2 τ φ entry, using the appropriate boundary conditions [pentry entry 2kentry tan 1], φ 2 where 1 is the roll gap angle and the ve sign of the coefficient of the friction term, integration leads to a curve for the roll pressure. The next step is integration from the exit, and again, using the appropriate boundary condition there [pexit 5 2kexit 2 σexit] and now the 1 sign leads to another curve for the pressure distribution. Two curves thus produced give the pressures exerted by the rolled strip on the roll, referred to as the friction hill. (Note that the subscripts “entry” and “exit” in the parentheses refer to the values of the designated parameters at those locations. The terms σentry and σexit indicate the front and the back tensions, respectively. In most laboratory mills or a single-stand roughing mill, these are not applied.) The location of the intersection of the curves is defined as that of the neutral point, at which the roll surface velocity and that of the strip are equal and no rela- tive movement between them takes place. Further integration of the roll pressure distribution over the contact, from entry to the exit, leads to the roll separating force. Integration of the product of the roll radius and shear forces from the entry to the exit leads to the roll torque. The necessity of accounting for the flattening of the work roll makes an iterative solution unavoidable. In the first set of calcula- tions, rigid rolls are assumed to exist, i.e. R 5 R0. In the second iteration, the roll separating force, that has just been determined, is used to calculate the flattening of the roll employing Hitchcock’s relation (see Eq. (5.3)) and, using the radius of the flattened roll, a new roll force is obtained. The iteration is stopped when a pre- determined tolerance level on the roll force is satisfied. Corrections for the contri- bution of the elastic entry and exit regions can also be included in Orowan’s model; for the details, see Alexander (1972). Equation (5.18) may be used to analyse the cold, warm or hot flat rolling pro- cesses, the difference being the manner of the description of the term 2k, the metal’s resistance to deformation. If cold rolling is considered, one may follow Alexander (1972) and use the relation 2 2 h n1 2k 5 pffiffiffi Y 11 pffiffiffi Bln entry ð5:23Þ 3 3 h pffiffiffi where the 2= 3 multiplier corrects the stress strain relation, obtained in a uniaxial tension or compression test, to be applicable for the analysis of the plane-strain flow 70 Primer on Flat Rolling problem of flat rolling. If hot rolling is to be studied, the resistance to deformation needs to be expressed in terms of the strain rate, at the least. A form often used is
2 2k 5 pffiffiffi Cε_m ð5:24Þ 3 where C and m need to be determined in independent tests. In a more advanced approach, the equation should include several more parameters. These will be dis- cussed further in Chapter 8.
5.3.2 Sims’ Model Sims (1954) takes advantage of the fact that the angles in the roll gap are small when compared to unity, leading to the approximations sin φ tan φ φ and 1 2 cos φ φ2=2. He also assumes that the product of the interfacial shear stress and the angular variable is negligible when compared to other terms and that stick- ing friction, i.e. τ 5 k, is present in the contact between the roll and the strip18. These simplifications, in addition to assuming that the material of the rolled metal is characterized as rigid-ideally plastic, allow for a closed-form integration of the equation of equilibrium, and the roll separating force per unit width is obtained as
Pr 5 2kLQp ð5:25Þ an equation that is similar to that of Schey, see Eq. (5.1).InEq. (5.25) the term 2k stands for the yield strength of the metal,pffiffiffiffiffiffiffiffiffiffiffiffi obtained in plane-strain compression. The 0 contact length is as given above, L 5 R Δh, and the multiplier Qp is dependent on the ratio of the radius of the flattened roll, the exit thickness of the rolled strip and the thickness of the strip at the neutral point, Y: " sffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi sffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi rffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi π 2 π 2 0 1 r 21 r 1 r R Y Qp 5 tan 2 2 ln 2 r 1 2 r 4 r hexit hexit : sffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi # ð5 26Þ 1 1 2 r R0 1 1 ln 2 r hexit 1 2 r where the thickness of the strip at the neutral point is found by equating the φ magnitudes of the roll pressures there. The location of the neutral point, n,is obtained from rffiffiffiffiffiffiffiffi rffiffiffiffiffiffiffiffi rffiffiffiffiffiffiffiffi rffiffiffiffiffiffiffiffiffiffi π 0 0 0 2 5 R 21 R φ 2 R 21 r : lnð1 rÞ 2 tan n tan ð5 27Þ 4 hexit hexit hexit 1 2 r
18Note that the sticking friction assumption is not appropriate, even in hot rolling. The coefficient of fric- tion, as a function of the temperature, will be discussed in Chapter 9. Mathematical and Physical Modelling of the Flat Rolling Process 71
In the above relations r stands for the reduction in the pass, expressed as a fraction. Because of its simplicity, Sims’ model often forms the basis of on-line roll force models for hot rolling in the steel rolling industry, although it is adapted for the par- ticular mill on which it is used. The mathematical model of Caglayan and Beynon (1993), called SLIMMER, makes use of Sims’ approach and combines it with sev- eral relationships that describe the microstructural evolution of the rolled metal. The model developed by Svietlichnyy and Pietrzyk (1999) for on-line control of hot plate rolling also uses Sims’ model to calculate the roll separating forces.
5.3.3 Bland and Ford’s Model In addition to the small angle assumption, Bland and Ford (1948) assume that the roll pressure equals the stress in the vertical direction and since the difference between them is a function of the cosine of very small angles, the error is not large, especially in cold rolling where roll diameters are usually much larger than the thickness of the strip. As with Sims’ model, this allows a closed-form solution to be obtained. The roll force is then expressed: () ðφ ðφ n 1 ÂÃ 0 h h Pr 5 2kR expðμHÞdφ 1 exp μðHentry 2 HÞ dφ ð5:28Þ h φ h 0 exit n entry where H is given by rffiffiffiffiffiffiffiffi rffiffiffiffiffiffiffiffi R0 R0 H 5 2 tan21 φ ð5:29Þ hexit hexit
The location of the neutral point is calculated by rffiffiffiffiffiffiffiffi rffiffiffiffiffiffiffiffi h H h φ 5 exittan n exit ð5:30Þ n R0 2 R0 and the term Hn is determined by the formula
Hentry 1 hentry Hn 5 2 ln ð5:31Þ 2 2μ hexit where the subscripts indicate the conditions at the entry orp atffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi the exit. The angular φ 5 2 = 0 distance at the entry, the roll bite, is obtained by 1 ðhentry hexitÞ R .The Bland and Ford model is often used in the rolling industry in the analysis and the control of the cold rolling process. Puchi-Cabrera (2001) used the Bland and Ford approach in a different way. He considered cold rolling of an aluminium alloy, from a thickness of 6 mm to a final thickness of 0.012 mm. The industrial practice is to roll the alloy in three stages. 72 Primer on Flat Rolling
In the first stage the work piece is reduced from 6 to 0.68 mm in four passes. In the second stage the alloy is annealed and in the third stage it is reduced, in several passes, to the 0.012 mm thickness. In each of the rolling passes the reduction, and hence the rolling load, is reduced and the mill’s full capability is not utilized. The author considered the effects of maintaining a constant load during each of the multi-stage reductions and concluded that this may create clear advantages in terms of productivity, product quality and roll life.
5.4 Refinements of the Orowan Model
Introducing the equations of elasticity to analyse the elastic entry and exit regions, as well as the deformation of the work roll, leads to a somewhat more fundamental model of the flat rolling process (Roychoudhury and Lenard, 1984). The model is still based on the equilibrium method the Orowan approach and it is applica- ble when the roll radius to strip thickness ratios are much larger than unity, allow- ing for the assumption of homogeneous compression in the roll gap. The differences between this model and the Orowan approach are as follows:
G Hitchcock’s equation is replaced by a 2D elastic analysis of roll deformation. The rolls are assumed to be solid cylinders initially, which deform under the action of non-symmetrical normal and shear stresses during the pass. Two-, four- or six-high roll arrangements can be treated by the analysis, depending on how keeping the work rolls in balance is described mathematically. The 2D theory of elasticity, coupled with the elastic plastic 1D treatment of the rolled strip, is used to determine the contour of the deformed roll. G The elastic loading and unloading regions in the rolled strip at the entry and exit, respec- tively, are analysed using the 1D theory of elasticity. The locations of the elastic/plastic interfaces at both locations then become parts of the unknowns and are determined during the solution process by using the Huber Mises criterion of plastic flow. G The equation of equilibrium is written using the variable in the direction of rolling as the independent variable. The roll gap is divided into a finite number of slabs each of which is assumed to be either elastic or ideally plastic. As the metal is deformed and strain hard- ens during the rolling process, the flow strength of each slab is changed accordingly. As well, the roll pressure and the interfacial shear stresses are expressed in terms of Fourier series. A closed-form solution for each slab is thus obtained. Assembling the slabs is accomplished by enforcing horizontal equilibrium, leading to the complete solution for the pressure distribution and hence to the roll separating force and the roll torque. G The roll pressures and the interfacial shear stress distributions thus obtained are then used to calculate the contour of the deformed roll, using the Fourier series and the biharmonic equation. G The current shape of the flattened work roll is used to determine the roll pressure, interfa- cial shear stress, the roll separating force and the roll torque, which are employed to re- calculate the roll contour. G The iteration is continued until satisfactory convergence of the roll force is reached. Since the details of the model have been published (Roychoudhury and Lenard, 1984), only a brief exposition is given below. The schematic diagram from which the equation of equilibrium is derived, as shown in Figure 5.3, differs from the one Mathematical and Physical Modelling of the Flat Rolling Process 73
y x
y = f(x) R´ C
p μp h h 1 1e h h2e T1 T2 Elastic compression Elastic recovery
Figure 5.3 Schematic diagram of the rolled metal and the roll, used in the model of Roychoudhury and Lenard (1984). used by Orowan (1943) and Alexander (1972) in that the roll contour is taken to be an unknown function y 5 f(x), to be determined as part of the computations. The balance of the forces of a slab of the rolled metal is now derived using the direction of rolling as the independent variable, leading to d dy dy hp2 2k 7 τ 5 2 p 6 τ ð5:32Þ dx dx dx and as before, the positive algebraic sign in front of the interfacial shear stress indi- cates the region between the neutral point and the exit and the lower sign desig- nates the region between the neutral point and the entry. The thickness of the strip, using C to designate half the distance between the two centres of the two roll-neck bearings, is
h 5 2ðy 1 CÞð5:33Þ
Using the coordinate system in Figure 5.3, the term y in Eq. (5.33) becomes a nega- tive number. Expressing the roll contour of one particular slab as a straight line, defined by
y 5 ax 1 b ð5:34Þ and, as mentioned above, assuming that each slab is either elastic or is made of an ideally plastic metal simplifies Eq. (5.32), and closed-form integration, slab by 74 Primer on Flat Rolling slab, is now possible. The constants of integration are determined by assembling the slabs such that horizontal equilibrium is assured. The elastic regions at the entry and exit are also explicitly accounted for in the model. The equation of equilibrium, Eq. (5.32), is valid in those regions as well. Combining them with the 1D plane-strain form of Hooke’s law leads to the stress distributions in the elastic loading and recovery regions. Using the Huber Mises yield criterion, and matching the elastic and the plastic stress distribution, the loca- tions of the elastic plastic boundaries are determined. The analysis requires the explicit determination of the constants a and b, defin- ing the roll contour at each slab. By expressing the roll pressures and the interfacial shear stress distributions in terms of Fourier series and analysing roll flattening fol- lowing Michell’s 2D elastic treatment (Michell, 1900), the roll separating forces are obtained as " ð ð xn dy xexit dy Pr 5 p 1 1 μ dx 1 1 1 μ dx xentry dx xn dx : ð ð # ð5 35Þ xn dy xexit dy 1 μ 2 dx 1 μ 1 dx xentry dx xn dx and the roll torques by ð ð xn dy dy xexit dy dy M=25p x2y 1μ y1xy dx2p x2y 2μ y1x dx xentry dx dx xn dx dx ð5:36Þ
5.4.1 The Deformation of the Work Roll The critique of Roberts (1978) concerning the use of Hitchcock’s formula to calculate the radius of the flattened but still circular work rolls is well accepted. The elastic flattening of the rolls has been treated by Jortner et al. (1959). The authors considered the effect of a force on the deflection of a solid cylinder and showed that the rolls don’t, in fact, remain circular in the deformation zone. Non- circular roll profiles have also been developed by Grimble (1976) and Grimble et al. (1978). The problem of the deformation of the work roll is treated here by assuming that the work roll is a solid cylinder, subjected to non-symmetrical loads. The load- ing diagram is shown in Figure 5.4 (Roychoudhury and Lenard, 1984) where the roll pressure is designated by pðϕÞ and the interfacial shear stress by τðϕÞ. The roll is kept in equilibrium in one of two ways. If there is a back-up roll, the pressure between the two rolls will keep the work roll in its place. If a two-high mill is con- sidered, the roll centre is taken to be stationary, achieved by letting 2ξ 5 π, where 2ξ is the extent of the pressure distribution of the now imaginary back-up roll. Mathematical and Physical Modelling of the Flat Rolling Process 75
∞ φ = + φ + φ Rb ( ) R0 ∑[Rancos(n ) Rbnsin(n )] n=1
ξ ξ
R
β β E a a 1 1 ⎛πφ ⎞ τ ()φ = G sin⎜ ⎟ F ⎝ 2β ⎠ G
⎛πφ ⎞ p(φ) = −E − F cos⎜ ⎟ ⎝ 2β ⎠
Figure 5.4 The loading diagram of the work roll, showing the roll pressure and the interfacial shear stress distributions in addition to the forces that keep the roll in equilibrium (Roychoudhury and Lenard, 1984).
The stress distribution in any problem of linear elasticity should satisfy the biharmonic equation, which in the 2D cylindrical coordinates are δ 1 δ 1 δ2 δ2φ 1 δφ 1 δ2φ 1 1 1 1 5 0 ð5:37Þ δr2 r δr r2 δϕ2 δr2 r δr r2 δϕ2 where the stress components are defined in terms of the Airy stress function, φ,as
1 δφ 1 δ2φ σ 5 1 ð5:38Þ r r δr r2 δϕ2
δ2φ σϕ 5 ð5:39Þ δr2 76 Primer on Flat Rolling and δ 1 δφ τ ϕ 52 ð5:40Þ r δr r δϕ
Following Michell (1900), the stress and the strain distributions may be calculated using biharmonic functions
XN φ 5 c r2 1 d r3 sin ϕ 1 d r3 cos ϕ 1 ða rn 1 b rn12ÞsinðnϕÞ 0 1 2 1n 1n : n52 ð5 41Þ n n12 1ða2nr 1 b2nr ÞcosðnϕÞ where the constants a1n; a2n; b1n; b2n; c0; d1 and d2 need to be determined such that the stress boundary conditions at r 5 R are satisfied:
σr 5 pðϕÞ and τrϕ 5 τðϕÞð5:42Þ
The coefficients in Eq. (5.41) can be determined by representing the normal and the shear loading on the roll’s surface in terms of Fourier series
XN pðϕÞ 5 pa0 1 ½pan cosðnϕÞ 1 pbn sinðnϕÞ ð5:43Þ n51 and
XN qðϕÞ 5 qa0 1 ½qan cosðnϕÞ 1 qbn sinðnϕÞ ð5:44Þ n51 where the coefficients may be determined by the Euler formulas19. The roll flattening, thus determined, was tested in a simple experiment. The side of the 125 mm radius work roll was fitted by two strain gauges and the strains dur- ing rolling of commercially pure aluminium alloys were measured20. These were compared to the calculated strains. The results are shown in Figure 5.5, plotting the radial strains against the angular distance around the work roll, using the data from the strain gauge near the edge, at 120 mm from the roll’s centre. It is observed that the predicted strains by the 2D elastic analysis compare well to the measurements.
5.5 The Effect of the Inertia Force
The metal to be rolled enters the roll gap at some velocity, which is usually lower than the surface velocity of the roll. As the thickness is reduced, the width remains
19The detailed development of the 2D analysis of Michell (1900) is given by Pietrzyk and Lenard (1991). 20The 50 mm wide, 2 mm thick aluminium strips were reduced by 5% in the tests. Mathematical and Physical Modelling of the Flat Rolling Process 77
–1000 Analytical –800 Experimental
–600 6 ×10
r –400 ε Roll separating force 1800N r R –200 / = 0.957
0 100 0 πππ π π π π 3 5 3 7 π 8482 848
Figure 5.5 The calculated and measured radial strains of the work roll (Roychoudhury and Lenard, 1984). unchanged and the length grows; the metal accelerates and exits from the roll gap at a velocity larger than that of the roll under most circumstances. Hence, there exists a force due to this acceleration and its effect on the rolling variables needs to be established. While 1D models usually ignore this contribution, the finite- element models usually include it in their analyses. In what follows the validity of these approaches will be discussed and the potential effect of the mass 3 accelera- tion term on the roll force, etc. will be given in numerical terms.
5.5.1 The Equation of Motion The effects of the inertia forces on the rolling process have rarely been analysed explicitly. In what follows, this effect will be considered in some detail. Equating the forces acting on a slab of the material in the roll gap to the product of the mass of the slab and its acceleration, and using the distance in the direction of rolling as the independent variable, leads to
dðσ hÞ dh ma x 1 p 7 2μp 5 ð5:45Þ dx dx dx where the mass/unit width is given by m 5 h dx ρ, the density is designated by ρ and the acceleration is a. TheleftsideofEq. (5.45) is, of course, identical to that of Eq. (5.18). In order to develop a relation for the acceleration of the slab, use is made of mass conservation, which requires that dðvhÞ 5 0, leading to a 5 dv=dt 52ðv=hÞðdh=dtÞ. The time derivative of the strip’s thickness may be 2 0 obtained from the simplified version of Eq. (5.20), h 5 h2 1 x =R , written in terms of x, the variable along the direction of rolling, in the form dh=dt 5 2xv=R0, where the strip velocity, v, in terms of the roll’s surface velocity and the thickness at the neutral 78 Primer on Flat Rolling point, is given as v 5 vrhn=h. Substituting the above into Eq. (5.45) along with the Huber Mises criterion of plastic flow yields the differential equation of motion:
dp p 2k dh dð2kÞ 2xρ ðv h Þ2 6 2μ 5 1 1 r n ð5:46Þ dx h h dx dx R0 h3
It is now possible to estimate the orders of the magnitudes of the terms of Eq. (5.46). The magnitude of the roll pressure is in the order of several hundred MPa. The magnitude of the last term of the equation, for any reasonable set of roll- ing parameters, is less than 1% of that.
5.5.2 A Numerical Approach In another, simpler approach, the inertia force acting on the whole of the mass in the deformation zone can be determined. The acceleration is then given by 5 2 =Δ a ðvexit ventryÞ t and thep timeffiffiffiffiffiffiffiffiffiffiffi taken for a cross-sectional plane to travel from Δ 5 0Δ = the entry top theffiffiffiffiffiffiffiffiffiffiffiffi exit is t R h vr. The mass of the metal in the roll gap is 0 m 5 ρwhave R Δh so the inertia force is
FI 5 ρwhavevrðvexit 2 ventryÞð5:47Þ
For the inertia force to be a significant contributor in the analysis of permanent deformation, the stress it creates over the average cross-section of the rolled metal should be similar in magnitude to the yield strength. From Eq. (5.47) equate the stress created by the inertia force to the yield strength:
FI σyield 5 5 ρvrðvexit 2 ventryÞð5:48Þ whave
For any realistic set of numbers, the difference between the exit and entry veloci- ties becomes unrealistically high, underscoring the conclusions drawn above: the contribution of the inertia force may be safely ignored. To get a numerical esti- mate, take a steel whose density is 7850 kg/m3 and let a 1 m diameter roll have a rotational speed of 100 rpm, leading to a roll surface velocity of 5.24 m/s. Let the entry thickness be 5 mm, at a velocity of 5 m/s. The exit velocity is then, from mass conservation, 12.5 m/s. Substituting these numbers in the right side of Eq. (5.48) leads to a stress, due to inertia effects alone, of 0.31 MPa, clearly negli- gible in comparison to the magnitudes of all other stress components.
5.6 The Predictive Ability of the Mathematical Models
The decision to be made when choosing a mathematical model to analyse the flat rolling process is not an easy one. In what follows, it is assumed that the objective of the analysis is to predict only some of the rolling variables, namely the roll Mathematical and Physical Modelling of the Flat Rolling Process 79 separating force. The predictive abilities of some of the models discussed above will be presented and critically discussed. The experimental data, developed by McConnell and Lenard (2000), will be used. In that project, low-carbon steels were rolled at various rolling speeds and to various reductions, using low viscosity oils for lubrication. The roll separating forces and the roll torques were measured. In the calculations that follow, the roll separating forces are considered and the predictive abilities of three models those given by Schey (2000), Bland and Ford (1948) and Roychoudhury and Lenard (1984) are compared. The results of the comparison are shown in Figure 5.6 in terms of the ratios of the measured and the calculated roll forces for each of the methods of calculation, as functions of the rotational speed of the roll. The reductions vary from a low of 14% up to 50% in the rolling passes. The data given in the figure need to be discussed very carefully and in some detail. The essential information for modelling includes the material’s resistance to deformation and the coefficient of friction. The former was given by McConnell and Lenard (2000) for the steel used here, obtained in traditional uniaxial tension : tests, as σ 5 150ð11234εÞ0 251 MPa. The latter was determined by inverse calcula- tions, matching the measured separating forces to those calculated by the approach of Roychoudhury and Lenard (1984). This is evident in Figure 5.6, as the triangles of Roychoudhury and Lenard are always very close to unity, as expected, of course. The magnitude of the coefficient of friction, thus obtained, was then used in the two other methods of calculations. The diamonds of the Bland and Ford (1948) approach are approximately 20% over unity. The crosses of the Schey (2000) tech- nique are not very consistent. It needs to be pointed out that when judging a model for its predictive ability, consistency is much more important than accuracy, since predictions with low standard deviation can always be adjusted by the use of care- fully determined factors.
1.50 Figure 5.6 Comparison of the predictive capabilities of three simple models for cold rolling of low-carbon steel strips. 1.25 calculated F / 1.00 measured F 0.75 Schey's method Bland and Ford's method Roychoudhury and Lenard's method 0.50 0 1000 2000 3000 Roll speed (mm/s) 80 Primer on Flat Rolling
Both of these approaches Bland and Ford’s and Schey’s could have been used to determine the coefficient of friction, in an inverse manner, of course. Both would have yielded values for μ that would vary broadly and would be quite differ- ent from those, used in Figure 5.6, indicating that the inverse method for the deter- mination of the coefficient may not be the most suitable approach. Instead, independent experiments, to be discussed in Chapter 9, are recommended.
5.7 The Friction Factor in the Flat Rolling Process
The referee of a manuscript of the present author and his student (Lenard and Barbulovic-Nad, 2002) questioned the use of the coefficient of friction in bulk form- ing processes, stating correctly that at high normal pressures the physical meaning of μ is lost. The rebuttal, which was accepted by the editor, is quoted below:
It is realized that the coefficient of friction obtained by inverse modelling, while it may be close to the actual value, is in fact an effective one. Further, while applica- tion of the traditional definition of the coefficient, as the ratio of the tangential to the normal forces, in metal forming operation has been questioned, it still remains a parameter in widespread use. As shown by Schey (2000), μ reaches a maximum as the normal stresses increase. This condition, while it may be reached during dry con- tact, is not likely to be observed when forming occurs in the boundary or mixed lubrication regimes. Azarkhin and Richmond (1992) also show that the friction factor will be less than unity, even when adhesion is the main cause of frictional resistance.
Nevertheless, the comments of the referee were taken seriously and they gave the impetus to develop a model of flat rolling, using the friction factor, instead of the coefficient of friction. Pashley et al. (1984) examined the three most significant factors that contribute to surface interactions involving adhesion: the area of real contact, the interfacial bond strength and the mechanical properties of the interface. They used a tungsten tip and a nickel flat, the tungsten being nearly 10 times harder than the nickel. When the sur- faces were clean, the junction failed at a stress level roughly equal to the yield strength of the metal. Li and Kobayashi (1982) included the effect of the relative velocity of the sliding surfaces in their formulation of the frictional model. A similar model is used in Elroll21, a finite-element software developed by Pietrzyk (1982) in which the μ coefficient of friction is defined in terms of a constant value, 0, the relative velocity of the roll and the strip, Δv,andaconstant,a, which is chosen to be 1023, in the form
μ 2 Δv 5 21 ð : Þ μ π tan 5 49 0 a
21Elroll, a finite-element program that analyses the flat rolling process has been developed in the Department of Modelling and Information Technology AGH in Krako´w, Poland. The distributor of the software may be reached by e-mail: [email protected]. Mathematical and Physical Modelling of the Flat Rolling Process 81
Most commercially available finite-element software packages allow the user to choose the manner in which friction is to be modelled. A random search on the Internet yielded a 1994 newsletter from the MARC Corporation, giving an equation for the friction force:
2 Δv f 5 μf tan21 ð5:50Þ t n π C where μ is the coefficient of friction, fn is the normal force and C is a constant. Another relationship for the interfacial shear stress in terms of the relative veloc- ity of the roll and the rolled strip was given by Gratacos et al. (1992):
σ Δv jτj 5 m pfmffiffiffi pffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi ð5:51Þ 3 Δv2 2 K2 where K is identified as the “regularization parameter for the friction law”, given later as a very small number, in the order of 0.001. An interesting expression was presented by Nadai (1939) for the interfacial shear stress as a function of the rela- tive velocity of the strip and the roll, the lubricant’s viscosity and the thickness of the oil film:
ηðv 2 v Þ τ 5 strip r ð5:52Þ hfilm;ave where the thickness of the oil film is to be the average over the rolling pass. A third possibility in modelling friction is presented by Carter (1994) by relating the fractional shear strength of the contacting interface to the normal component of the deviatoric stress, through a “constant of proportionality”, identified as “much like the coefficient of friction”. Carter also states, unfortunately without referencing the information, that in simple compression “the fracture strength of the junction is close to the shear strength of the softer material”. Regardless of the manner in which friction is to be modelled, some difficulties, uncertainties and unknowns will always remain. In what follows, the friction factor is used in developing a 1D model of the flat rolling process, partially as the result of the comment of a reviewer of one of the present author’s recent manuscripts, ques- tioning the use of the coefficient of friction in the flat rolling process. Aiding in making the decision to use the friction factor, in spite of the lack of precise knowl- edge of the magnitude of “k”, the shear strength of the interface, are three factors. One is consideration of the pressure sensitivity of lubricants, which, for an SAE 10 W oil, is given as 0.0229 MPa21 by Booser (1984) who also gives the viscosity as 32.6 mm2/s. If the roll pressure is 800 MPa, not an unreasonable magnitude when cold rolling steel, the Barus equation (see Eq. (9.48)) gives the viscosity at that pres- sure as 2.9 3 109 mm2/s. This number, while possibly unrealistically high, indicates that shearing the lubricant at that pressure may require as much of an effort as shear- ing the metal. The other is the comment, referred to above, concerning the level of 82 Primer on Flat Rolling stress at which the tungsten nickel junction failed (Pashley et al., 1984) and the third, also mentioned above, is the conclusion that ploughing was the major frictional mechanism (Lenard, 2004; Dick and Lenard, 2004) when a sand-blasted roll was used. Carter (1994) and Montmitonnet et al. (2000) reinforce this last factor by indi- cating that ploughing may be as important as adhesion in understanding frictional resistance. The objectives are then:
G to develop a 1D model of the flat rolling process using the friction factor; G to determine the dependence of the friction factor on speed and the reduction by using data, developed earlier on cold rolling of steel strips (McConnell and Lenard, 2000); G to test the predictive capability of the model by comparing the predictions to experimen- tal data; G to develop a correlation of the coefficient of friction and the friction factor.
5.7.1 The Mathematical Model The choice of the level of complexity in mathematical modelling of the flat rolling process depends on the objectives of the researchers. The comments in the last para- graph of the concluding chapter of Pietrzyk and Lenard (1991) are still valid: if the aim is to analyse mechanical events in strip rolling, where the roll diameter/strip thickness ratio is large, a 1D treatment is sufficient. This is followed in the present analysis in which the usual simplifying assumptions of previous workers are also employed. These include the assumptions of rigid rolls, homogeneous compression, a rigid-plastic material which remains isotropic and homogeneous as the rolling pro- cess continues. The angles are taken as small when compared to unity. As well, iner- tia forces are small in comparison to other forces and are therefore ignored. The usual, 1D schematic diagram of the flat rolling process is used and the bal- ance of forces in the direction of rolling on a slab of the rolled metal then leads to the well-known relation
dðσ hÞ dh x 1 p 2 2τ 5 0 ð5:53Þ dx dx where σx is the stress in the direction of rolling and p is the roll pressure. In simplifying Eq. (5.53), the Huber Mises flow criterion, σx 1 p 5 2k, is used, 2 the strip thickness is taken in terms of the independent variable, h D hexit 1 x =R, and the interfacial shear stress is defined by the friction factor, τ 5 mk. The shear strength of the softer material, the rolled steel, is taken as k and as usual, 0 # m # 1. A first-order ordinary differential equation for the roll pressure is then obtained:
dp 2k 5 ð 2 Þð: Þ 2 2x mR 5 54 dx hexitR 1 x where the friction factor, m, is to be expressed in terms of the significant variables and parameters. Equations (5.49) (5.52) expressed the coefficient of friction or the friction stress in various forms, as functions of the relative velocity of the strip with Mathematical and Physical Modelling of the Flat Rolling Process 83 respect to the roll, Δv, acknowledging the well-known speed dependence of the fric- tional resistance, in addition to the viscosity, the thickness of the oil film and several constants. Following these but also recognizing the dependence of friction on the nor- mal stresses, the friction factor is now written as dependent on both load and speed:
5 2 2 2 1 21 Δ = : m aðx xnÞp b tan ð v qÞð5 55Þ where a and b are constants to be determined and q is a constant, taken arbitrarily to be 0.1. The relative velocity is given in terms of the location of the neutral point, xn, and the surface velocity of the roll, vr
x2 2 x2 Δ 5 n ð : Þ v vr 2 5 56 hexitR 1 x allowing the friction factor to vary from the point of entry to exit. Since the numer- ator in Eq. (5.56) changes algebraic sign as x varies, the friction factor also changes sign at the neutral point. At this stage of the calculations, the constants a and b in Eq. (5.55) and the location of the neutral point, xn, are not known. The computations start by integrating Eq. (5.54), using a Runge Kutta approach, for the roll pressure, starting at the entry with the appropriate boundary condition, and using assumed values for all three unknowns, a, b and xn. The boundary condition at the exit is satisfied by adjusting the location of the neutral point. Integral of the roll pressure distribution, thus obtained, over the contact length, is the roll separating force. By adjusting the constants a and b in Eq. (5.55) for the friction factor, repeating the integration, the calculated and the measured roll separating forces are compared and when satisfactory convergence is reached, the constants a and b and the location of the neutral point are deemed to have been determined. At this point uniqueness of the predictions is not considered. The friction factor, thus determined, varies from a negative value at the entry to the neutral point where it reaches zero. Beyond that the factor becomes positive. Its average value, mave, is indicative of frictional resistance. The roll torque is determined using the power, W_ , required to roll the metal. The power is obtained as the sum of the power for internal deformation and friction: ð ð 2σ W_ 5 pfmffiffiffi ε_ dV 1 2 τ Δv dS ð5:57Þ 3 V S where the friction stress is as given above (τ 5 mk) and the torque is then, for both rolls,
RW_ M 5 ð5:58Þ vr
The closeness of the calculated and measured roll torques indicates that both con- stants a and b have been determined correctly. 84 Primer on Flat Rolling
5.7.2 Calculations Using the Model The predictive abilities of the model are tested in two instances. First, the roll sepa- rating forces are compared to those measured in earlier cold rolling experiments, followed by comparing the calculated and measured roll pressure distributions.
5.7.2.1 Cold Rolling of Steel Selected portions of the data, obtained by McConnell and Lenard (2000), are used to determine the friction factor. In that publication low-carbon steel strips, having a : true stress true strain relation of σ 5 150ð11234εÞ0 251 MPa and measuring 1 3 23 3 300 mm3, have been cold rolled, using lubricants, containing various addi- tives and having broadly varying viscosities. The rolls were made of D2 tool steel, hardened to Rc 5 63 and were of 249.8 mm diameter. Their surface roughness was Ra 5 0.2 μm. The objective was to determine the coefficient of friction by inverse calculations and by the use of Hill’s formula. The data, used in the present study, involves a lubricant with a kinematic viscosity of 19.83 mm2/s and a density of 861.6 kg/m3. The dependence of the average friction factor on the surface velocity of the roll and on the reduction is shown in Figure 5.7. As expected from previous studies, the friction factor decreases with both increasing rolling speed and reduction, affected by the same mechanisms that affected the coefficient of friction. As has been pointed out in several instances, as the speed increases, more oil is drawn into the contact, leading to lower friction; and as the loads increase, the viscosity increases, also leading to lower friction, at least in the boundary and in the mixed lubricating regimes.
1.2 Figure 5.7 The friction factor as m v ave = –1.607(red) – 0.00013 r +1.256 a function of the reduction and the roll surface velocity. 1.0 Reduction 0.8 14%
ave 0.6 m
20% 0.4 35% 46% 0.2 Cold rolling steel Viscosity = 19.83 mm2 /s 0.0 0 1000 2000 3000 Roll speed (mm/s) Mathematical and Physical Modelling of the Flat Rolling Process 85
Statistical modelling, using non-linear regression analysis, gives the dependence of the friction factor on the two process parameters, load and speed. The relation is shown in Eq. (5.59):
mave 521:607ðredÞ 2 0:00013 vr 1 1:256 ð5:59Þ where “red” is the reduction in decimals. The predictive ability of Eq. (5.59) was tested on data, not used in its determination. The data points from McConnell and Lenard (2000) were taken using a different lubricant whose viscosity was similar to the one used in developing Eq. (5.59), its value being 20.03 mm2/s. The roll surface velocity was 2308 mm/s. The results are given in Table 5.1. In Column 1 of the table the roll forces, as measured, are given. In Column 2, the forces, as calculated by the model, are shown while in Columns 3 and 4, the torques are indicated. Column 5 lists the average friction factors that resulted in the calculated forces and torques. The friction factors, as predicted by Eq. (5.59), are shown in Column 6, demonstrating that within the range of the process parameters of the experiments, the equation predicts the friction factor reasonably well. As mentioned, the calculations proceed until the measured and calculated roll separating forces and roll torques are close, to within a pre-specified tolerance. The accuracy of the computations is shown in Figure 5.8, which gives the ratios of the measured and estimated loads on the mill against the number of tests. All speeds, from 261 to 2341 mm/s, and all reductions, from 14% to 46%, are included in the figure. In general, one may conclude that a reasonable accuracy has been reached. At lower reductions the differences between the experimental data and the calcula- tions are larger, due to the deviation from homogenous compression. The numbers fall to near unity as the loads increase. McConnell and Lenard (2000) determined the coefficient of friction using Hill’s equation (see Eq. (9.26)). These values are compared to the friction factor in Figure 5.9. A linear relationship is evident and the equation
5 : μ 1 : : mave 4 425 Hill 0 01 ð5 60Þ relates the two descriptions of frictional events in the roll gap. A relationship between mave and μ, for use in forging, has been suggested by Kudo (1960) in the form
Table 5.1 A Comparison of the Predictions of the Model and That of Eq. (5.59)
Roll Force, Roll Force Roll Torque, Roll Torque mave,by mave from Measured by the Measured by the the Model Eq. (5.59) (N/mm) Model (Nm/mm) Model
6086 3927 39.39 37.38 0.214 0.17 8223 8239 45.48 45.03 0.302 0.301 7782 46.29 46.29 44.01 0.403 0.417 6871 6833 41.18 41.4 0.303 0.31 86 Primer on Flat Rolling
1.6 Figure 5.8 The accuracy of the computations: the ratio of the Cold rolling of steel measured and calculated roll force Roll speed = 261 – 2341 mm/s Reduction = 14 – 46% and torque. 1.4 Torque Load
1.2
1.0
Measured/estimated load and torque Reduction 14%26% 35% 46% 0.8 0 5 10 15 20 25 Number of experiments
1.2 Figure 5.9 The friction factor Cold rolling of steel versus the coefficient of friction Roll speed = 261 – 2341 mm/s by Hill’s formula. Reduction = 14 – 46%
) 0.8 m
Friction factor ( factor Friction 0.4
m = 4.425 μ + 0.01
0.0 0.0 0.1 0.2 0.3 Coefficient of friction ( μ)
pffiffiffi m = 3 μ 5 ave ð5:61Þ pave=σ0
Using the data of the flat rolling tests leads to the conclusion that the values of mave, predicted by Eqs. (5.59) and (5.60), are close at low speeds, underscoring the impor- tance of the speed in defining either the coefficient of friction or the friction factor. Mathematical and Physical Modelling of the Flat Rolling Process 87
1.0 Figure 5.10 The variation of the friction factor along the roll/strip Cold rolling of steel Roll speed = 2341 mm/s contact.
0.5
0.0 Reduction
Friction factor Friction 46% 35% –0.5 26%
14%
–1.0 0246810 Distance from exit (mm)
The variation of the friction factor over the contact length is shown in Figure 5.10, at a roll surface velocity of 2341 mm/s and reductions ranging from 14% to 46%. It is observed that the positive values at the exit and the negative values at the entry are quite similar in magnitude, indicating that the surfaces in contact have been well lubricated. High values of the friction factor at the exit would imply that the lubricant has not been carried through the location of maxi- mum pressure.
5.7.2.2 Distribution of the Roll Pressure at the Contact While integrating the friction hill over the contact gives realistic magnitudes of the roll separating forces, its shape has been shown to be unrealistic in several publications, starting with the work of Siebel and Lueg (1933). The friction hill is the result of the 1D models’ traditional approach, in which the intersection of the curves, obtained by integrating the equations of equilibrium from the entry and from the exit, is taken as the location of the maximum pressure and of the neutral point. In the present work the shooting approach is followed in which integration proceeds from the exit and satisfac- tion of the boundary condition at the entry indicates success. The roll pressure distribu- tion, thus obtained, is different from the sharp cusp of the usual 1D models. Comparisons of the predicted roll pressures to experimental data are given in Figures 5.11 and 5.12.InFigure 5.11, the measurements of Lu et al. (2002) are used. Employing pins and transducers in the work roll, the authors rolled low- carbon steel strips at 1000 C and reported on the distribution of the roll pressures and the interfacial shear stresses over the contact zone. One of these experiments is used here and the measured and calculated interfacial stresses are shown in Figure 5.11. The test was conducted at 33 rpm and the 20 mm thick slab was reduced by 20%. The roll separating force is read off Fig. 3 of Lu et al. (2002) as 88 Primer on Flat Rolling
150 Figure 5.11 Comparison of the Low carbon steel roll pressures, as measured by 100 Friction stress Rolled at 1000°C Lu et al. (2002) and calculated 35 rpm (412 mm/s) by the present model: hot rolling 20% reduction 50 of steel.
0
–50
–100 Roll pressure –150
–200 Roll pressure and friction stress (MPa) Lu et al. (2002) Present model –250 0 5 10 15 20 25 Distance from exit (mm)
250 Figure 5.12 Comparison of the 1100 H 14 Al roll pressures, as measured by 200 Malinowski Rolled at 100°C et al. (1993) Malinowski et al. (1993) and 12 rpm (157 mm/s) 150 Present model calculated by the present model: 39.3% reduction 100 warm rolling of aluminium. 50 0
–50 Friction stress –100 –150 Roll pressure –200
Roll pressure and friction stress (MPa) –250 –300 0 4 8 12 16 20 Distance from exit (mm)
3000 N/mm and the roll torque as 66 Nm/mm. (Note that this figure is for a roll speed of 40 rpm, and no roll force data are given for a speed of 33 rpm.) The aver- age flow strength of the steel, at the temperature and the strain rate used, is obtained by Shida’s (1969) relations (see Eqs. (8.10) (8.16)) as 124.74 MPa. Figure 5.11 indicates that the predicted pressures and shear stresses match the mea- surements quite well, indicating that use of the friction factor, as a variable in the contact zone, is quite realistic. Mathematical and Physical Modelling of the Flat Rolling Process 89
Roll pressure and interfacial shear stress distributions, obtained during warm roll- ing of 1100-H14 aluminium alloy strips, have been presented by Malinowski et al. (1993). A comparison of the predictions of the present model to the measurements by Malinowski et al. (1993) is shown in Figure 5.12. The 6.28 mm thick strip has been reduced by 39.3% at 100 C at a roll speed of 12 rpm. The average flow strength of the metal is taken as 163 MPa in the calculations. The roll separating force was measured to be 3240 N/mm. The model calculated it to be 3293 N/mm. Examination of the two figures leads to the conclusion that allowing the friction factor to vary from the entry to the exit in the roll gap leads to realistic calculations of the roll pressure distribution.
5.8 Extremum Principles
Arguably, the most powerful of the approximate techniques available to analyse metal forming processes are the extremum principles, specifically the upper bound and lower bound theories. Both theories are formulated to estimate the power required for plastic forming. The upper bound theorem can be shown to predict the power that is always more than necessary. The lower bound is designed to lead to a power that is less than needed. Hence, since the upper bound theorem is the more conservative and the more useful of the two, it will be described in some detail. In spite of the wide- spread use of these theories in the treatment of problems of metal forming, the upper bound approach has rarely been used to treat the process of flat rolling.
5.8.1 The Upper Bound Theorem The upper bound theorem is described by Avitzur (1968) as follows: Among all kinematically admissible strain rate fields the actual one minimizes the expression ð rffiffiffiffiffiffiffiffiffiffiffiffiffiffi ð ð σ 2 fm 1 J 5 pffiffiffi ε_ijε_ij dV 1 τ Δv dS 2 Tivi dS ð5:62Þ 3 V 2 SΓ Si
A strain rate field derived from a kinematically admissible velocity field is kine- matically admissible. In Eq. (5.62), J is the externally supplied power; the first inte- gral represents the power for internal deformation over the volume of the body (V), the second evaluates power due to shearing over surfaces of velocity discontinuities (SΓ) and the last term accounts for power supplied by body tractions over the surface, designated by Si. There are several concepts, mentioned above, that require careful definition. The term “kinematically admissible velocity field” implies the requirement that the velocity field must satisfy constancy of volume and all boundary conditions. The concept of velocity discontinuities is also mentioned above. As Avitzur (1968) explains, the velocity field within a deforming body need not be continuous. As shown in Figure 5.13, it is permissible to divide a body into several zones, in each of which a different set of velocities may exist. The boundary, at which the velocity 90 Primer on Flat Rolling
Discontinuity v(N) Figure 5.13 Velocity discontinuity within 1 a metal forming system. Zone 2 v1 v(N) = v(N) v(T) 1 2 1 (N) v 2 (T) v(T) ≠ v(T) v 2 1 2 v Zone 1 2 may be discontinuous, is indicated in the figure; this boundary may be located at the die/metal contact or it may be within the deforming metal. When the flat rolling process is analysed, the roll/strip contact surface is considered one of these surfaces of discontinuity. In Figure 5.13, two zones are identified, Zone 1 and Zone 2. The velocity of a N material point in Zone 1 is v1; its component normal to the discontinuity is v1 and T the component parallel to the surface of discontinuity is v1 . In Zone 2 the velocity is N v2; its component normal to the discontinuity is v2 and the component parallel to the T surface of discontinuity is v2 . As shown in the figure, continuum mechanics requires only that the velocity components normal to the surface be continuous. The tangential components need not be equal on the two sides of the surface of discontinuity, giving rise to a region of high shearing stresses. Using these concepts and the assumption that the velocity of the rolled metal in the deformation zone moves towards the inter- section of lines, tangential to the rigid rolls at the entry, the upper bound on the power, required for plastic deformation of the rolled metal, becomes (Avitzur, 1968) 2 sffiffiffiffiffiffiffiffisffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi σ 2 σ 2 4 hentry 1 hexit hentry entry exit J 5 pffiffiffi σfmvhexit ln 1 2 1 1 pffiffiffi 3 hexit 4 R hexit ð2= 3Þσ0 : 0sffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi sffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi13 ð5 63Þ m h h 1 pffiffiffiffiffiffiffiffiffiffiffiffiffiffi @ entry 2 1 2 tan21 entry 2 1A5 hexit=R hexit hexit
At the boundaries separating these zones only the normal velocity component must be continuous; the tangential component in one zone may be different than the cor- responding component on the other side of the separating surface. This velocity dis- continuity, of magnitude
Δ 5 ðtÞ 2 ðtÞ : v vI vII ð5 64Þ will create shearing stresses along the “surface of discontinuity” SΓ in Eq. (5.62) whose magnitude is given by mσ τ 5 pffiffiffi0 ð5:65Þ 3 where the magnitude of the friction factor m may be in the range 0 # m # 1. Mathematical and Physical Modelling of the Flat Rolling Process 91
The roll torque, for both rolls, may be obtained from the power as
R M 5 J ð5:66Þ U_
Tirosh et al. (1982) applied Avitzur’s (1968) upper bound approach to analyse cold rolling of viscoplastic materials at high speeds. The authors focused their attention on the effect of the speed, the inertia and the temperature dependence of the materi- al’s resistance to deformation on the roll separating forces and on the roll torques. The Bingham material model22 was taken as the constitutive relation, defining the stress deviator tensor components in terms of the metals’ viscosity as
2η Sij 5 pffiffiffiffiffi ε_ij ð5:67Þ 1 2 ðk= J2Þ where the dynamic viscosity of the material is designated by η, k stands for the yield strength of the material in pure shear, ε_ij are the components of the strain rate tensor and J2 is the second invariant of the of the stress deviator tensor, defined as
1 J 5 S S ð5:68Þ 2 2 ij ij
For completeness, recall that the deviator stress tensor components are defined in terms of the stress components by the relation
1 S 5 σ 2 σ δ ð5:69Þ ij ij 3 kk ij where δij is Kronecker’s delta. In deriving the velocity field, the authors assumed that the arc of contact may be replaced by straight lines. The flow pattern then becomes a radially converging flow, leading to the statement that the resulting stress field is “unavoidably approx- imate in nature”. The coefficient of friction is taken to depend on the speed of the rolled strip at entry. They use the two relations given by Sims and Arthur (1952):
μ 5 0:08 expð20:51v0Þð5:70Þ for
0 # v0 # 0:25 m=s
22It is rare to see the Bingham model used in problems dealing with plastic forming of metals. One of the exceptions is the work of Haddow on the compression of a disk; see Haddow, J.B. 1965. On the compression of a thin disk. Int. J. Mech. Sci. 7, 657 660. 92 Primer on Flat Rolling and
μ 5 23 20:038 : 10 expð4v0 Þð5 71Þ for
0:25 # v0 # 1:5m=s
The predicted roll separating force and torque values compared very well to the experiments of Shida and Awazuhara (1973) on cold rolling of steel strips. Further, increasing speeds were found to cause increasing compressive loads on the rolls and increasing tensile stresses within the strip, both of which were most likely caused by the strain rate dependence of the rolled metal, as predicted by the Bingham material model.
5.9 Comparison of the Predicted Powers
Several mathematical models have been introduced in this chapter: an empirical model, 1D models and a model based on the upper bound theorem. Two formulas have also been given to estimate the power required to reduce a strip of metal in a rolling mill; see Eqs. (5.8) and (5.9). Their predictions can now be compared and discussed in light of their assumptions. Consider the hot rolling of a low-carbon steel strip in a single stand roughing mill. Let the entry thickness of the slab be 20 mm and its width to be 2000 mm. Its resistance to deformation is taken to be 150 MPa. It is reduced by 30% using work rolls of 800 mm diameter, rotating at 50 rpm. The coefficient of friction is taken to be 0.2. The estimated power for plastic deformation, by Eq. (5.7), is obtained as 6115 kW. With four bearings of 400 mm diameter and a coefficient of friction of 0.01 in the bearings, the losses there are estimated to be 500 kW. Assuming further that the efficiencies of the motor and the transmission are both 0.9, the total power to drive the mill is obtained, by Eq. (5.8), as 8170 kW. Using the same numbers and Eq. (5.9), the total power is estimated to be 5350 kW. The upper bound theo- rem, designed to give conservative estimates, also allows the prediction of the power, required for plastic deformation of the strip. Equation (5.63), with the fric- tion factor equal to 0.8, yields 3200 kW. Calculations using the refined 1D model (see Section 5.4) leads to a torque for both rolls of 524 Nm/mm, which when used to compute the power needed to reduce the strip, gives 5483 kW. Adding on the power losses in the four bearing and using 0.9 for the efficiency of the motor as well as the transmissions, one obtains 7262 kW. Based on these calculations23,itis recommended to use either the refined 1D model or the empirical model. A conser- vative number for the motor power is likely to result.
23It is to be noted that only one set of data was used in the exercise. Statistical analysis is necessary to prove the consistency of the predictions of any of the models. Mathematical and Physical Modelling of the Flat Rolling Process 93
The second number appears to be closer to reality, based on Robert’s calcula- tions, mentioned above.
5.10 The Development of the Mechanical Attributes of the Rolled Strip
A detailed exposition of state-of-the-art of the evolution of the microstructure and the resulting mechanical attributes after hot flat rolling have been presented by Lenard et al. (1999). Carbon and alloy steels were included in the discussion and the predictions of the metallurgical model have been substantiated by comparing them to results obtained in the laboratory and in industry. In what follows, a revised and updated version, dealing with carbon steels, is described. Numerical examples are also given. The development of the draft schedule of the hot or the cold controlled rolling processes is usually performed off-line, using sophisticated mathematical models, which are composed of mechanical, thermal and metallurgical parts. The objective of the process is the creation of steel with small, uniform ferrite grains and as the Hall Petch equation demonstrates, this will increase the strength of the rolled metal. There are a limited number of parameters whose magnitudes may be chosen relatively freely, although several of them are connected through mass conserva- tion. The parameters include:
G the starting temperature; G the strain per pass; G the strain rate per pass (within strict limits); G the interstand tensions G the interstand and the pre-coiler cooling rates. The engineer must also consider the given parameters which cannot be altered: these involve the rolling mill and its capabilities. At this point the chemical compo- sition of the steel is also given and the designer of the draft schedule must keep that in mind. The thickness of the scale on the surface may be controlled to some extent by the scale breakers. The interfacial frictional forces may also be con- trolled, also only to some extent, by the careful design of lubricant and coolant delivery. Lenard and Pietrzyk (1993) showed in a numerical experiment that while austenite grain size of a low-carbon steel is not affected by the coefficient of fric- tion, the higher the surface heat transfer coefficient, the lower the grain diameter near the surface of the rolled steel, as expected by the higher surface cooling rates. There is some evidence that the metallurgical structure at the end of the rough rolling process doesn’t affect the subsequent events in any significant manner so the concern here is with the design of the passes on the finishing train and the cooling banks. The metallurgical events that affect the eventual attributes of the rolled metal are the hardening and the restoration processes. The hardening processes include strain, strain rate and precipitation hardening; the restoration processes include 94 Primer on Flat Rolling recovery and recrystallization, static, dynamic or metadynamic. These, in turn, are affected by the mechanical and thermal events. The three critical temperatures need to be known: 1. The precipitation start and stop temperature 2. The recrystallization start and stop temperature 3. The transformation start and stop temperature. In Lenard et al. (1999), the analysis of the thermal and mechanical events was accomplished using a finite-element model of the rolling process. Carbon and alloy steels were examined. A 2D model was used to determine the distributions of the mechanical and the thermal variables during and after rolling, and these data were then used to calculate the resulting grain sizes, amount of recrystallization and the mechanical properties after cooling. In the present treatment, the 2D model is replaced by one of the 1D models described above, and the output of this is then employed as the initial condition to determine the development of the post-rolling attributes. Since carbon steels only are considered here which experience no signifi- cant precipitation, the two mechanisms of interest are the processes of recrystalliza- tion and transformation. Their progress depends on the temperature and time available, in addition to the strain and the rate of strain in the pass. Sellars (1990) summarized the importance of modelling of the evolution of the microstructure:
G for a given composition of alloy, the high-temperature flow stress is influenced to a large extent by the microstructure. Proper prediction of the rolling force is possible only if the relevant microstructure is known and the microstructure present at the end of the rolling and cooling operations controls the product properties. Austenite, a face-centred-cubic structure (FCC), is formed after solidifying. It is designated by γ. On further cooling to the Ar3 temperature, the ferrite (α)grains appear and the steel reaches the two-phase region. The structure of the ferrite is body-centred-cubic (BCC). As the temperature drops to the Ar1 temperature, the transformation stops and the steel has become fully ferritic. Depending on the carbon content and cooling rates, other phases such as pearlite or bainite may appear as well. The two temperatures, Ar3 and Ar1, are affected by the chemical composition, pre-strain, cooling rate and initial austenite grain size; see Hwu and Lenard (1998). The costs associated with industrial trials are prohibitively high. The trials are expensive and difficult to control and monitor, and are necessarily constrained by the capabilities of existing plants. Laboratory simulation tests are unable to repro- duce all conditions of industrial hot rolling24. Both the torsion and compression tests have limitations on the attainable strain rates, particularly in relation to strip or rod rolling. Further limitations are evident in torsion testing, in which the sample also develops different textures from those in flat rolling. On the other hand, the plane-strain and axisymmetrical compression tests cannot achieve the total strains of complete industrial rolling schedules. Hence, the use of off-line models which, in
24In spite of this limitation, laboratory simulation of the multi-stage hot rolling process yielded extremely useful results. Mathematical and Physical Modelling of the Flat Rolling Process 95 spite of the critique above, have been obtained from laboratory simulation tests is very useful, especially if the consistency and the accuracy of their predictions can be demonstrated. It must be realized at this point that the predictive abilities of these models have been substantiated by comparing their predictions to a selected number of measurements. Statistical analysis of the predictions, while necessary, is not widespread.
5.10.1 Thermal Mechanical Treatment The two major objectives of the hot-rolling process are to control the dimensions of the product and to affect the attributes the metal will possess on cooling. For most commercial products in the steel industry, their external shapes are the result of hot deformation, such as hot rolling, while the necessary mechanical proper- ties are obtained by alloying elements and heat treatment after deformation. However, metallurgical changes caused by hot deformation may result in additional beneficial effects on the mechanical properties of steels and sometimes can eliminate heat treatment after deformation. Thermomechanical processing is a technique to combine shaping and heat treating of steel. Controlled rolling is a typical example of thermomechanical processing in which the austenite is conditioned to produce a fine ferrite grain size. The development of controlled rolling approaches, used for carbon steels, is shown in Figure 5.14. There are four different techniques in the figure, in which “R” refers to rolling in the roughing mill and “F” indicates the finishing mill. In the first method, both roughing and finishing are completed at a temperature at which the steel is fully recrystallized. The resulting product will emerge as soft and ductile. In the second, the finish rolling process is interrupted and the steel is allowed to cool but the rolling process is still completed in the full recrystallization region. The result is a steel that is somewhat harder than in the first process. In both the third and the fourth strategies, the processing temperatures are further
1250 1250 R R 1150 γ R 1050 F 1100 $
C) R ° 1000 Recryst. F 950 850 100°C[Nb] γ 900 $ γ F F Unrecryst Unrecryst A 800 r γ+α γ+α 3
Temperature ( Temperature Ar A l r1 α+θ α+θ Holding Holding Holding
Time
Figure 5.14 Controlled rolling strategies. 96 Primer on Flat Rolling decreased and rolling is completed such that the steel is only partially recrystallized or, in the last step, finish rolling is performed in the two-phase region. Hodgson and Barnett (2000) review the practice of thermomechanical proces- sing of steels. They list the processes in use in industry, classifying them as those carried out during the deformation process and those performed during the cooling phase, after deformation. These processes are:
G Conventional controlled rolling to improve strength and toughness G Recrystallization controlled rolling to achieve fine grains by affecting austenite grain growth and higher strength by precipitation hardening G Accelerated cooling, direct quenching, quench and self-tempering to affect the transfor- mation mechanisms G Warm forming to affect the ferrite phase G Intercritical rolling of the austenite ferrite structure to increase the strength and toughness. The authors also write about how thermomechanical processes may develop in the future. They identify the processes that produce ultrafine grains by heavy plastic deformation (see Chapter 13) and by the application of magnetic fields. In another process (Hodgson et al., 1998), austenite grains are coarsened prior to deformation, followed by a small reduction and cooling. The result is a composite strip with ultra- fine grains in the surface layers, possessing markedly increased strength.
5.10.1.1 Controlled-Rolling of C Mn Steels Notch ductility and yield strength can both be improved by α grain refinement. Among other techniques for grain refinement, European mills utilized controlled low-temperature hot rolling in order to refine the α grains and to increase the tough- ness. The following features were generally applied in this controlled rolling process: Interrupting the hot-rolling operation when the slab had been reduced to the prescribed thickness, e.g. 1.65 times the final thickness. Recommencing hot-working when the slab has reached a prescribed temperature and fin- ishing at temperatures in the austenite (γ) range, above the Ar3 but lower than the con- ventional finishing temperatures, e.g. down to 800 C. The low-temperature finish rolling practice refines the γ grains, hence the trans- formed α grains. A considerable additional grain refinement can be achieved by roll- ing in the non-recrystallized γ region, where deformation bands increase nucleation sites for α grains. However, the temperature range for non-recrystallized austenite in C Mn steels is relatively narrow, and this mechanism for grain refinement cannot be effectively utilized, due to the risk of getting into the two-phase region deformation.
5.10.1.2 Dynamic and Metadynamic Recrystallization Controlled Rolling In rod and bar rolling, using high strain rates (100 1000 s21), short interpass times (between a few tens of milliseconds to a few hundreds of milliseconds), and large strains per pass (0.4 0.6) dynamic recrystallization has been found to occur. It has been proposed that under appropriate conditions, dynamic recrystallization also Mathematical and Physical Modelling of the Flat Rolling Process 97 occurs during strip rolling of niobium HSLA steels. The occurrence of dynamic recrystallization during simulated strip rolling of HSLA steels has been cited by several other authors. The results of an analysis of the events during strip rolling also indicated that dynamic recrystallization is happening during rolling of Nb. Dynamic recrystallization affects rolling loads and is reported to produce consider- ably finer ferrite grains (B3 μm) than those transformed from pancaked austenite (B7 μm). However, there are concerns regarding the validity and applicability of the results obtained in all of the above studies to the real mill practice, primarily due to the low strain rates employed in the experiments. Conventional controlled rolling relies on static recrystallization in the early stages of finish rolling to refine the austenite and pancaking of the austenite in the last stages to enhance ferrite grain nucleation during transformation. In contrast, dynamic recrystallization favours higher reductions in the first few stands to exceed the critical strain for the onset of dynamic recrystallization. Dynamic recrystalliza- tion controlled rolling leads to greater ferrite grain refinement through austenite grain refinement. Another advantage of the initiation of dynamic recrystallization during rolling is a marked reduction in roll forces and torques, which in turn trans- lates to savings in energy consumption and less roll wear. Also, the gauge accuracy will be enhanced due to the lower reductions required in the last stands. The only justification that the author found in the literature regarding the better grain refine- ment through dynamic recrystallization is the higher nucleation rate and formation of “necklace structure” during deformation. High density of grain nucleation already incorporated into the matrix expedites the post-dynamic recrystallization compared to static recrystallization, as no incubation time is required.
5.10.1.3 Effects of Recrystallization Type on the Grain Size Many different authors have attempted to develop models predicting grain sizes produced by static, dynamic and metadynamic recrystallization for different materi- als. The general observation, common in all these models, is that statically recrys- tallized grain size is a function of initial grain size, temperature and amount of strain, while dynamically and metadynamically recrystallized grain sizes are only a function of Zener Hollomon parameter, i.e. temperature and strain rate, in an inverse power law form. This indicates that increasing strain rate and decreasing rolling temperature lead to more grain refinement provided dynamic and metady- namic recrystallization are in place. Another common understanding is that rolling schedules with dynamic and metadynamic recrystallization produce finer final grain sizes compared to schedules with only static recrystallization. This idea is appeal- ing to the steel manufacturers to achieve further grain refinement.
5.10.1.4 Controversies Regarding the Type of Recrystallization in Strip Rolling The occurrence of dynamic recrystallization by strain accumulation during indus- trial hot strip rolling schedules has been questioned. It has been argued that the 98 Primer on Flat Rolling kinetics of static recrystallization approaches those of dynamic recrystallization as the strain increases. In addition, interpass times are generally much greater than deformation times. Hence, softening of the material during strip rolling may be due to enhanced static recrystallization. This controversy, in spite of its practical importance in terms of final mechanical properties and mill set-up, still remains. The physical proof of the possibility of dynamic recrystallization during strip rolling is notoriously difficult, since it requires extremely fast quenching of steel during deformation to freeze the structure and look for dynamically created grain nuclei. Most of the mill engineers do not believe in the possibility of dynamic recrystallization in any kind of steel during strip rolling. This belief has been reinforced by the fact that the possibility of dynamic recrystallization has not been taken into account in the conventional strip mill set-up and in control modules developed by General Electric and Westinghouse. In these control modules, which are in use in North America, it is assumed that the steel repeatedly goes through only work hardening during deformation and static softening during interpass times. This assumption may lead to erroneous roll force prediction if the steel actu- ally softens in one or more stands instead of hardening. There are few examples of phenomenological models being in use in hot rolling. This is due to the complexity of the process and the lack of true phenomenological models to be able to quantitatively describe the microstructural changes occurring during rolling. Historically, there has been widespread application of empirical and semi-empirical models, based on simple statistical regressions of large data sets of plant measurements. The accuracy of these models depends on the availability of a general form of mathematical equations which can fit the data well. Data are usu- ally non-linear and interrelated, which limits the applicability and accuracy of regression models. It is expected that the next decade will see extensive use of both the semi-empirical and heuristic models within the steel industry.
5.10.2 Conventional Microstructure Evolution Models Mathematical models of the evolution of the microstructure have been published in the technical literature. Sellars (1990), Roberts et al. (1983), Laasraoui and Jonas (1991a, b), Choquet et al. (1990), Hodgson and Gibbs (1992), Yada (1987), Beynon and Sellars (1992), Sakai (1995), Kuziak et al. (1997) and Devadas et al. (1991) presented various closed-form equations, describing the processes of recrys- tallization and grain growth. The restoration processes are time dependent and since in industrial hot rolling the strain rates are high, there is not enough time to trigger dynamic restoration of the work-hardened material; note that the time available is determined by the ratio of the strain and the strain rate, t 5 εpass=ε_pass. To demonstrate the validity of this statement, take a typical set of numbers in the first stand of a hot strip mill. Let the entry thickness be 15 mm and consider a fairly high, 50% reduction at a roll speed of 30 rpm. Take the diameter of the work roll as 500 mm. The average strain rate in the pass is then estimated to be 12 s21, the true strain is 0.69 and hence the pass takes place in about 55 ms, indicating that concurrent static recovery, accompanied Mathematical and Physical Modelling of the Flat Rolling Process 99 by static recrystallization, usually occurs after deformation. Both static recovery and recrystallization have been observed in austenite, although the extent of the former is rather limited. Some caution is introduced at this point. Biglou et al. (1995) consid- ered industrial hot-rolling schedules of Nb-bearing microalloyed steels. Torsion test- ing was used to simulate the finish rolling schedules and some softening, attributed to metadynamic recrystallization, was found in the third stand. As well, accumulat- ing strains have been thought to contribute to dynamic recrystallization.
5.10.2.1 Static Changes of the Microstructure The first step is to attempt to control the temperature at the entry to the first stand of the finishing mill. The success of this attempt is limited by the temperature of the just-hot-rolled strip, called the transfer bar, which is most likely waiting to exit the coil box. The temperature of the strip entering the coil box is controlled by the reheat furnace, held at 1200 1250 C, and by the heat gains and losses in the roughing passes. The difference between the head and the tail temperatures is mini- mized while the steel is coiled up in the coil box within which the cooling rate is quite slow. The entry temperature therefore will depend on all of the above: the temperature in the reheat furnace, the gains and losses during rough rolling and the time spent in the coil box. The temperature above which recrystallization will occur is given by Boratto et al. (1988): pffiffiffiffiffiffiffiffiffi T 5 887 1 464 ½C 1 ð6445 ½Nb 2 644 Nb NRX pffiffiffiffiffiffiffi ð5:72Þ 1 ð732 ½V 2 230 ½V Þ 1 890 ½Ti 1 363 ½Al 2 357 ½Si so a low-carbon steel, containing 0.05% C, will recrystallize above 910 C. The higher the carbon content, the higher the temperature above which recrystallization will be present. The entry temperature into the first stand is usually higher than 900 C, unless ferrite rolling is contemplated. The extent of static recovery, defined as a softening process in which the decrease of density and the change in the distribution of the dislocations after hot deformation or during annealing are the operating mechanisms, is rather limited in hot-rolling processes. There is a general consensus that the maximum amount of softening during holding, attributable to recovery, is approximately 20%. The hot deformation of austenite at strains typically encountered in plate or strip rolling processes leads to significant work hardening, which is usually not removed by either dynamic softening processes or static recovery. This hardening creates a high driving force for static softening processes. The mechanism of these processes is explained clearly by Hodgson et al. (1993). Some of his observations are pre- sented briefly below:
G A minimum amount of deformation (critical strain) is necessary before static recrystalli- zation can take place. G The lower the degree of deformation, the higher the temperature required to initiate static recrystallization. 100 Primer on Flat Rolling
G The final grain size depends on the degree of deformation and to a lesser extent, on the annealing temperature. G The larger the original grain size, the slower the rate of recrystallization. During conventional preheating at high temperatures, incomplete recrystalliza- tion can take place at an early stage of the rolling process when small reductions are applied. The accumulation of strains then leads to full recrystallization in subse- quent passes and, in consequence, the effect of the initial conditions on the down- stream final microstructure is very small and is usually neglected. The recrystallized volume fraction X is determined by the Johnson Mehl Avrami Kolmogorov equation as a function of the holding time after deformation: "# t k X 5 1 2 exp A ð5:73Þ tX where t is the holding time, tX is the time for a given volume fraction X to recrys- tallize, A 5 ln(X) and k is the Avrami exponent. The majority of microstructure evolution models has been developed for X 5 0.5, indicating that tX in Eq. (5.73) represents the time for 50% recrystallization and the constant A 520.695. The most commonly used form describing the time for 50% recrystallization (t0.5X)is p q r s QRX t : 5 Bε D Z ε_ exp ð5:74Þ 0 5X RT where ε is the strain, D is the grain size prior to deformation in μm, Z is the 25 Zener Hollomon parameter , ε_ is the strain rate, QRX is the apparent activation energy for recrystallization, R is the gas constant and T is the absolute temperature. 219 Sellars (1990) gives B 5 2.5 3 10 , p 524, q 5 2, QRX 5 300,000 J/mole and the Avrami exponent, k 5 1.7. The exponents of the Zener Hollomon parameter and the strain rate are indicated to equal zero. Equation (5.74) implies that the time for 50% recrystallization decreases with increasing strains and grows with the grain size. The time required for 50% recrystallization is given as a function of the temperature of the pass in Figure 5.15, for a set of realistic strains and pre-pass grain sizes. It is clear that the steel will recrystallize quite fast at higher strains and at higher temperatures. The recrystallized grain size is reportedly sensitive to the temperature. The most commonly used form of the equation (Sellars, 1990) describes the dependence of the grain size after recrystallization (Dr) on the strain, the strain rate, the prior aus- tenite grain size, the apparent activation energy and the temperature:
2Q D 5 C 1 C εmε_nDl exp d ð5:75Þ r 1 2 RT
Sellars (1990) gives the magnitudes of the constants and the exponents in Eq. (5.75) as follows: C1 5 0; C2 5 0.5; m 521; n 5 0; l 5 0.67; Qd 5 0, indicating that the
ÀÁ 25The Zener Hollomon parameter is defined as Z 5 ε_ exp Q=RT . Mathematical and Physical Modelling of the Flat Rolling Process 101
1E+5 Figure 5.15 The time required Strain Dγ (μm) for 50% recrystallization as a 1E+4 0.1 50 function of the temperature, the 0.1 100 strain and the initial grain size. 1E+3 0.1 150 0.5 50 1E+2 0.5 100 0.5 150 1E+1
1E+0
1E–1
1E–2 Sellars (1990) Time for 50% recrystallization (s) Time for 1E–3
1E–4 600 800 1000 1200 1400 1600 Temperature (°C) strain and the prior austenite grain size are the most significant variables. Roberts et al. (1983) provides somewhat different magnitudes. He gives C1 5 6.2; C2 5 55.7; m 520.65; n 5 0; l 5 0.5; Qd 5 35 000 J/mole. Note that Sellars’ equation excludes the dependence of the recrystallized grain size on the temperature but Roberts’ accounts for it. Both researchers indicate that the grain size after recrystallization is independent of the rate of strain. Choquet et al. (1990) and Hodgson and Gibbs (1992) also gave various magnitudes for the coefficients and the exponents. Laasraoui and Jonas (1991a,b) offer another relation for the recrystallized grain size in a C Mn steel in terms of the strain and the pre-deformation austenite grain size, similar to that of Sellars (1990) with somewhat different exponent for the strain:
0:67 20:67 Dr 5 0:5D ε ð5:76Þ
The equations predict different grain sizes for the same initial conditions. Assuming an initial grain size of 50 μm, a strain of 0.30 and at a temperature of 800 C, Sellars and Roberts predict a grain size of 23 μm, while Laasraoui and Jonas predict 15 μm. Increasing the initial size to 150 μmgives48μm by Sellars, 36 μm by Roberts and 32 μm by Laasraoui and Jonas. It is difficult to recommend one of these relations for use without some more data, preferably analysed statistically. The time for the completion of recrystallization is calculated from the Avrami equation for the recrystallized volume fraction, X (Eq. (5.73)). The constant A is taken to correspond to 50% recrystallization. In that case X 5 0.5, both t and tX are t0.5X and A 5 lnð1 2 0:5Þ 520:693. The time for X% of recrystallization is thus
1 lnð12XÞ k t 5 t ð5:77Þ A X 102 Primer on Flat Rolling
and the time for 95% recrystallization, when tX 5 t0.50 is
1 k lnð0:05Þ 1 t : 5 t : 5 4:3219k t : ð5:78Þ 0 95 lnð0:5Þ 0 50 0 50
Situations when partial recrystallization takes place during interpass times are com- mon in the industrial rolling processes. Beynon and Sellars (1992) present an equa- tion to calculate the grain size at the entry to the next pass:
ð4=3Þ 2 Dp 5 DrX 1 Dð12XÞ ð5:79Þ where D represents the grain size prior to deformation, Dp is the recrystallized grain size and X is the recrystallized volume fraction. Considering some of the grain sizes used above (800 C, D 5 50 μm, Dr 5 23 μm and 75% recrystallization), the average grain size of the rolled strip entering the next stand is predicted to be nearly 19 μm.
5.10.2.2 Dynamic Softening All softening processes that take place during plastic deformation are referred to as dynamic ones. These include dynamic recovery and dynamic recrystallization. The conventional models of dynamic recrystallization involve equations describing the critical strain, kinetics of dynamic recrystallization and the grain size after dynamic recrystallization. The critical strain at which dynamic recrystallization starts is given in terms of the Zener Hollomon parameter, the grain size and several constants:
p q εc 5 AZ D ð5:80Þ
Sellars (1990), considering a C Mn steel, defines A 5 4.9 3 1024, p 5 0.15, q 5 0.5 24 and QDRX 5 312,000 J/mole. Laasraoui and Jonas (1991a) give A 5 9.82 3 10 , p 5 0.13, q 5 0 and QDRX 5 312,000 J/mole for a similar steel. A check of Sellars’ predictions of the critical strain is possible by considering the true stress true strain curve for a 0.05% C steel at 975 C at a strain rate of 1.4 3 1023 s21, presented by Jonas and Sakai (1984). Reading the critical strain off the curve, one obtains εc 0:14. The grain size is taken as 65 μm and the predicted critical strain is then found to be 0.15. The equation describing dynamically recrystallized volume fraction is "# k ε2εc XDRX 5 1 2 exp B ð5:81Þ εp
where εp is the strain at the peak stress, usually calculated as εp 5 Cεc. Hodgson et al. (1993) give the coefficients in Eq. (5.81) for C Mn steels as B 5 0.8, k 5 1.4 and C 5 1.25. The strain for 50% recrystallization is calculated as Mathematical and Physical Modelling of the Flat Rolling Process 103 23 0:28 0:05 51880 ε : 5 1:144 3 10 D ε_ exp ð5:82Þ 0 5X RT
The equation describing the grain size after dynamic recrystallization is
r DDRX 5 BZ ð5:83Þ
Sellars (1980) provides the coefficients in Eq. (5.83) for C Mn steels as B 5 1.8 3 103 and r 520.15. The apparent activation energy is, as given above, 312,000 J/mole.
5.10.2.3 Metadynamic Recrystallization When dynamic recrystallization starts during the deformation and the recrystallized nuclei continue to grow after the deformation ends, the phenomenon is identified as metadynamic recrystallization. The equation describing the time for 50% meta- dynamic recrystallization is s Q t : 5 A Z exp ð5:84Þ 0 5 1 RT
The constants in Eq. (5.84) for carbon manganese steels are given by Hodgson et al. (1993): A1 5 1.12, s 520.8, Qd (the activation energy of deformation in the Zener Hollomon parameter) 5 312,000 J/mole and Q 5 300,000 J/mole. The meta- dynamic grain size is (Hodgson et al., 1993)
u DMD 5 AZ ð5:85Þ where A 5 2.6 3 104 and u 520.25. The grain size during metadynamic recrystallization is calculated as the weighted average of the contributing grains:
DðtÞ 5 DDRX 1 ðDMD 2 DDRXÞXMD ð5:86Þ
In Eq. (5.86), XMD is the volume fraction after metadynamic recrystallization, cal- culated from the Avrami equation with k 5 1.5.
5.10.2.4 Grain Growth Following complete static or metadynamic recrystallization, the equiaxed austenite microstructure coarsens by grain growth. Nanba et al. (1992) and Hodgson and Gibbs (1992) presented the equation for C Mn steels: 2 Q DðtÞn 5 Dn 1 k t exp g ð5:87Þ RX g RT 104 Primer on Flat Rolling
where DRX is the fully recrystallized grain size, t is the time after complete recrys- tallization, Qg 5 66,600 J/mole is the apparent activation energy for grain growth, 12 and n 5 2 and kg 5 4.27 3 10 are constants. The equation predicts a linear depen- dence of the grain growth on the time.
5.10.3 Properties at Room Temperatures Empirical relations, leading to the mechanical attributes of the rolled product, have also been developed and in what follows, these are reviewed in some detail. At the Ar3 temperature, given by
Ar3 5 910 2 310ðCÞ 2 80ðMnÞ 2 20ðCuÞ 2 15ðCrÞ 2 80ðMoÞ 1 0:35ðt 2 8Þ ð5:88Þ the austenite grains begin their transformation to ferrite grains. Equation (5.88) was developed for plate rolling and t represents the thickness of the plate.
5.10.3.1 Ferrite Grain Size The ferrite grain sizes may be estimated by the relation of Sellars and Beynon (1984):
5 2 : ε1=2 3 : 1 21=2 1 2 2 : 3 22 : Dα ð1 0 45 r Þ f1 4 5Cr 22½1 expð 1 5 10 DÞ g ð5 89Þ where Dα is the ferrite grain size in μm, Cr is the cooling rate in K/s, D is the aus- tenite grain size, also in μm and εr is the accumulated strain. When the cooling rate is taken as 20 K/s, the accumulated strain as 0.4 and the grain size as 50 μm, Eq. (5.89) predicts a ferrite grain size of 10 μm.
5.10.3.2 Lower Yield Stress
According to the Hall Petch equation, the lower yield stress σy for a homogeneous microstructure is expressed as
20:5 σy 5 σ0 1 KyDα ð5:90Þ
where σ0 is the lattice friction stress, Ky is the grain boundary unlocking term for 23/2 high-angle grain boundaries, taken as 15.1 18.1 N mm and Dα is the ferrite grain size. Le Bon and Saint Martin (1976) presented a simple equation for the lower yield stress of carbon steels, in terms of the ferrite grain size:
20:5 σy 5 190 1 15:9ð0:001DαÞ ð5:91Þ Mathematical and Physical Modelling of the Flat Rolling Process 105
5.10.3.3 Tensile Strength Hodgson and Gibbs (1992) published a simple formula expressing the tensile strength of carbon steels with some alloying elements:
σu 5 164:9 1 634:7 ½C 1 53:6 ½Mn 1 99:7 ½Si 1 651:9 ½P ð : Þ 20:5 5 92 1 472:6 ½Ni 1 3339 ½N 1 11ð0:001DαÞ
The tensile strength of a carbon steel, containing 0.1% C and 0.6% Mn, and 10 μm ferrite grains, is estimated as 370 MPa. The yield strength of the steel is 349 MPa.
5.10.4 Physical Simulation In spite of the comments above regarding the limited abilities of physical simula- tion of thermal mechanical treatment, useful and detailed information can be obtained about the hot response of steels. While the number of publications in the field is too numerous to be reviewed here, many of the equations, given above, have been obtained as a result of simulation experiments: multi-stage compression and torsion tests have been found to be very useful. Some of the publications have been reviewed by Lenard et al. (1999); in one of these, Majta et al. (1996) performed multi-stage hot compression of a high-strength low-alloy steel, mea- sured the yield strength after cooling and compared it very successfully to the measurements of a large number of researchers (Morrison et al., 1993; Coldren et al., 1981; Irvine and Baker, 1984). Several meetings have been devoted to the subject. One of the outstanding conferences was held in Pittsburgh in 1981, entitled “Thermomechanical Processing of Microalloyed Austenite”, edited by A.J. DeArdo, G.A. Ratz and P.J. Ray.
5.11 Miscellaneous Parameters and Relationships in the Flat Rolling Process
The mathematical models presented above take account of the contributions of the most significant variables and parameters. Several more phenomena are associated with the flat rolling process, however, and it is surprising that these aren’t usually included in the traditional analyses26. These are listed below; their definitions are given and simple formulae are presented for their evaluation.
5.11.1 The Forward Slip The relative velocities of the strip and the roll have been identified as having an effect on the rate of straining, lubrication, friction, scaling and the interfacial
26On-line and off-line models used in the rolling industry often include these parameters. 106 Primer on Flat Rolling forces. The forward slip, which is given in terms of the relative velocity, has, on occasion, been used to characterize tribological events. It is defined as
vexit 2 vroll Sf 5 ð5:93Þ vroll
In determining the exit velocity of the strip, one may use a variety of approaches. Optical techniques, which monitor the roll and the strip velocities, arguably offer the most accurate measurements. One often-used method is to mark the work roll surface using equally spaced, parallel lines, the separation of which is designated by lr. These lines make their impressions on the surface of the rolled strips and their distance on the strip, ls, may be measured using travelling microscopes. The forward slip can then be determined from these distances as
ls 2 lr Sf 5 ð5:94Þ lr
Using the idea of mass conservation or its equivalent, volume constancy, indicating that the volume of the rolled metal at any particular location is constant, it can be shown that the two formulas for the forward slip are identical. Researchers studying the development of surfaces as a result of flat rolling may well object to marking the roll surface as the lines may affect the interactions of the surfaces and the lubricants. The forward slip is often taken as a direct indication of frictional conditions in the roll gap. There are several formulas in the technical literature, connecting the coefficient of friction and the forward slip. These will be discussed in some more detail in Chapter 9.
5.11.2 Mill Stretch
When a certain exit thickness, hexit, is required, and the roll gap is to be set such that it is achieved, it is necessary to account for the extension of the mill frame, as well. The formula expressing the thickness that will result when the roll gap is set 0 to h1 is given below:
P h 5 h0 1 ð5:95Þ exit 1 S where P is the roll separating force in N and S is the mill stiffness, measured in N/mm. A typical value for the mill stiffness is 5 MN/mm; however, this would have to be ascertained for each particular mill.
5.11.3 Roll Bending Rowe presents a simple formula to estimate the maximum deflection at the centre of the work roll (Rowe, 1977), treating the roll as a simply supported beam, Mathematical and Physical Modelling of the Flat Rolling Process 107 loaded at its centre. The formula accounts for the deflections due to shear loading, as well:
Pl3 Pl Δ 5 1 0:2 ð5:96Þ EI AG where Δ is the maximum deflection of the roll at its centre in mm, P is the roll force in N and l is the length of the roll, bearing to bearing in mm. The elastic modulus is designated by E and taken as 200,000 MPa and the shear modulus by G, equal to 86,000 MPa. The cross-sectional area of the roll in mm2 is A and I is the moment of inertia27 of the roll’s cross-section in mm4. Roberts (1978) developed a more fundamental formula for the maximum deflec- tion of the roll, based on the double integration method. The effects of both the normal and shear loads are included here as well:
PL2ð5L 1 24 Þ PL Δ 5 1 1 c 1 ð5:97Þ 6πED4 2πGD2 where L1 is the centre-to-centre distance of the bearings and c is half of the bearing length. The equation presented by Wusatowski (1969), similar to Eq. (5.97), includes several more geometrical parameters. He gives the roll deflection at the centre, including the effects of shear: 8 < 1 Â Δ 5 P 8L3 2 4L b2 1 b3 1 64c3ðD4=d4 2 1Þ :18:8ED4 1 1 9 ð : Þ = 5 98 1 ÂÃ 1 L 2 0:5b 1 2cðD2=d2 2 1 GD2π 1 ; where b is the width of the rolled strip. Simple calculations indicate interesting magnitudes of the deflection of a work roll at its centre. In a laboratory experiment, using a 250 mm diameter steel roll, with the bearings 400 mm apart, and reducing a 25 mm wide low-carbon steel strip by 50%, the roll separating force was measured to be 8000 N/mm. The roll deflec- tion is then obtained as 0.337 mm, a little over 0.1% of the roll diameter, indicating no need for crowning. Similar calculation for an industrial case yields quite differ- ent numbers. Considering hot rolling of a 2000 mm wide low-carbon steel strip and reducing it with 1000 mm diameter rolls, leads to roll separating forces of 24 34 MN, depending on the temperature and the reduction. Equation (5.96) now indicates that the roll deflection will be in the order of 26 mm. If no crowning is used, the cross-section of the rolled strip will not be satisfactory.
27A more suitable name for I is “second moment of the area”. 108 Primer on Flat Rolling
5.11.4 Cumulative Strain Hardening The cumulative effect of sequential straining on the resistance of the material to deformation is well understood. In what follows, a simple procedure to estimate this effect in multi-pass flat rolling is presented. In the example, a strip of steel is to be rolled in two consecutive passes. In the first pass its thickness at the entry is hentry and its thickness at the exit is hexit;1: hentry ε1 5 ln ð5:99Þ hexit;1 and the average flow strength is obtained by integrating the true stress true strain relation over the strain in the pass
ðε 1 1 σ 5 σðεÞ ε ð : Þ 1 ε d 5 100 1 0
In the second pass the entry thickness is hexit;1 and the exit thickness is hexit;2 so the strain in the second pass is hexit;1 ε2 5 ln ð5:101Þ hexit;2 and the total strain experienced by the strip so far hentry εtotal 5 ln ð5:102Þ hexit;2
The average flow strength in the second pass is then determined by integrating over the strain in the second pass:
ðε 1 total σ 5 σðεÞ ε ð : Þ 2 ε 2 ε d 5 103 total 1 ε1
The steps described above are illustrated by an example in which a low-carbon steel strip is reduced, first by a strain of 0.1, followed by another pass creating the same magnitude of the strain. The true stress true strain relation of the steel, in : MPa, is σ 5 100ð11182:02εÞ0 355 so the average flow strength in the first pass is obtained as 218 MPa and in the second, 326 MPa; Figure 5.16 shows the details.
5.11.5 The Lever Arm In the empirical model of the flat rolling process (see Section 5.2), the roll torque was calculated by assuming that the roll separating force acts halfway between the Mathematical and Physical Modelling of the Flat Rolling Process 109
400 Figure 5.16 The true 0.355 σ = 100(1+ 182.02ε) MPa stress true strain curve and the average flow strengths in the two passes. 300
200 σ 2 True stress (MPa) True σ 100 1
ε ε 1 cum 0 0.00 0.05 0.10 0.15 0.20 0.25 True strain entry and the exit, making the ratio of the torque for both rolls and the roll separating force the lever arm equal to the projected length of the contact, L. As men- tioned above, while the predictions of the roll separating forces by the empirical model are reasonably accurate and consistent, those of the roll torque are not quite as good. The reason is found in the assumption of the magnitude of the lever arm. In an effort to develop a better appreciation of the lever arm, the data of McConnell and Lenard (2000) are employed once again. These include approxi- mately 250 experiments. The ratios of the measured roll torques and the roll sepa- rating forces are calculated, yielding the actual lever arm, a. Then, the ratio of the projected contact length and the lever arm are calculated, resulting in
L 5 3:983 3 1025P 1 0:946 ð5:104Þ a r
The results are shown in Figure 5.17, where the ratio, L/a, is plotted versus the roll separating force. All data are included, with the roll speeds varying from a low of 260 mm/s to a high of 2400 mm/s and the reductions varying from a low of 12% to a high of 50%. The lever arm is obtained as 1 6 30%. Lundberg and Gustaffson (1993) estimate the lever arm in edge rolling to be close to unity.
5.12 How a Mathematical Model Should Be Used
For successful predictions of the rolling variables while using any of the available mathematical models, knowledge of the accurate magnitudes of the coefficient of friction or the friction factor and the metal’s resistance to deformation is absolutely necessary. While it is clear that without them the predictions become essentially 110 Primer on Flat Rolling
2.0 Figure 5.17 The dependence of the ratio of the contact length Contact length = 3.983 × 10–5 P +0.947 Lever arm r and the lever arm on the roll 1.6 separating force.
1.2
0.8 Increasing speeds Increasing reductions
Contact length/lever arm Contact length/lever Cold rolling of steel strips 0.4 Various lubricants Reductions from 12 – 50% Roll speeds from 260 – 2400 mm/s 0.0 0 2000 4000 6000 8000 10000 Roll separating force (N/mm) useless, their determination may cause almost insurmountable difficulties in many instances. The following steps are then recommended.
5.12.1 Establish the Magnitude of the Coefficient of Friction Conduct a carefully controlled set of rolling tests and measure the roll separating force as a function of the rolling speed and the reductions. If hot rolling is studied, the temperature also becomes one of the independent parameters and its effect also needs to be taken into account. Its measurement is not easy. Arguably the best approach may be to embed thermocouples in the strip to be rolled, even though the stress concentration this causes may affect the magnitude of the reduction. Optical pyrometers may be used instead at both the entry and the exit and the average of their readings may give the average surface temperature quite closely. Once the data are collected, using one of the models of the rolling process and employing the inverse method, determine the coefficient of friction such that the measured and the calculated roll forces agree. This should then be followed by using non- linear regression analysis to develop a relationship of the coefficient of friction as a function of the speed and the reduction and possibly the temperature. In further modelling, this equation may then be used with good confidence.
5.12.2 Establish the Metal’s Resistance to Deformation Use the plane-strain compression test to determine the material’s resistance to deformation. If a plane-strain press is not available, a uniaxial tension or compres- sion test will be acceptable; if both are possible, choose the compression test. The experimental difficulties increase if one deals with hot deformation. In an ideal case, isothermal tests should be conducted. Mathematical and Physical Modelling of the Flat Rolling Process 111
Regardless of whether hot or cold rolling is considered, the effects of friction and temperature rise should be removed from the data. If experimental equipment, needed to determine the material’s strength, is not available, one has no choice but to rely on published data, the perils of which have been pointed out elsewhere. For hot rolling, Shida’s (1969) equations are recommended, but checking them against the data of Suzuki et al. (1968) would be helpful.
5.13 Conclusions
In this chapter mathematical models that describe the mechanical and the metallur- gical phenomena during flat rolling of metals were discussed. Modelling of the roll- ing process of strips and thin plates were examined exclusively so a 1D treatment was considered to be satisfactory. The potential objectives of modelling were listed first. The models presented were classified according to their level of sophistica- tion. These started with an empirical model and were followed by several well- known 1D models, including a 1D elastic plastic model that takes careful account of the elastic entry and exit regions as well as the elastic flattening of the work roll. In another 1D model the coefficient of friction was replaced by the friction factor which was allowed to vary along the contact region from the entry to the exit. Based on past experience, the factor was taken to depend on the roll pressure, the relative velocity of the roll and the strip and the distance along the contact. The roll pressure distribution was calculated by using the shooting method: numerical integration of the equation of equilibrium was started at the exit and the location of the no-slip point was adjusted to meet the boundary condition at the entry. The extremum theorem the upper bound formulation was also used to estimate the power needed to roll a strip. Following the mechanical models, the development of the microstructure during and after the rolling pass was described. Empirical relations that can be used to esti- mate the metallurgical parameters during rolling of low-carbon steels were listed. A few numerical examples indicated the predictions of the equations. The chapter was concluded by presenting several parameters and relationships in the rolling process which are not usually included in mathematical models: the for- ward slip, mill stretch, roll bending and the effect of cumulative strain hardening. Recommendations regarding the choice of a model to analyse the flat rolling process may now be made. As long as the roll diameter to thickness ratio is much larger than unity, a criterion that is satisfied well in strip and thin plate rolling, the “planes remain planes” assumption is valid and 1D analyses are satisfactory. The choice of the model depends on the objectives of the user. The guiding principle should be to use the simplest model that satisfies the need. Regardless of the model chosen, the accurate knowledge of three parameters is necessary: the coefficient of friction, the heat transfer coefficient and the metal’s resistance to deformation. 112 Primer on Flat Rolling
If the roll separating force only is needed, the empirical model of Section 5.2 is adequate. If the force and the torque are needed, a 1D model should be used. For somewhat more confidence in the predictions, the refined 1D model should be employed. If, in addition to the above, the temperature changes, roll flattening, required power and the metallurgical events are to be determined, the refined 1D model is recommended. See Section 5.4. If the distributions of the normal pressures and the interfacial shear stresses on the work roll are wanted, the coefficient of friction or the friction factor should be expressed as a variable from the entry to the exit of the roll gap. The shape of the coefficient of friction distribution may be based on existing data. If rolling of thicker plates is to be analysed, the recommendation is to use the finite- element technique. 6 An Advanced Finite Element Model of the Flat, Cold Rolling Process1
6.1 Introduction
As long as the mill frame is taken to be rigid, the three important components of the metal rolling system include the work rolls, the rolled strip and their interface. While a complete mathematical model of the cold, flat rolling process should account for the behaviour of all three, published studies often include several sim- plifications. The most significant of these concerns the modelling of the frictional resistance at the interface between the work roll and the rolled strip, the location where the transfer of energy is accomplished. While it is well known that the coefficient of friction and the friction factor depend, in a significant manner, on the relative velocity, the interfacial pressure, the viscosity and the surface rough- ness, a model describing the relationship of these parameters to the frictional events has still not been provided. In most of the literature the coefficient of fric- tion is treated as a free parameter whose magnitude is determined by inverse calculations. While most analyses treat the rolled metal as isotropic (Dixit and Dixit, 1996), a rare exception is the work of the same authors (Dixit and Dixit, 1997). Hartley et al. (1979) commented that earlier finite element studies of metal forming have used unrealistic frictional conditions. Hence, the authors included a layer of elements at the interface whose properties controlled friction. They applied their model to ring compression and found excellent agreement of their predictions and experiments. Liu et al. (1985) analysed the elastic plastic cold rolling process employing the layer of elements at the surface of contact, following Hartley et al. (1979). In their analysis, the Huber Mises flow criterion and the Prandtl Reuss relationship with strain hardening were included. The work rolls were taken to be rigid. While the calculated roll pressure distributions were close to those measured by Al-Salehi et al. (1973) for low reduction, there were large differences when higher reductions were considered. Li and Kobayashi (1982) expressed the frictional shear stress at the roll/rolled metal contact as a function of the relative velocity. They analysed the problem of
1This chapter is based on “Lemezhengerle´sKı´se´rleti Vizsga´lata e´sVe´geselemes Modelleze´se” by Z. Be´zi, G. Kra´llics, M. Szucs˝ and J. Le´na´rd, published in Hungarian in Anyagme´rno¨ki Tudoma´ny, Vol. 37, 2012, pp. 23 33; with permission.
Primer on Flat Rolling. DOI: http://dx.doi.org/10.1016/B978-0-08-099418-5.00006-8 © 2014 Elsevier Ltd. All rights reserved. 114 Primer on Flat Rolling cold rolling of rigid-plastic strips between rigid work rolls. They also compared their predicted roll pressure distributions to the data of Al-Salehi et al. (1973). As with the study of Liu et al. (1985), some of the comparisons were successful and some were not. Tieu and Liu (2004) used four pin-transducer combinations embedded in the work roll to monitor the variation of the interfacial normal and shear stresses while rolling aluminium alloy and carbon steel strips. They confirmed earlier studies (Siebel and Lueg, 1933; van Rooyen and Backofen, 1957; Banerji and Rice, 1972; Hum et al., 1996, among others), showing that the coefficient of friction varies from the entry to the exit. As well, they showed that while the use of the “friction hill” in the calculations of the roll pressure distributions offers a useful shortcut in analyses, actual roll pressures possess rounded tops, not saddle points. They indicated that the forward slip increases as the reduction is increased. Further, they demonstrated that both the coefficient of friction and the forward slip drop as the relative velocity between the roll and the strip increases. Jiang et al., (2003) analysed cold, flat rolling of steel and copper strips. They employed a three-dimensional, rigid-plastic finite element model and used a fric- tional shear stress as suggested by Kobayashi et al. (1989). The shear stress there- fore depended on a friction factor, the relative velocity, the yield stress of the rolled metal, a coefficient of friction and two positive constants, defined for both the forward and the backward slip zones. The authors write “... a major handicap to produce an accurate and reliable model ... is the lack of a well-defined friction boundary condition ...”, a statement with which the present author agree whole- heartedly. It is regretted therefore that no specific information regarding the friction model used was provided. There was no reference to the deformation of the work rolls, so it may be inferred that they were taken to be rigid. The predictions of the model compared well to measured roll pressures, the origins of which, however, were not identified. In more recent studies Dvorkin et al. (1997) and Jiang et al. (2004) analysed cold rolling of rigid-plastic strips. In contrast, Gudur and Dixit (2008) considered the behaviour of elastic plastic metals. The effects of both rigid and elastic rolls were studied by Shangwu et al. (1999). The least well-understood phenomena are still the frictional conditions at the interface. In the present work, the coefficient of friction is taken to depend on the relative velocity of the roll and the rolled strip. Muniz (2007) used what is arguably the most complete finite element model of the flat rolling process. He took account of elastic work rolls, elastic plastic rolled strips and a coefficient of friction which was dependent on the relative velocity of the roll and the rolled strip. He presented the distributions of the parameters stress, strain, rate of strain, temperature in the rolled strips and in the rolls. Beyond a statement that the results confirm others’ studies, no experimental sub- stantiation was given. As observed from the review of the literature, a complete model that accounts for the behaviour of all three of the rolling system’s components and is fully An Advanced Finite Element Model of the Flat, Cold Rolling Process 115 substantiated by comparing its predictions to experimental data, is not yet available. Hence, the objective of the present chapter is to include all three components of the rolling system in a finite element model. The elastic deformation of the work roll, the elastic plastic rolled strip and the velocity-dependent coefficient of friction are to be modelled. The magnitude of the average coefficient of friction is determined by an inverse approach, such that the computed roll separating force, the roll torque and the forward slip match the experimental values. Following the validation of the predictive accuracy of the model, the distributions of the roll pressures, interfacial shear stresses and the equivalent strains in addition to the changes of the radius of the deformed roll are documented.
6.2 Modelling the Flat Rolling Process
Pa´czelt writes that the most important aspect of the formulation of a mathematical model is the close correlation of the equations of continuum mechanics and the physical events (Pa´czelt, 1999). In the finite element approach use of the virtual work hypothesis leads to this correlation. Starting with the known initial conditions at time t, and using the Updated Lagrange approach, iteration leads to the state at time t 1 Δt (Dixit and Dixit, 2008): ð t1Δtσ δ t1Δtε t1Δt 5 t1Δt : ij ð ijÞd V R ð6 1Þ t1ΔtV
t1Δt t1Δtσ where R is the virtual work of external forces, ij is the Cauchy stress δ t1Δtε tensor at time t and ð ijÞ is the variation of the virtual deformation. Since the solution at time t 1 Δt is unknown, Eq. (6.1) is transformed to reflect events at time t: ð t1Δt δ t1Δt t 5 t1Δt : tSij ð teijÞd V R ð6 2Þ tV
t1Δt δ t1Δt where tSij is the second Piola Kirchhoff stress tensor and ð teijÞ is the Green Lagrange virtual deformation. The equation of motion is now expressed following Bathe (1996): ð ð ð Δ δ Δε t 1 tσ δ Δη t 1 tσ δ Δε t 5 t1Δt : t Sij ðt ijÞd V ij ðt ijÞd V ij ðt ijÞd V R ð6 3Þ tV tV tV
Employing the constitutive relations
σ 5 EP L : d ij Cijkl dekl ð6 4Þ 116 Primer on Flat Rolling the linear form of the equations of motion is then written as (Bathe, 1996) ð ð ð t EP Δ δ Δ t 1 tσ δ Δη t 1 tσ δ Δ t 5 t1Δt Cijkl t ekl ðt eijÞd V ij ðt ijÞ d V ij ðt eijÞd V R tV tV tV ð6:5Þ EP tσ where Cijkl is the constitutive tensor and ij is the Cauchy deformation tensor at η time t. The terms eij and ij denote the linear and the non-linear changes in the deformation, as referred to the configuration at time t:
1 1 Δe 5 ð Δu ; 1 Δu ; Þ; Δη 5 ð Δu ; 1 Δu ; Þð6:6Þ t ij 2 t i j t j i t ij 2 t k i t k j
The Updated Lagrange method takes detailed account of all non-linear effects, including the material’s non-linearity and large deformations. The virtual work hypothesis then leads to the non-linear discretized algebraic system of equations
t Δ 1 t 5 t1Δt : ½K tf ug ff g fFgð6 7Þ which is solved by the Newton Raphsoniteration,stepbystep(MSC-MARC, 2011). In the present study, the MSC-MARC finite element software is used to analyse the cold rolling process. The material is taken to be elastic plastic. In the first step, the work rolls are treated as rigid. In the second step, the computations are repeated, and the elastic deformation of the rolls is accounted for. Figure 6.1 shows
Figure 6.1 Discretization of the roll. An Advanced Finite Element Model of the Flat, Cold Rolling Process 117 the isoparametric elements (QUAD 4/11) and the refinement of the net near the contact region. A total of 4785 four-node elements are used. The deformation of the rolled strip is assumed to be two-dimensional. The rolling process is taken to be symmetrical, leading to significant simplifications. The rolled material remains isotropic and it obeys the Huber Mises yield crite- rion. Young’s modulus is 69 GPa and Poisson’s ratio is 0.3. The constitutive rela- tion in the plastic region is
0:143 kf 5 270ð1177εÞ ð6:8Þ where kf is the flow strength of the rolled metal and ε is the effective strain. Young’s modulus of the roll material is 210 GPa and the Poisson’s ratio is 0.3. As discussed in Section 5.7, the coefficient of friction in the contact region is given in terms of the relative velocity between the roll and the rolled strip:
2 Δν μ 5 μ arctan ð6:9Þ 0 π C μ where 0 is the maximum Coulomb coefficient of friction and the relative speed between the roll and the rolled strip is Δν 5 νh 2 νt. The subscript h refers to the roll and t indicates the rolled strip. C is a parameter, taken to be C 5 vh=20. Note that Eq. (6.9) allows for the change of algebraic sign of the coefficient of friction at the neutral point.
6.3 Experiments
Cold rolling experiments were conducted on a STANAT experimental rolling mill. The mill was driven by a 12 kW DC motor, through a four-speed gearbox. The top surface speed of the rolls was 1100 mm/s. The surfaces of the 150 mm diameter, 203 mm long tool steel rolls were sandblasted, creating random roughness of Ra 5 0.3 μm. Load cells, placed over the bearing blocks of the top roll, monitored the roll separating forces. The roll torques were measured by transducers placed in the drive spindles. The signals from two photodiodes at the exit led to the exit speed of the rolled strip, and hence to the forward slip. The rotational speed of the top roll was monitored by a tachometer. All data were collected using a DASH 16A/D board and Labview. The 6061 T6 aluminium strips were 1.0 mm thick, 25 mm wide and 300 mm long. They contained 1% Mg, 0.6% Si, 0.3% Cu and 0.2% Cr. Their initial sur- face roughness, both along and across the strips was Ra 5 0.2 μm. Prior to the tests, all strips were cleaned using acetone. Mineral seal oil was used as the lubri- cant, 10 drops on each surface, spread using a roller. Its kinematic viscosity at 40 C was 4.4 mm2/s and at 100 C, 1.53 mm2/s. Its density was 850 kg/m3 at 40 C (Lenard, 2004). 118 Primer on Flat Rolling
6.4 Results
The details of the experiments, used in the calculations, are given in Table 6.1. The reduction and the rolling speed are given in the first two columns. The coefficient of friction, as calculated by Hill’s formula (see Eq. (9.26)), is shown in the third column, while the forward slip, the roll separating force and the roll torque for both rolls follow. The first set of results of the calculations is shown in Figures 6.2 and 6.3.In both figures the distance along the roll gap is given in the abscissa while the roll pressures and the interfacial shear stresses are indicated on the ordinate. As expected, increasing reductions result in higher roll pressures and interfacial shear stresses. As in the one-dimensional models, the location of the maximum roll pressure coincides with the location of the change of the algebraic sign of the shear stress. Accounting for elastic deformation of the rolls leads to larger length of con- tact, resulting in significantly larger roll pressures on the rigid rolls. It is clear that accounting for the elastic deformation of the rolls leads to larger contact length and zones of deformation. The effect of the speed of rolling is also observed in Figures 6.2 and 6.3. As the speed increases, the pressures drop, as do the interfacial shear stresses caused by the improving tribological situation at the contact. Recall that increasing the speed of lubricated rolling consistently resulted in lower coefficients of friction; see Figures 5.28 and 5.29 in Section 5.5.2. The distribution of the total equivalent plastic strain in the rolled strip, undergo- ing 60% reduction at a speed of 0.796 m/s, is shown in Figure 6.4. The grey area indicates the roll. The changes of the roll radius as a function of the reduction and the rolling speed are shown in Figure 6.5. The distributions of the roll pressures are also
Table 6.1 Experimental Details Used in the Calculations
Pass Details Experimental Results
Reduction Roll Speed Coefficient of Forward Roll Force Roll Torque (%) (m/s) Friction (Hill) Slip (%) (N/mm) (N m/mm)
17.86 0.376 0.246 4.161 2750.89 10.88 19.39 0.184 0.204 3.446 2720.13 10.55 17.84 0.875 0.219 3.577 2613.71 8.96 43.04 1.036 0.143 21.262 4615.95 25.84 43.49 0.312 0.135 21.704 4484.31 26.19 44.87 0.833 0.108 1.821 4067.00 25.38 60.19 1.753 0.164 9.919 7173.67 44.10 60.04 0.349 0.150 10.666 6663.80 43.04 62.35 0.796 0.129 3.764 6151.85 41.30 An Advanced Finite Element Model of the Flat, Cold Rolling Process 119
700
600
500
400 p_m r = 17% v = 0.184 m/s τ_m p_r 300 τ_r p_m v = 0.875 m/s Stress (Mpa) 200 τ_m p_r τ 100 _r
0
–100 0123 456 x 1 (mm)
Figure 6.2 The roll pressures (p) and the interfacial shear stresses (τ) at 17% reduction and various rolling speeds. The index “m” refers to rigid rolls while “r” indicates elastic rolls.
1400 p_m r = 60% v = 0.175 m/s τ_m 1200 p_r τ_r 1000 p_m v = 0.796 m/s τ_m p_r 800 τ_r
600
Stress (Mpa) 400
200
0
–200 0246810 x 1 (mm)
Figure 6.3 The roll pressures (p) and the interfacial shear stresses (τ) at 60% reduction and various rolling speeds. The index “m” refers to rigid rolls while “r” indicates elastic rolls. 120 Primer on Flat Rolling
1.08 0.94 0.8 0.67 0.54 0.4 0.27 0.13
Figure 6.4 The plastic deformation of the strip, showing the equivalent strain distribution. The grey area indicates the roll.
r v = 0.184 m/s p = 519 MPa 0.08 = 17% max 0.375 522 0.875 556 r = 44% v = 0.104 560 0.312 635 0.06 0.833 675 r = 60% v = 0.175 856 0.349 986 0.796 1088 0.04 (mm) R Δ
0.02
0.00 010203040 50 60 Contact length (mm)
Figure 6.5 The changes of the roll radius and the length of contact at various speeds and reductions.
indicated in the figure and it is evident that they occur at the largest changes of the radii. The iso-stress distribution on the work roll is shown in Figure 6.6. It is noted that the most highly stressed location is not at the contact zone but is located a few millimetres from the surface. Figure 6.7 indicates the changes of the stress compo- nents as a function of time. While the calculations were performed for a reduction of 60.04%, similar results have been obtained in other cases, as well.
6.5 Comparison of the Experimental and Numerical Results
Tables 6.2 and 6.3 list the comparison of the measured and the computed data. The results of the calculations are given in Table 6.2. In each case the coefficient An Advanced Finite Element Model of the Flat, Cold Rolling Process 121
Figure 6.6 Iso-stress distribution in the work roll.
171 228 285 341 114 398 455 58 507
(MPa)
600 σ e 400 σ 11 σ 200 22 σ 12 0
–200 Stress (MPa) –400
–600
–800 0.00 0.02 0.04 0.06 0.08 0.10 0.12 0.14 Time (s)
Figure 6.7 The maximum stress components in the work roll as function of the time of contact. 122 Primer on Flat Rolling
Table 6.2 Results of the Calculations, Using the Finite Element Method
Rigid Roll Elastic Roll
Forward Roll Roll Torque Coefficient Forward Roll Roll Torque Coefficient Slip (%) Force (N m/mm) of Friction Slip (%) Force (N m/mm) of Friction (N/mm) (N/mm)
3.62 2751.34 10.74 0.242 2.80 2754.03 9.96 0.158 3.32 2721.34 11.11 0.170 1.99 2726.32 10.39 0.105 3.25 2616.91 10.22 0.190 2.36 2615.19 9.51 0.112 5.59 4611.84 28.24 0.128 4.78 4650.39 26.73 0.105 4.76 4466.21 27.62 0.115 3.83 4481.28 26.17 0.094 1.69 4063.77 25.92 0.083 2.01 4146.33 25.18 0.071 10.77 7121.51 49.39 0.150 8.98 7157.77 45.49 0.127 9.48 6581.45 45.71 0.137 7.86 6677.90 43.04 0.116 7.77 6107.88 43.85 0.117 5.93 6143.75 41.26 0.102
Table 6.3 Comparison of the Measured and the Computed Data
Rigid Roll Elastic Roll
Roll Force Roll Torque Forward Slip Roll Force Roll Torque Forward Slip Difference Difference Difference Difference Difference Difference (%) (%) (%) (%) (%) (%)
0.016 2 1.287 2 0.541 0.114 2 8.456 2 1.361 0.044 5.308 2 0.126 0.228 2 1.517 2 1.456 0.122 14.063 2 0.327 0.057 6.138 2 1.217 2 0.089 9.288 6.852 0.746 3.444 6.042 2 0.404 5.460 6.464 2 0.068 2 0.076 5.534 2 0.079 2.128 1.508 1.951 2 0.788 1.828 2 0.727 11.995 0.851 2 0.222 3.152 2 0.939 2 1.236 6.204 2 1.186 0.212 0.000 2 2.806 2 0.715 6.174 4.006 2 0.132 2 0.097 2.166
of friction was chosen such that the difference between the measured and the computed roll separating forces is minimized. It is noted that when the elastic rolls are used the coefficients are significantly less than the ones obtained with the rigid rolls. The percentage differences between the finite element method results and the experimental data are given in Table 6.3. As expected, the roll forces are computed well when either rigid or elastic rolls are used. The roll torque differences are much less when the elastic deformations of the work rolls are accounted for. An Advanced Finite Element Model of the Flat, Cold Rolling Process 123
6.6 Conclusion
The parameters of the cold strip rolling process were measured and calculated, using an advanced finite element model. Elastic plastic deformation of the rolled strip was taken into account. Two approaches were followed: in the first, the roll was assumed to remain rigid, while in the second, its elastic deformation was con- sidered. The coefficient of friction was expressed as a function of the relative velocity between the roll and the rolled strip. In each calculation it was chosen such that the difference between the measurements and the calculations was minimized. The coefficient of friction dropped as the rolling speed was increased. As well, while the roll forces were determined accurately by using either rigid or elastic rolls, the accuracy of the roll torque computations increased when the elastic deformation of the rolls and the elastic plastic deformation of the strip were accounted for.
6.7 Acknowledgements
The financial assistance of The Centre of Excellence for the Development of the Quality of Higher Education in the University of Miskolc, TA´ MOP-4.2.1.B-10/2/KONV-2010-0001 project, is gratefully acknowledged. 7 Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling1
7.1 Introduction
Local buckles are shape defects resulting from the local increase in strip elongation along a line at any position across the strip width. They can be caused by three irregular factors in a cold mill. These are 1. The hot rolled coil ridges or high spots, in which case the elongation will increase locally at the position of the ridge during cold rolling and local buckles, also called ridge- buckles, may occur on the cold rolled strip. 2. The feed stock local yield stress drop, caused during casting and hot rolling when the micro- structure variation across the width resulted in areas that contain coarse grains having a lower yield stress which will elongate more during cold rolling, thus producing local buckles. 3. The work roll crown ridges in the last stand which may be induced by clogging of the roll cooling nozzles or improper maintenance of the cold mill work rolls. In what follows, a mathematical model to simulate strip shape and the local buckle’s formation under the above-mentioned three irregular conditions in the cold rolling pro- cess is described. The shape model includes five underlying models as follows: The first model is a strain rate based finite difference 3D strip deformation model The second model calculates the roll stack deflection and work roll 3D flattening The third model is a work roll thermal crown model The fourth model is an analytical model to determine the tension distribution between stands and after the last stand The fifth model is a local buckling model to predict the local buckling threshold and the shape of the local buckles. By combining the above five models, the software is capable of simulating the formation of local buckles and calculating their limiting values. This chapter intro- duces the models and the simulation results.
1Contributed by Dr. Yuli Liu, chief process engineer and manager of Process Engineering and Development, Quad Engineering Inc. This chapter is a combination of the following publications: Liu et al. (2005, 2007a,b, 2011a,b, 2012). The models have also been presented in Vladimir, B. (Ed.), 2009. Flat-Rolled Steel Processes. CRC Press, Ginzburg.
Primer on Flat Rolling. DOI: http://dx.doi.org/10.1016/B978-0-08-099418-5.00007-X © 2014 Elsevier Ltd. All rights reserved. 126 Primer on Flat Rolling
7.2 Strain Rate Based Strip 3D Deformation Model
7.2.1 Analysis Model of Deformation Zone Figure 7.1 shows the strip deformation zone and the stresses acting on an element in the roll bite. The nomenclatures of geometrical dimensions and stresses are also shown in the figure. 7.2.2 Strip Thickness Distribution in the Roll Bite The strip thickness profile in the roll bite along the rolling direction is assumed to be parabolic, given by x 2 hðx; yÞ 5 h2ðyÞ 1 ½ h1ðyÞ 2 h2ðyÞ ð7:1Þ ld where
ld 5 contact length between the roll and strip; h1(y) 5 strip entry thickness profile in the width direction; h2(y) 5 strip exit thickness profile in the width direction. The entry thickness profile in the first stand is equal to the hot rolled band pro- file h0(y). Under normal rolling conditions, the hot band profile is fitted with the following function: y 2 y 4 h ðyÞ 5 a 1 a 1 a ð7:2Þ 0 0 2 b=2 4 b=2
z x p τ y
σ σ σ σ σ σ x +d x σx σ y +d y y 1 2 y OOy h x h (y) h +dh dx n 1 h (y) x 2 l d
y τxy +dτxy
σy +dσy τ σ +dσ y x x σx dy τ xy y σy
x O dx b x b+Δb
Figure 7.1 Sketch of strip 3D deformation model. Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 127 where
a0, a2, a4 5 fitting coefficients; b 5 the width of the strip. If the hot band has a ridge, another parabolic term is added to the above function within the ridge width to form the ridged profile: 8 ! <> 2 y2yr h0ðyÞ 1 Δhr 1 2 yr 2 wr # y # yr 1 wr h ðyÞ 5 wr ð7:3Þ 0r :> h0ðyÞ y , yr 2 wr or y . yr 1 wr where
h0r(y) 5 hot band profile with a ridge; Δhr 5 maximum height of the ridge; yr 5 y coordinate of the ridge centre; wr 5 half width of the ridge.
7.2.3 Strain Rate and Velocity Field Model It is assumed that the ratio of transverse strain rate to longitudinal strain rate, β,is constant along the rolling direction
ξ βð Þ 5 y ð : Þ y ξ 7 4 x
With this assumption and applying the constant volume principle, the strain rate field (ξx, ξy, ξz, ηxy) and the velocity field (vx, vy) in the roll bite become
1 @h ξ v ð7:5Þ z h @x x β ξ 52 ξ ð7:6Þ y 1 1 β z
1 ξ 52 ξ ð7:7Þ x 1 1 β z
@v @v η 5 x 2 y ð7:8Þ xy @y @x
ð1=11βÞ vx 5 vnðhn=hÞ ð7:9Þ ð y β 1 @h 5 ð : Þ vy 1 β @ vx dy 7 10 0 1 h x 128 Primer on Flat Rolling
where hn and vn are thickness and longitudinal velocity distributions at the neutral plane, respectively.
7.2.4 Yield Criterion and Plastic Flow Equation Considering the yield stress variation along width direction, the Huber Mises yield criterion and the Levy Mises plastic flow equations can be expressed by the stress field (σx, σy, σz, τxy) as follows:
2 2 2 2 ðσx 2σyÞ 1 ðσy 2σzÞ 1 ðσz 2σxÞ 1 6τxy 5 6½kðyÞ ð7:11Þ and
ξ ξ ξ η H x 5 y 5 z 5 xy 5 ð7:12Þ σx 2 σm σy 2 σm σy 2 σm τxy kðyÞ where
1 σ 5 ðσ 1 σ 1 σ Þ m 3 x y z H 5 effective shear strain rate; k(y) 5 yield stress in shear, a function of the width direction in the case of local yield stress variation:
8 ! <> 2 y2yr k0 1 Δk 1 2 yr 2 wr # y # yr 1 wr kðyÞ 5 wr ð7:13Þ :> k0 y , yr 2 wr or y . yr 1 wr where
k0 5 average yield stress in shear in the roll bite, considered to be a constant value; Δk 5 maximum value of local yield stress increase (positive) or drop (negative). Combining the yield condition, the plastic flow equations and the strain rate equations leads to the stress strain rate relationships 8 ð Þ > σ 5 σ 1 2k y ξ 1 ξ > y x ð2 y zÞ > H > < 2kðyÞ σ 5 σ 1 ðξ 1 2ξ Þ : > z x H y z ð7 14Þ > > > kðyÞ :> τxy 5 η H xy Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 129
7.2.5 Surface Friction Model
The surface friction τf is divided into components in the longitudinal and trans- verse directions, τx; τy:
vx 2 vn vsx τx 5 τf qffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi 5 τf ð7:15Þ 2 2 1 2 vs ðvx vnÞ vy
vy vy τy 5 τf qffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi 5 τf ð7:16Þ 2 2 1 2 vs ðvx vnÞ vy
( μp μp # kðyÞ τf 5 ð7:17Þ kðyÞ μp . kðyÞ where p 5 specific roll force; μ 5 friction coefficient; vs 5 relative speed of the roll and the strip surfaces; vsx 5 longitudinal component of the relative speed of the roll and the strip surfaces.
7.2.6 Longitudinal Equilibrium Equation Using slab analysis, the longitudinal equilibrium equation is (Tozawa, 1984):
@ðσ hÞ @h x 1 p 2 2τ 5 0 ð7:18Þ @x @x x
Introducing the stress strain rate relationships and the surface friction equations into the longitudinal equilibrium equation and making further simplifications, the following equations are obtained: sffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi @σ μ ð Þ μ @ H2 2 η2 x 1 2 vsx σ 2 k y 2 vsx 2 h xy 1 β 5 μ # x 2ð2 Þ 0 p kðyÞ @x hvs hH vs @x 1 1 β 1 β ð7:19Þ sffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi @σ @ ð Þ H2 2 η2 x 2 vsx 1 h k y xy 1 β 5 μ . : 2k 2ð2 Þ 0 p kðyÞð7 20Þ @x hvs @x Hh 1 1 β 1 β
The above equations are solved numerically. 130 Primer on Flat Rolling
7.2.7 Entry and Exit Tension Stress Models The entry and exit tension stress models developed by Liu et al. (2005) are employed. The entry tension stress is then ! E v E v ðh =h Þð1=11βÞ σ 5 σ 1 s x1 2 1 1 σ 5 σ 1 s n n 1 2 1 1 σ 1 1 2 υ2 0 1 2 υ2 0 1 s vx1 1 s vx1 ð7:21Þ where
σ1 5 average entry tension stress; vx1 5 entry velocity distribution due to plastic deformation in the roll bite; vx1 5 average entry velocity; σ0 5 residual stress of the incoming strip; Es 5 elastic modulus of the strip; 2 υs 5 Poisson’s ratio of the strip . The exit tension stress is "# E v E v ðh =h Þð1=11βÞ σ 5 σ 1 s 1 2 x2 5 σ 1 s 1 2 n n 2 ð7:22Þ 2 2 2 υ2 2 2 υ2 1 s vx2 1 s vx2 where
σ2 5 average exit tension stress; vx2 5 exit velocity distribution due to plastic deformation in the roll bite; vx2 5 average exit velocity.
7.2.8 Transverse Equilibrium Equation The finite difference form of the transverse equilibrium equation is used to avoid the discontinuities of the partial derivatives in the y direction: Δσ Δτ h y 2 h xy 2 2τ 5 0 ð7:23Þ Δy Δx y
To get better convergence, a simplified form of the transverse equilibrium equation is adopted here based on the method of weighted residuals to get an approximate solution (Ishikawa, 1987): ð ld Δσ Δτ y 2 xy 2 τ 5 ð : Þ h Δ h Δ 2 y dx 0 7 24 0 y x
2Note that the symbol for Poisson’s ration here is υ; it is used to avoid confusion with the symbol for the velocities, ν. Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 131 with the boundary condition at the strip edge y 5 b/2 ð ld hσy dx 5 0 ð7:25Þ 0
7.2.9 Numerical Scheme The above equations are solved using finite difference methods. The flow chart of the calculation procedure is shown in Figure 7.2.
In
Assume neutral plane profile
Mesh the deformation zone
Calculate thickness distribution and its derivatives
Assume lateral spread ratio
Calculate strain rate field and velocity field
Calculate stress field from entry to exit
Calculate residual values of transverse equilibrium equations Modify spread ratio
N Equilibrium equation satisfied? Modify neutral plane profile Y
N Longitudinal stress profile = tension profile at exit?
Y Calculate roll force distribution and lateral spread
Out
Figure 7.2 Flow chart of strip 3D deformation model. 132 Primer on Flat Rolling
The stress fields are calculated from the entry to the exit by solving the longitu- dinal equilibrium equations (7.19) and (7.20) with the initial values determined by Eq. (7.21). There are two main iterative loops in the calculation procedure. The inner loop calculates the lateral spread ratio by satisfying the transverse equilibrium equation (7.24) and the strip edge boundary condition (7.25). The outer loop deter- mines the neutral plane profile by matching the exit tension stress calculated by the longitudinal equilibrium equation with the tension stress determined by the exit ten- sion model (7.22).
7.3 Work Roll Thermal Crown Model
An axisymmetric 2D finite difference model is developed to calculate the work roll temperature field and thermal crown. Since there are several different heat transfer zones along the circumferential direction, the weighted average of the heat fluxes during one revolution is used in the calculation. The heat transfer coefficient formu- lations by Ginzburg (1997), Tseng and Wang (1996), Steden and Tellman (1987) and Devadas and Samarasekera (1986) are adopted to calculate the heat fluxes in different zones. The roll cooling nozzles are controlled independently; therefore, the roll thermal crown ridge effect can be simulated by turning off one or two noz- zles. The governing equation and solving procedure used by Ginzburg (1997) are followed. Extensive measurements of work roll temperature field and work roll thermal crown were carried out at Dofasco’s CPCM3. The work roll thermal crown model was tuned and verified using the data collected during the measurements.
7.4 Roll Stack Deformation Model
The roll stack deformation model for a 4-high mill, considering possible work roll crown ridge and kiss rolling condition4, is shown in Figure 7.3.
7.4.1 Roll Separating Forces The roll separating forces at the drive side and operator side may be different. They are obtained by balancing the force and moment of the roll system:
PL 5 P1 1 Pk 1 FL 1 FR 2 PR ð7:26Þ " 1 Xm P 5 l ðP 1 P 1 F 1 F Þ 1 p Δy y R ð 1 Þ b 1 k R L cj j j Lb 2lb j51 0 1 0 13 ð7:27Þ L 2 L L 2 L 2 F @l 1 w bA 1 F @l 1 b wA5 L w 2 R w 2
3CPCM 5 coupled pickle line and tandem cold mill. 4“Kiss” indicates that the work rolls are in contact. Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 133
Z Pr Pl lb Lb lb
O Db Y
Contact length
q
o D w Y p P P k k
b Fr Fl lwLw lw
Figure 7.3 Roll stack deformation model. where
PL 5 roll separating force at the left side (drive side); P1 5 total rolling force; Fl 5 work roll bending force on the left side (drive side); Fr 5 work roll bending force on the right side (operator side); PR 5 roll separating force on the right side (operator side); Pk 5 total contact force between the top and the bottom work rolls; Lb 5 back-up roll barrel length; Lw 5 work roll barrel length; lb 5 back-up roll neck length; lw 5 work roll neck length; pc 5 combined work roll contact pressure and rolling pressure; 8 < P rolling zone 5 pc : pk work roll to work roll contact zone 0 non-contact zone
P 5 roll pressure per unit width; pk 5 work roll contact pressure per unit width; yj 5 coordinate of the jth element in the y direction (roll axial direction); Δyj 5 the length of the jth element; m 5 number of elements. 134 Primer on Flat Rolling
7.4.2 Roll Equilibrium Equations Two independent roll equilibrium equations are used to determine the inter-roll pressure distribution:
Xm qjΔyj 2 PL 2 PR 5 0 ð7:28Þ j51
Xm qjΔyjyj 2 lbðPR 2 PLÞ 2 PRLb 5 0 ð7:29Þ j51 where q 5 the contact pressure between the back-up roll and the work roll.
7.4.3 Roll Deflection Equations
With the formulation of influence functions, the back-up roll deflection Zb is expressed as
Xm Xm yi Zbi 5 αbijqjΔyj 1 αbLPL 1 αbRPR 1 αΔbjqjΔyj 5 Lb 5 j 1 j 1 : Xm ð7 30Þ 1 αΔbjqjΔyj ði 5 1; 2; ...; mÞ j51 and the work roll deflection Zw is expressed as
Xm Xm Zwi 5 αwijpcjΔyj 2 αwijqjΔyj 2 αFLFL 2 αFRFR j51 j51 ð7:31Þ yi 1 Δwz 1 Kwz ði 5 1; 2; ...; mÞ Lc where
Lc 5 contact length between rolls; Δwz 5 work roll rigid skewing parameter; Kwz 5 work roll rigid movement; α 5 influence functions for different cases; i 5 suffix counter, denoting the position of an element in the axial direction.
7.4.4 Roll Deformation Compatibility Equation The deformation compatibility between the back-up roll and the work roll is
Zbi 1 δbwi 5 Zwi 1 CRbi 1 CRwi ði 5 1; 2; ...; mÞð7:32Þ Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 135 where
CRb, CRw 5 back-up and work roll crown radii, relative to the middle of the roll barrel; δbw 5 contact deformation between the work roll and the back-up roll (Lian and Liu, 1995). Roll crown profile consists of roll initial crown and roll thermal crown. If there is no crown ridge, the roll initial crown profile is assumed to be parabolic. Another parabolic term is added to the roll initial crown profile if a roll crown ridge exists.
8 ! <> 2 y2yr CwðyÞ 1 ΔCwr 1 2 yr 2 wr # y # yr 1 wr C ðyÞ 5 wr ð7:33Þ Rw :> CwðyÞ y , yr 2 wr or y . yr 1 wr where
CRw(y) 5 work roll initial crown include a ridge; Cw(y) 5 parabolic work roll initial crown; ΔCwr 5 maximum height of the work roll crown ridge.
7.4.5 Roll Gap Profile The roll gap profile is
u u d d hi 5 hz 1 ðZ 2 Z Þ 1 ðZ 2 Z Þ 1 2ðδ i 2 δ zÞ wi wz wz wz ww ww ð7:34Þ 2 2ðCRwi 2 CRwzÞði 5 1; 2; ...; mÞ where
hz 5 exit thickness at the centre; u 5 the top work roll; d 5 the bottom work roll; z 5 centre of the strip; δww 5 work roll flattening (Ishikawa, 1987).
7.4.6 Calculation Procedure The kernel part of the roll deformation calculation solves the equation system con- sisting of roll deformation compatibility and roll equilibrium equations. The flow chart of the calculation procedure is shown in Figure 7.4. Considering the inter-roll pressure peaks due to the work roll crown ridge, itera- tion to determine the inter-roll pressure distribution is used in the program. This also determines the inter-roll contact length at the same time. Another iteration loop calculates the kiss pressure, if kiss rolling occurs. 136 Primer on Flat Rolling
In
Assume kiss pressure = 0
Calculate combined work roll pressure
Assume WR & BUR contact length & pressure distribution
Assemble compatibility & equilibrium equations
Modify contact length, pressure distribution Solve compatibility & equilibrium equations
Pressure N distribution converge?
Y Calculate work roll deflection and flattening
Calculate work roll gap profile
Y N Work roll gap> = 0?
Kiss pressure = 0 Iteratively calculate kiss pressure
N Kiss pressure converge? Modify kiss pressure
Y
Out
Figure 7.4 Flow chart of roll stack deformation model.
7.5 Stress Unloading Model
The analytical stress unloading model of Yukawa et al. (1987) is adopted to calcu- late the residual stress. The residual stress σxr is
Ð = b2 2 σ 2 υ σ 1 σ 0 f x2 sð y2 z2Þgh2 dy σxr 5 σx2 2 υsðσy2 1 σz2Þ 2 Ð ð7:35Þ b2=2 0 h2 dy Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 137 where
h2 5 strip thickness at the exit of the roll bite; b2 5 strip width at the exit of the roll bite.
7.6 Local Buckling Threshold Model
The local buckling threshold model is derived based on conventional thin plate buckling theory with a discrete method (Liu et al., 2011a). Applying the governing equation of thin plate bending (Timoshenko and Gere, 1989) to a thin plate with thickness h and width b (h«b), subject to a residual stress distribution with a com- pressive force per unit width Nx 52hσx0 and varying with y across the width, leads to
@2w @4w @4w N @2w 1 2 1 52 x ð7:36Þ @x4 @x2@y2 @y4 D @x2 where w 5 vertical deflection of the plate; D 5 flexural rigidity of the plate given by
Eh3 D 5 ð7:37Þ 12ð1 2 υ2Þ
E 5 Young’s modulus and υ is Poisson’s ratio. Introducing the non-dimensional compressive stress
N b2 k 5 x ð7:38Þ π2D the governing equation becomes
@4w @4w @4w gkπ2 @2w 1 2 1 52 ð7:39Þ @x4 @x2@y2 @y4 b2 @x2 where g is a multiplier of the force Nx. In order to deal with an arbitrary distribution of residual stresses, the discrete method is used by dividing the plate into 2m elements along the width (Bush et al., 2001). For each element, a solution is sought of the form
nπx w ðx; yÞ 5 sin f ðyÞði 5 1; 2; ...; 2mÞð7:40Þ i a i where n is the number and a is the length of half-waves of the deflected curve. 138 Primer on Flat Rolling
Substituting Eq. (7.40) into Eq. (7.39) results in d4f nπ 2 d2f nπ 4 π2 nπ 2 i 2 2 i 1 2 gk f 5 0 ði 5 1; 2; ...; 2mÞð7:41Þ dy4 a dy2 a i b2 a i
2 2 Letting A 5 ðnπ=aÞ and K 5 gkiðπ =b Þ, Eq. (7.41) is rewritten as
d4f d2f ÂÃ i 2 2A2 i 1 A4 2 KA2 f 5 0 ði 5 1; 2; ...; 2mÞð7:42Þ dy4 dy2 i
Assuming that the residual stress ki is constant within one element, the solution to Eq. (7.42) becomes (Timoshenko and Gere, 1989)
2α α 5 iy 1 iy 1 β 1 β 5 ; ; ...; : fiðyÞ Ci1e Ci2e Ci3 cosð iyÞ Ci4 sinð iyÞði 1 2 2mÞð7 43Þ
α β where i and i are real and positive and are given by pffiffiffiffi 2 1=2 αi 5 ½A 1A K ði 5 1; 2; ...; 2mÞð7:44Þ pffiffiffiffi β 5 2 2 1 1=2 5 ; ; ...; : i ½ A A K ði 1 2 2mÞð7 45Þ
The solution function (7.43) applies to each element. Each solution function contains four arbitrary constants Cij ðj 5 1; 2; 3; 4Þ, thus, the general solution across the width of the strip is represented by 2m solution functions, involving 8m arbi- trary constants. The continuity condition is imposed on f ; df=dy; d2f=dy2; d3f=dy3 between the elements. There are two boundary conditions at the left and right sides of the plate. The total conditions are 8m. The resulting 8m linear equations are homogeneous. In matrix form they are
X8m MIJ CJ 5 0 ðI 5 1; ...; 8mÞð7:46Þ J51
The coefficient matrix M is derived based on the continuity conditions and bound- ary conditions. Buckling occurs when a non-zero solution for the coefficients CJ is possible, and the condition for this is that the determinant of the coefficient matrix MIJ vanishes,
jMIJj 5 0 ð7:47Þ
For any chosen non-dimensional residual stress ki, the coefficient matrix M is a function of the multiplier g. The values of g such that the determinant is zero are obtained using the bisection method. Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 139
Once the multiplier g is calculated, the critical residual stress σc is obtained from the maximum value of the input residual stress σmax:
σc 5 gσmax ð7:48Þ
Even though the buckling threshold can be calculated using the above model, the local buckling amplitude of the shape of post-buckling cannot be determined since Eq. (7.46) are homogeneous and have multiple solutions. To calculate the local buckling shape, the energy method in large deflection buckling theory is used.
7.7 Local Buckling Shape Model
The function describing the strip shape after local buckling is assumed to have the following format: 8 2 3 2 = # , > 0 b 2 y c < π 2 π ; 5 4 2 2 ðy cÞ5 x # # 1 : wðx yÞ > f 1 cos sin c y c Lm ð7 49Þ :> Lm Ln 0 c 1 Lm , y # b=2 where f is the nominal amplitude of the buckles to be determined. The widths in the x and y directions are denoted by Lm and Ln. The parameter c indicates the edge of the buckle. Introducing Y 5 y 2 c; X 5 x; α 5 2π=Lm; β 5 π=Ln leads to Y0 52b=2 2 c and Yb 5 b=2 2 c and Eq. (7.49) is rewritten as a function of Xand Y 8 < 0 Y0 # Y , 0 ; 5 2 α β # # : wðX YÞ : f ð1 cos YÞsin X 0 Y Lm ð7 50Þ 0 Lm , Y # Yb
The bending strain energy Vw and the neutral plane strain energy Vc of the strip are calculated following Lian et al. (1987): ()"# ð ð 2 2 D Ln Yb @2w @2w @2w @2w @2w V 5 1 2 2ð1 2 vÞ 2 dX dY w @ 2 @ 2 @ 2 @ 2 @ @ 2 0 Y0 X Y X Y X Y ð7:51Þ
! ð ð 2 Eh Ln Yb @u 1 @w 2 5 ε 1 1 ð : Þ Vc 0 @ @ dX dY 7 52 2 0 Y0 X 2 X
where ε0 is the initial residual strain and u is the displacement function in the lon- gitudinal direction. 140 Primer on Flat Rolling
The governing equation of the neutral plane displacement u is obtained from the equilibrium equation and the stress strain relationship (Lian et al., 1987)
@2u @w @2w 1 5 0 ð7:53Þ @X2 @X @X2
Solving Eq. (7.53) and considering the boundary conditions results in
1 u 52 f 2βð12cos αYÞ2 sin 2βX 1 ε X ð7:54Þ 8 1 where ε1 is the shortened strain of the neutral plane after the strip lost stability. The total strain energy V of a strip of length L is
L V 5 ðVw 1 VcÞð7:55Þ Ln
Integrating Eqs. (7.51) and (7.52) and substituting them into Eq. (7.55): πDf 2LÂÃEhL 3πf 2β2ε 35πf 4β4 V 5 α4 12α2β2 13β4 1 f 2π2β2S 1S 1bε2 1 1 1 4α 2 0 1 1 2α 64α ð7:56Þ where ð Yb X2m 5 ε2 5 ε2 Δ S1 0 dY 0i b Y0 i51 ð Xim 1 Lm 1 S 5 ε ð12cos αYÞ2dY 5 ε ð12cos αY Þ2Δb 0 2π2 0 2π2 0i i 0 i5i0 and the initial residual strain is ε0i 5 σx0i=E ði 5 1; 2; ...; mÞ. Based on the energy principle, the buckled strip reaches its stable state when the total strain energy V is the minimum value:
@V @V @V @V @V 5 0; 5 0; 5 0; 5 0 and 5 0 @ε1 @f @Ln @Lm @c
From these conditions, the following equations are derived
3πf 2β2 ε 52 ð7:57Þ 1 4αb Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 141
ðD=EhÞðα4 1 2α2β2 1 3β4Þ 1 2παβ2S f 2 5 0 ð7:58Þ ðβ4=4Þðð9π=αbÞ 2 ð35=4ÞÞ pffiffiffi 4 3 L 5 L ð7:59Þ n 2 m h2 3 24L4 4L2 @S 3L2ε 35f 2 2 n 2 n 1 2L2 0 1 n 1 1 5 0 ð7:60Þ 2 2 4 2 n @ π2 12ð1 v Þ 2 Lm Lm Lm 2 64
@S 2L2 0 5 0 ð7:61Þ n @c where
@S Δb Xi1 2πðy 2 cÞ 0 52 ε ð 2 Þ i 2 0i yi c sin @Lm 2πL Lm m i5i0
Xi1 @S0 Δb 2πðyi 2 cÞ 52 ε0i sin @c 2πLm Lm i5i0
Solving Eqs. (7.57) (7.61), the parameters f, ε1, Lm, Ln are obtained. In order to solve the above equations, the minimization method of Press is used (Press, 1988). The cost function for the minimization method is defined as
; 5 2 1 2 : FðLm cÞ Z1 Z2 ð7 62Þ where 2 3 h 3 24L4 4L2 @S 3L2ε 35f 2 Z 5 2 4 2 n 2 n5 1 2L2 0 1 n 1 1 1 2 2 4 2 n @ π2 12ð1 v Þ 2 Lm Lm Lm 2 64 @S Z 5 2L2 0 2 n @c
Once the parameters are calculated, the buckling shape is obtained, using Eq. (7.49).
7.8 Flow Chart of the Main Program
Combining the above models, a program that simulates the local shape phenomena in a tandem cold mill is formed. The program is designed in a way that a multi-coil line-up can be simulated in one run. The main flow chart of the local shape simula- tion program is shown in Figure 7.5. 142 Primer on Flat Rolling
Run shape simulation
Get simulation option, number of colis, number of stands
Coil number = 1
Get coil data
Stand number = 1
Get stand data
Call thermal model
Roll profile = initial + thermal Coil number ++
Assume strip exit profile
Call 3D strip deformation model
Call roll deformation model Modify exit profile
N Exit profile converge? Stand number ++
Call stress unloading model
N Last stand? Pass residual stress and exit profile to next stand
Y Call buckling threshold model
Y Buckling? Call buckling shape model
N
Output results
N Last coil?
Y Return to GUI
Figure 7.5 Main flow chart of the shape simulation program. Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 143
7.9 Model Tuning and Verification
The model was tuned and verified under no local buckle conditions using the data collected from a CPCM to establish the base cases for the simulation. The shape meter readings of 20 coils in two line-ups were used for the model tuning and verifi- cation. The shape readings in I-units5 were translated into residual stress and tension stress distributions acting on the shape meter. For each coil, the average value of 200 readings in a stable rolling period was used as the shape reading of the coil. The corresponding process parameters for each coil were then extracted from the data- base of the mill. A tuning factor was added to modify the work roll crown to com- pensate for effects not considered in the model, such as roll horizontal deflection, effects of roll wear and errors in roll grinding. This tuning factor was determined by fitting the shape readings of one coil for each line-up. With a fixed tuning factor, the shape readings of other coils in the line-up were used to verify the model. The model provided a consistent shape prediction for all the coils in each line-up. The shapes of sample coils of the line-ups are shown in Figures 7.6 and 7.7. Although there are still discrepancies, the consistency of the overall match of the measured and predicted shape proves the validity of the model. The buckling models were verified separately using theoretical results and the FEA method (Liu et al., 2011b).
7.10 User Interface
A graphic user interface has also been developed to integrate the sub-models and to manage the simulation options and the input and output data, and then graphically
120 Predicted Measured 100
80
60
40
20 Tension stress distribution (MPa) stress distribution Tension 0 0 100 200 300 400 500 600 Distance to strip centre (mm)
Figure 7.6 Sample comparison of first line-up.
5The I-unit is a measure of strip waviness. 144 Primer on Flat Rolling
70 Predicted 60 Measured
50
40
30
20
10 Tension stress distribution (MPa) stress distribution Tension 0 0 100 200 300 400 500 600 Distance to strip centre (mm)
Figure 7.7 Sample comparison of second line-up. display the simulation results. The simulation results are output to data files which can be further processed by the user. The major results currently selected for graphical display in the user interface include 3D longitudinal stress, 3D transverse stress, 3D vertical stress, 3D shear stress, lateral spread ratio, neutral plane profile, exit velocity profile, entry tension stress profile, exit tension stress profile, residual stress distribution, inter-roll con- tact pressure distribution, exit thickness profile, roll thermal profile, roll force dis- tribution and local buckling shape. Since the local shape defects are the main focus of this simulation program, three abnormal rolling conditions are listed as the main simulation options. These abnormal rolling conditions are simulated and discussed in subsequent sections.
7.11 Base Case for Local Shape Defect Simulation
To simulate the local shape defects from various sources, an actual rolling case is selected as the base in which no local shape defect was produced. The various causes of local shape defects are then added to the base case to examine their effects. In the calculations, a 5-stand mill was considered. The work roll diameters ranged from 495 to 516 mm while the back-up roll diameters varied from 1400 to 1511 mm. The thermal conductivitywastakentobe0.06W/mm Candthe thermal expansion coefficient was 0.000013 mm/ C.Thespecificheatwas 434 J/kg C. The entry thickness of the strip into the first stand was 2.442 mm and into the last stand, 0.417 mm. The coefficient of friction varied from a high 0.05 in the first stand to 0.028 in the last stand. Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 145
7.12 Effects of Entry Strip Profile Ridge
The feed stock of cold strip mills are coils rolled by hot strip mills. If abnormal conditions, such as excessive roll wear, occur in the hot strip mill, thickness profile ridges are produced on the hot rolled strip. When the hot rolled strip with ridges is subsequently fed into a cold mill, local buckles are produced in the cold rolled strip. The extra material forming the thickness ridge may be divided into three por- tions in subsequent cold rolling. A portion of the material will remain in the form of a thickness ridge in the cold rolled strip due to a local roll flattening increase, caused by the higher local roll force when rolling the thickness ridge. The second portion of the material will produce a local elongation increase, causing a local strip compression increase that may induce local buckles. The third portion of the material will spread laterally, which actually has the effect of attenuating the local buckles and the thickness ridges of the cold rolled strip. The percentage of each portion depends on the parameters of the rolls, products and the rolling process and may vary over a wide range. This shape simulation program is capable of quantita- tively determining what happens when rolling a thickness profile ridge. Figures 7.8 7.16 show the major simulation results when cold rolling a coil with two thickness ridges in a five-stand fully continuous tandem mill. The height of the thickness ridges is assumed to be 2% of the entry strip thickness, 0.051 mm. The thickness ridges are assumed to be parabolically distributed over the 100 mm width and symmetrical about the centre line of the strip. The strip thickness profiles after each stand are shown in Figure 7.8. Even though the height of the ridges is continuously reduced from stand to stand, the ridges could not be totally eliminated. There are still thickness ridges, about 0.004 mm in height, left in the final product. The additional reductions to the thick- ness ridges will cause peaks in the roll force distribution as shown in Figure 7.9. Figure 7.10 shows the 3D stress distributions in the roll bite when rolling a thickness ridge. It is clear that the thickness ridges cause reduced normal stresses
2 Stand 1 Stand 2 Stand 3 Stand 4 Stand 5
1.5
1
0.5 Exit thickness profile (mm) Exit thickness
0 0 400 800 1200 1600 Distance to roll end (mm)
Figure 7.8 Exit thickness profile. 146 Primer on Flat Rolling
16,000 Figure 7.9 Roll force transverse distribution.
12,000
8000
Stand 1 4000 Stand 2 Stand 3 Roll force distribution (N/mm) distribution Roll force Stand 4 Stand 5 0 0 400 800 1200 1600 Distance to roll end (mm)
Figure 7.10 3D stress distribution in roll bite.
370 270 170 70 –30 –130 0 3 distribution (MPa) distribution 0 Longitudinal stress 200 6 9 Half width (mm)400 12 600 15 Contact arc (mm) 800 18
0
–300
–600
(MPa) 0 0 3 200 6 9 Vertical stress distribution Vertical Half width (mm)400 12 600 15 Contact arc (mm) 800 18 Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 147
0.06 Stand 1 0.05 Stand 2 Stand 3 0.04 Stand 4 Stand 5 0.03
0.02
0.01 Lateral spread ratio Lateral
0
–0.01 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.11 Lateral spread ratio distribution.
6
5
4
3 Stand 1 Stand 2 2 Stand 3 Stand 4 Neutral plane profile (mm) Neutral Stand 5 1 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.12 Neutral plane profile. locally in all three directions. The ridges also induce the local shear stress variation due to lateral spread and speed variation. The thickness ridge will also induce lateral spread around it. However, the mag- nitude of the lateral spread ratio, which is defined as the ratio between lateral strain rate and longitudinal strain rate, is much smaller in the region of the thickness ridge than that in the strip edge. The lateral spread ratio in the region of the thickness ridge also decreases from the first stand to the last stand as shown in Figure 7.11. The lateral spread ratio at the strip edge, however, may not always decrease from the first to the last stand. Because of the thickness ridge and lateral spread at the edge, the neutral planes are not “planes” anymore. They are curved by the material flow variation and 148 Primer on Flat Rolling lateral spread as shown in Figure 7.12. The curved portions are mainly at the region of the ridge and the strip edge. The relative exit speed profile, which is defined as the ratio of the strip longitu- dinal speed at the roll bite exit to the roll linear speed, is also curved around the ridge and the strip edge as shown in Figure 7.13. The entry tension stress profile, which mainly depends on the residual stress formed in the previous stand and the entry speed profile of the current stand, is also influenced by the thickness ridge (Figure 7.14). The exit tension stress drops around the ridge area are evident as shown in Figure 7.15.
1.06
1.05
1.04
Stand 1 1.03 Stand 2 Stand 3 Relative exit velocity profile velocity exit Relative Stand 4 Stand 5 1.02 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.13 Relative exit velocity profile.
Stand 1 400 Stand 2 Stand 3 Stand 4 Stand 5 200
0 Entry tension profile (MPa)
–200 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.14 Entry tension stress profile. Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 149
Stand 1 400 Stand 2 Stand 3 Stand 4 Stand 5 200
0 Exit tension profile (MPa)
–200 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.15 Exit tension stress profile.
200 Stand 1 Stand 2 Stand 3 100 Stand 4 Stand 5
0
Residual stress profile (MPa) –100
0 200 400 600 800 Distance to strip centre (mm)
Figure 7.16 Residual stress profile.
However, the amount of tension stress drop decreases substantially from the first stand to the last stand. The exit tension stress drop in stand 5 is only about a quarter of that in stand 1. A similar phenomenon also occurs in the residual stress profile as shown in Figure 7.16. The interaction among reduction, lateral spread, tension, residual stress, roll bending and flattening of all stands determines the final residual stress due to thickness ridge rolling, which will dictate the local shape of the product. One feature that distinguishes the local hot band ridge defects from other causes, such as yield stress drop or roll crown ridge, is that both local thickening and local buckles exist at the same position as shown in Figures 7.8 and 7.16. 150 Primer on Flat Rolling
7.13 Effect of Local Yield Stress Drop
There are abnormal metallurgical or physical conditions that may cause non- uniform yield stress across the strip width. For example, microstructure changes occurring in the finishing mill as a result of temperature variation in various zones of the strip may result in yield stress variations in the hot band. If a narrow slice of the hot rolled strip is softer than the rest, local buckles may be induced as a result of cold rolling. To see the effects of local yield stress drop, a parabolic yield stress valley with 15% yield stress drop in a 100-mm-wide slice is assumed. Yield stress distributions for each stand are shown in Figure 7.17. The local yield stress drops will induce a roll force drop at corresponding posi- tions as shown in Figure 7.17. However, the percentage of roll force drop is only about 2 3%, which is much smaller than the 15% yield stress drop. The reason is that the local roll force drops reduce the local roll flattening, which then reduces the local roll gaps and increases the local reductions slightly, which in turn offsets part of the roll force drops (Figure 7.18). The slightly increased local reductions cause strip exit speeds to increase locally as shown in Figure 7.19, which in turn changes the neutral plane profiles as shown in Figure 7.20. The slightly increased local reductions also cause compression at the entry to and exit from the roll bites and produce local tension stress drops at the entry and exit sides as shown in Figures 7.21 and 7.22. Because of the local exit tension stress drops, there are local compressions in the residual stress profile after unloading as shown in Figure 7.23. The local com- pressions in the residual stress profile would produce local buckles if they exceeded certain limits. Contrary to the local shape defects produced by hot band ridges, in
500
400
300
200 Stand 1 Stand 2 100 Stand 3
Yield stress in shear profile (MPa) Yield Stand 4 Stand 5 0 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.17 Assumed yield stress profile. Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 151
14,000 Figure 7.18 Roll force profile.
10,500
7000 Stand 1 Stand 2 3500 Stand 3 Stand 4 Roll force distribution (N/mm) distribution Roll force Stand 5
0 0 400 800 1200 1600 Distance to roll end (mm)
1.06 Figure 7.19 Relative exit velocity profile.
1.05
1.04
Stand 1 1.03 Stand 2
Relative exit velocity profile velocity exit Relative Stand 3 Stand 4 Stand 5 1.02 0 200 400 600 800 Distance to strip centre (mm)
6 Figure 7.20 Neutral plane profile. 5
4
3 Stand 1 Stand 2 2 Neutral plane profile (mm) Neutral Stand 3 Stand 4 Stand 5 1 0 200 400 600 800 Distance to strip centre (mm) 152 Primer on Flat Rolling
Figure 7.21 Entry tension Stand 1 400 Stand 2 stress profile. Stand 3 Stand 4 Stand 5 200
0 Entry tension profile (MPa)
–200 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.22 Exit tension stress Stand 1 400 Stand 2 profile. Stand 3 Stand 4 Stand 5 200
Exit tension profile (MPa) 0
–200 0 200 400 600 800 Distance to strip centre (mm)
200 Figure 7.23 Residual stress Stand 1 profile. Stand 2 Stand 3 100 Stand 4 Stand 5
0
–100 Residual stress profile (MPa)
0 200 400 600 800 Distance to strip centre (mm) Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 153
0.5
0.4
0.3 Exit thickness profile (mm) Exit thickness
0.2 0 400 800 1200 1600 Distance to roll end (mm)
Figure 7.24 Thickness profile after stand 5. which local thickening occurs at the location of the local buckles, local strip thin- ning would occur at the position of the buckles were they caused by local yield stress drops as shown in Figure 7.24.
7.14 Roll Cooling Nozzle Clog or Work Roll Crown Ridge Effect
Abnormal conditions in the cold mill may also cause local shape defects. If some roll cooling nozzles are clogged, a roll thermal ridge may be formed causing local buckles. As an example, assuming that two adjacent work roll cooling nozzles are clogged, a 0.007-mm work roll thermal crown ridge will be produced at thermal steady state conditions for the base case simulated. If the roll ridge occurs in the early stands, the potential local shape defects produced could be ironed flat in sub- sequent stands before the buckles occur. However, if the work roll thermal ridge is in the last stand, local buckles may be produced in the final product. Figure 7.25 shows the roll force distributions, assuming that four roll cooling nozzles are clogged at stand 5, two in each half of strip width and symmetric to the strip centre line. Maximum 0.007-mm roll thermal crown ridges are built up at the thermal steady state conditions of stand 5, which will produce the roll force peaks in stand 5 as shown in Figure 7.25. Local reduction increases induced by the roll force peaks will cause local drop of the entry tension stress profile, as shown in Figure 7.26, and a local drop in the exit tension stress profile, as shown in Figure 7.27. The local drop in exit tension stress profile will cause a local compression in the residual stress profile after unloading as shown in Figure 7.28. 154 Primer on Flat Rolling
10,000
5000 Stand 1 Stand 2 Stand 3 Roll force distribution (N/mm) distribution Roll force Stand 4 Stand 5 0 0 400 800 1200 1600 Distance to roll end (mm)
Figure 7.25 Roll force profile.
500 Stand 1 Stand 2 400 Stand 3 Stand 4 300 Stand 5
200
100
Entry tension profile (MPa) 0
–100 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.26 Entry tension stress profile.
7.15 Identification of Causes of Local Buckles
The effects of friction coefficient variations in the width direction and feed stock local residual stress are also simulated. In the practical variation range, they are unlikely to cause local shape buckles. Therefore, they are excluded from the possible causes of the local shape defects. Since the local residual stress induced by upstream stands can be ironed out, the working conditions of the upstream stands are excluded from the causes of the local buckles. The remaining possible causes of local shape defects are then the hot band ridge, the yield stress local drop and the abnormal rolls Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 155
500 Stand 1 400 Stand 2 Stand 3 Stand 4 300 Stand 5
200
100 Exit tension profile (MPa) 0
–100 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.27 Exit tension stress profile.
200 Stand 1 Stand 2 150 Stand 3 Stand 4 100 Stand 5
50
0
Residual stress profile (MPa) –50
–100 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.28 Residual stress profile. or operating conditions in the last stand. Determination of which of the three irregu- lar factors in a cold mill causes the occurrence of the observed local buckles requires a method to identify their specific causes. This is accomplished using simulation by measurement and analysis of the thickness profile at buckled regions across the strip width. Thus, three causes of local buckles are identified: 1. Local increased strip thickness and local buckles at the same position indicating feed stock ridge as the cause. 2. Local decreased strip thickness and local buckles at the same position, thus indicating that the work roll cooling system and condition of the work rolls as well as the operating conditions of the last stand should be checked first for any abnormalities. 156 Primer on Flat Rolling
Measuring strip thickness across strip width
Local increased strip Local decreased strip thickness and local thickness and local buckles at same position buckles at same position
Feed stock Lower yield stress Abnormalities ridge of coarse grains in at last stand buckling region
Local yield Roll crown ridge stress drop at last stand
Figure 7.29 Flow chart of the procedure to identify causes of local buckles.
3. Local decreased strip thickness and local buckles at the same position without any abnor- malities in the last stand, indicating local yield stress drop as the cause of the local buckles. This can be identified by checking the yield strength or microstructure across the strip width. Figure 7.29 shows the flow chart of the above described procedure to identify the causes of local buckles.
7.16 Predicting Limiting Values for Factors Causing Local Buckles
The local buckling simulation models are capable of calculating the limiting values of the factors causing local buckles to start occurring. These limiting values are important for quality control of cold rolled coils. A sample calculation was per- formed for a 0.275-mm-thick product with the local compression width of 110 mm. Assuming a parabolic local compression stress distribution, a critical local buckle stress for this case is 12.96 MPa. The limiting value of the feed stock ridge to induce this critical local compression residual stress in the final product is 0.046 mm as shown in Figures 7.30 and 7.31. Figure 7.30 shows the strip transverse thickness distribution at the entry side of each stand. Figure 7.31 shows the residual stress transverse distribution after each stand. From Figure 7.31, it is seen that while the local compression residual stress induced by feed stock ridge is quite large after the first pass, it decreases pass after pass. The local compression residual stress after the fifth pass is only about 18% of that after the first pass. Even though the critical local buckling stress decreases quickly as the strip is getting thinner, the likelihood of local buckles caused by feed stock ridge may not increase quickly since the local compression residual stress also decreases as the strip is getting thinner. This phenomenon is also the rea- son that the calculated limiting values for the feed stock ridge to induce local Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 157
3 Stand 1 Stand 2 Stand 3 Stand 4 Stand 5
2
1 Entry profile (mm) thickness
0 400 800 1200 1600 Distance to roll end (mm)
Figure 7.30 Thickness profile when the feed stock ridge is at its limiting value.
100 Stand 1 80 Stand 2 Stand 3 60 Stand 4 Stand 5 40
20
0
–20 Residual stress profile (MPa) –40
–60 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.31 Local compression residual stresses induced by the ridge at the limiting value. buckles are larger than the results of other calculations (Tieu et al., 2008). Larger entry thickness is another reason for the larger limiting value of the feed stock ridge. Nevertheless, since retained ridges will also cause build-up in the coil (Blazevic, 2002), the feed stock ridge may not be allowed even though it may be smaller than the limiting value for local buckles to occur. Therefore, the limiting values of feed stock ridge causing coil build-up need to be further investigated and compared with the limiting values of feed stock ridge causing local buckles. The smaller limiting value either from local buckling condition or coil build-up condi- tion should be used as the limiting value for hot band ridges. 158 Primer on Flat Rolling
The limiting value of the local yield stress drop to induce this critical local com- pression residual stress is 12.08 MPa as shown in Figures 7.32 and 7.33. Figure 7.32 shows the yield stress in shear along the strip width at each pass. Figure 7.33 shows the residual stress distribution along the strip width after each pass. From Figure 7.33, it is seen that the local compression residual stresses are almost the same after each pass. This phenomenon indicates the likelihood that the local buckling, induced by the local yield stress drop, increases quickly pass after pass as the strip is getting thinner. Since the increased local elongation caused by the local yield stress drop may also cause coil build-up, the limiting values of the
450 Stand 1 Stand 2 Stand 3 Stand 4 Stand 5
400
350 Yield stress in shear (MPa) Yield 300
0 200 400 600 800 Distance to strip centre (mm)
Figure 7.32 Shear yield stress variation.
100 Stand 1 Stand 2 80 Stand 3 60 Stand 4 Stand 5 40
20
0
–20
Residual stress profile (MPa) –40
–60 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.33 Local compression residual stress induced by local yield stress drop at its limiting value. Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 159 local yield stress drop causing coil build-up need to be further investigated. The smaller limiting value from local buckling condition or coil build-up condition should be used as the actual limiting value of the local yield stress drop. Comparing Figure 7.33 to Figure 7.31, it is concluded that the local buckles are more and more likely to be induced by the local yield stress drop than by the feed stock ridge as the strip is getting thinner. The limiting value of the last stand work roll diameter crown ridge to induce this critical local compressive residual stress is 0.010 mm as shown in Figures 7.34 and 7.35.
0.08 Stand 1 Stand 2 Stand 3 0.06 Stand 4 Stand 5
0.04
0.02 Initial work roll profile (mm)
0 0 400 800 1200 1600 Distance to roll end (mm)
Figure 7.34 Last stand work roll crown ridge at its limiting value.
100 Stand 1 80 Stand 2 Stand 3 60 Stand 4 Stand 5 40
20
0
–20 Residual stress profile (MPa) –40
–60 0 200 400 600 800 Distance to strip centre (mm)
Figure 7.35 Local compression residual stress induced by the last stand work roll crown ridge at its limiting value. 160 Primer on Flat Rolling
Figure 7.34 shows the work roll radius crown curve for each stand. Figure 7.35 shows the residual stress transverse distribution after each stand. The results show that the local compression residual stress is sensitive to the roll crown ridge. Small roll crown ridge at the last stand may induce local buckles. Since the increased local elongation caused by the roll crown ridge may also cause coil build-up, its limiting values need to be further investigated. The smaller limiting value from local buck- ling condition or coil build-up condition should be used as the actual limiting value of the roll crown ridge. A summary of the calculation conditions and the limiting values causing local buckles for this sample case is shown in Table 7.1. Both finished product thickness and local compression width have a very signifi- cant influence on the limiting values for the factors causing local buckles. Figure 7.36 shows the variation of limiting values of feed stock ridge height versus local compression width for three different strip thicknesses. It is seen that the lim- iting values of feed stock ridge height increase as the strip thickness increases and the local compression width decreases. Figure 7.37 shows the variation of the limiting values of the local yield stress drop versus local compression width for three different strip thicknesses. It is seen that the limiting values of the local yield stress drop increase as the strip thickness increases and the local compression width decreases.
Table 7.1 Summary of Conditions and Limiting Values
Feed Product Local Buckled Local Limiting Limiting Limiting Stock Thickness Compression Width Buckle Value of Value of Value of Thickness Width Critical Feed Local Yield Last Stand Stress Stock Stress Roll Crown Ridge Drop Ridge
2.442 mm 0.275 mm 110 mm 96.8 mm 12.96 MPa 0.046 mm 12.08 MPa 0.010 mm
0.16 h=0.25 h=0.275 h=0.30 0.12
0.08
0.04 Feed stock ridge height (mm) stock Feed
0 70 80 90 100 110 120 130 140 150 Ridge width (mm)
Figure 7.36 Limiting values of feed stock ridge height versus the local compression width. Flat Rolling Simulation and Reduction of Local Buckles in Cold Rolling 161
h=0.25 40 h=0.275 h=0.30
30
20
10 Yield stress drop (MPa) Yield
0 70 80 90 100 110 120 130 140 150 Ridge width (mm)
Figure 7.37 Limiting values of the local yield stress drop versus the local compression width.
h=0.25 0.03 h=0.275 h=0.30
0.02
0.01 Work roll ridge Work height (mm)
0 70 80 90 100 110 120 130 140 150 Ridge width (mm)
Figure 7.38 Limiting values of work roll crown ridge versus local compression width.
Figure 7.38 shows the variation of limiting values of the work roll crown ridge at the last stand versus the local compression width for three different strip thick- nesses. It is seen that the limiting values of the work roll crown ridge increase as the strip thickness increases and the local compression width decreases.
7.17 Reduction of Local Buckles
Even though the cold mill itself may cause local buckles, the majority of the local buckles are caused by the feed stock from the hot mill (Melfo et al., 2006). Therefore, proper monitoring of the hot band profile and mechanical properties 162 Primer on Flat Rolling will be the first choice to reduce local buckles. Since hot band ridges are most likely related to uneven roll wear, the measures to cause uniform roll wear, such as on-line roll grinding and work roll axial shifting, are suggested for reducing local buckles. If all measures in the hot strip mills fail and ridges are produced on the hot band, flattening the ridges before cold rolling using a mill stand with very high local rigidity (Liu et al., 2011b, 2012) can be used to reduce the local buckles sig- nificantly. The uniformity of the metallurgy-related factors in the hot strip mills and casters should be properly maintained to avoid the local yield stress drop and to reduce local buckles. Finally, rolls, roll cooling systems and other operational conditions of the cold mill need to be carefully maintained to avoid the local shape defects produced solely by the cold mill. 8 Material Attributes
8.1 Introduction
The metal’s resistance to deformation is often referred to by several names. It may be called the flow stress, the flow strength or the constitutive relation; the bottom line is that a relationship of the metal’s strength to other, independent variables is being considered. The best identification is the term “resistance to deformation” since it describes a material property and its meaning is clear: it indicates how the material reacts when it is loaded and deformed by external forces. The need for understanding the intricacies of the material’s resistance to deformation has been indicated in Chapters 5 and 6. This includes two ideas: the appreciation of the physical and metallurgical capabilities and the response of the materials while in service as well as the development of mathematical models of the metals’ resistance to deformation. The former is necessary to provide insight and to aid in the design and the planning of the metal forming processes. The lat- ter is critical for the success of the predictive models of the flat rolling process. Several steps need to be completed in order to reach these objectives. These are listed below:
G Determine the independent variables that are expected to affect the metal’s resistance to deformation. G Determine the metal’s resistance to deformation in an appropriate test, one that allows the variation of the independent variables over an appropriate range of magnitudes. G Develop through mathematical modelling (e.g. non-linear regression analysis, artificial intelligence or storing data in a multi-dimensional matrix of data) a true stress true strain, strain rate, temperature, etc. relation. In what follows, selected attributes of some of the steel and aluminium alloys used in the metal forming industry will be briefly reviewed and will be com- pared, with special attention paid to the automotive industry. Recently developed alloys will also be briefly introduced. Traditional testing techniques to determine the metals’ attributes will be discussed next; their advantages and disadvantages are given. This will be followed by a presentation of the mathematical descrip- tion of some of the attributes. Metallurgical events will also be discussed and the grain structures accompanying hot or cold deformation processes will be pre- sented. Most of the comments will concern steels, reflecting the experience of the writer. Hot rolling of aluminum is discussed in Chapter 11.
Primer on Flat Rolling. DOI: http://dx.doi.org/10.1016/B978-0-08-099418-5.00008-1 © 2014 Elsevier Ltd. All rights reserved. 164 Primer on Flat Rolling
8.2 Recently Developed Steels
The traditional metals used in the metal forming industry include the alloys of steel, aluminium, copper and titanium. New alloys have been developed in the last several decades, mostly driven by the need of the automotive industry to reduce weights and gasoline consumption and thus reduce air pollution. This need created one of the most important current objectives of the carmakers, which is to develop the technol- ogy to produce lightweight components. The materials used in this regard must have attributes that include high strength and high ductility. The new ferrous metals being introduced include the interstitial free (IF) steels, bake hardenable steels, transformation-induced plasticity (TRIP) steels, the high-strength low-alloy (HSLA) steels, dual phase (DP) steels and martensitic and manganese boron steels, having yield strengths that vary from a low of 200 up to 1250 MPa. The elongation of these steels decreases as the strength increases, from a high of nearly 40% to a low of 4 5%, affecting the design of the subsequent applications. A recent review (Ehrhardt et al., 2004) lists many of these steels and indicates that light construction steels with induced plasticity possess tensile strength in the order of 1000 MPa and remarkably high total elongation of 60 70%. The website of the American Iron and Steel Industry also includes up-to-date information concerning the description and the processing of recently developed steel alloys. As given in the site, advanced high-strength steels (AHSSs) in use in the automotive industry include the DP steels the microstructure of which includes ferrite and up to 20% and 70% volume fraction of martensite. While the use of bainite helps to enhance the capability to resist stretching on a blanked edge, the ferrite phase leads to high ductility and creates high work hardening rates, which give the DP steels higher tensile strength than conventional steels. Further, TRIP steels are also used, the microstructure of which consists of a ferrite matrix containing a dispersion of hard second phases martensite and/or bainite in addition to retained austenite in volume fractions greater than 5%. During deforma- tion, the hard second phases create a high work hardening rate while the retained austenite transforms to martensite, increasing the work hardening rate at higher strain levels. The complex phase (CP) steels consist of a very fine microstructure of ferrite and a higher volume fraction of hard phases that are further strengthened by fine precipitates. In the martensitic (MART) steels the austenite that exists during hot rolling or annealing is transformed almost entirely to martensite during quench- ing on the run-out table or in the cooling section of the annealing line. All AHSSs are produced by controlling the cooling rate from the austenite or austenite plus fer- rite phase, either on the run-out table of the hot mill (for hot rolled products) or in the cooling section of the continuous annealing furnace (continuously annealed or hot dip-coated products). AHSS cooling patterns and resultant microstructures are schematically illustrated on the continuous cooling-transformation diagram, avail- able for examination in the American Iron and Steel Institute (AISI) website. The cooling patterns are designed on the bases of mathematical models, which attempt to predict the structures and properties resulting from the processing technique. Material Attributes 165
Figure 8.1 Microstructure of an extra-deep-drawing ferritic steel 3003 . Source: Reproduced from http:// www.mittalsteel.com/.
Research is continuing in the development of twinning-induced plasticity steels and lightweight steels with induced plasticity (Gigacher et al., 2005)1.
8.2.1 Very Low Carbon Steels The structure of these steels is fully ferritic. A micrograph, reproduced from the website http://www.mittalsteel.com is shown in Figure 8.1. While the strength of these steels is very low, their very high formability makes them ideal candidates for parts that carry low loads but require high-strain carrying ability during the forming process. Automotive components and motor lamination steels are potential uses.
8.2.2 IF Steels These steels contain less than 0.003% C. The nitrogen level is also reduced during their preparation and the remaining carbon and nitrogen are tied up using small amounts of alloying elements, such as Ti or Nb. The steels are finish rolled above 950 C. Their strengths are low but they possess very high formability, especially after annealing (138 165 MPa yield strength, 41 45% elongation). Their structure is very similar to that shown in Figure 8.1, above.
8.2.3 Bake-Hardening Steels The carbon content is even lower, 0.001% C. The steels harden during the paint- curing cycle, performed usually at 175 C, for 30 min. The hardening is caused by the precipitation of carbonitrides. The as-received yield strength of the steel is 210 310 MPa; after baking and a 2% pre-strain these rise to 280 365 MPa. There is little change of the tensile strength but the dent resistance is increased. These
1I am grateful to Dr. G. Nadkarni, Mittal Steel, Southfield, MI, and to Dr. J. B. Tiley, hot rolling consul- tant, to bring these grades of steel to my attention. 166 Primer on Flat Rolling
Figure 8.2 BH steel. Source: Reproduced from http:// www.mittalsteel.com/.
grades are extensively used in automotive outer body panels. A typical microstruc- ture of a bake-hardening (BH) steel is given in Figure 8.2.
8.2.4 TRIP Steels These steels are highly alloyed and have been heat treated to produce metastable (that is, not fully stable with respect to transformation) austenite plus martensite. When subjected to permanent deformation, the austenite experiences strain-induced transformation to martensite. A tempering process may follow the transformation. The steels are highly ductile and are strain rate sensitive. Their ten- sile strength can reach magnitudes as high as 800 MPa. They respond well to bake hardening and an extra 70 MPa strength is the result. These steels are one of the newest families of AHSSs currently under development for the automotive indus- try. The steels have a microstructure of soft ferrite grains with bainite and retained austenite. The hard martensite delays the onset of necking, resulting in a product with high total elongation, excellent formability and high crash energy absorption. In addition, TRIP steels also exhibit extremely high fatigue endurance limits, thereby providing excellent durability performance. The micrograph of Mittal’s TRIP steel is shown in Figure 8.3.
8.2.5 HSLA Steels The HSLA steels, often referred to as microalloyed steels, are low-carbon steels with the strength increased by small amounts of alloying elements such as niobium, vanadium, titanium, molybdenum or boron, singly or in combinations. Their tensile strength may reach 450 MPa and their ductility may be as high as 30%. Thermomechanical processing is used to affect their mechanical and metallurgical attributes. Arguably, one of the best collections of information concerning some of these alloys appears in the Proceedings of the International Conference on the Thermomechanical Processing of Microalloyed Austenite, held in Pittsburgh, in Material Attributes 167
Figure 8.3 TRIP steel. Source: Reproduced from http:// www.mittalsteel.com/.
Figure 8.4 Micrographs of a boron steel; (A) ε_ 5 1:7 3 1022 s21 and ε 5 0:37; (B) ε_ 5 1:7 3 1021 s21 and ε 5 0:46 (Maki et al., 1981).
1981. Micrographs of many of these steels under a large number of processing con- ditions have been published at that conference. In what follows, two examples are shown. Figure 8.4 shows two micrographs (Cuddy, 1981) of a 0.057% C, 1.44% Mn, 0.112 Nb steel, reheated to 1200 C and reduced 55% in five passes. In (A) the steel, at 1100 1070 C, is fully recrystallized, while in (B) at 1000 960 C, the grain elongation is pronounced.
8.2.6 DP Steels These are low-alloy steels, similar to the HSLA steels. Their tensile strength is somewhat higher, 550 MPa. The structure, shown in Figure 8.5, contains approxi- mately 20% martensite in a ductile ferrite matrix. As written on Mittal’s website, DP steels are one of the important new AHSS products developed for the automo- tive industry. Their microstructure typically consists of a soft ferrite phase with dis- persed islands of a hard martensite phase. The martensite phase is substantially stronger than the ferrite phase. 168 Primer on Flat Rolling
Figure 8.5 A typical DP steel. Source: Reproduced from http:// www.mittalsteel.com/.
60 Austenitic Deep-drawing steels stainless steels 50
40 BH steels TRIP steels Duplex stainless 30 steels
Elongation (%) 20 Aluminium DP steels HSLA steels 10
Magnesium 0 0 100 200 300 400 500 600 Yield strength (MPa)
Figure 8.6 A compilation of material attributes. Source: After Pleschiutschnigg et al. (2004).
A compilation of the mechanical attributes of several materials is shown in Figure 8.6, reproduced, following Pleschiutschnigg et al. (2004). The figure gives the elongation and the yield strength, measured at 0.2% offset, of deep-drawing steels, austenitic stainless steels, BH steels, TRIP steels, duplex stainless steels, DP steels and HSLA steels in addition to aluminium and magnesium. It is noted that the deep-drawing quality steels and the austenitic stainless steels offer the highest formability. BH and TRIP steels indicate similar elongation but the TRIP steels also provide much higher strength. Aluminium is less strong and less formable but much lighter than the ferrous metals. Its competitiveness needs to be based on its superior strength to weight ratio. Material Attributes 169
The processing route that results in the TRIP steels and the DP steels is also dis- cussed by Pleschiutschnigg et al. (2004). The rolling process is similar for both metals, the difference being the cooling rate: faster for the DP steels and slower for the TRIP steels. The authors indicate that the controlled rolling process, not the chemical composition, has a dominating influence on the results.
8.3 Steel and Aluminium
The competition between aluminium and steel alloys for use in the automotive industry is intense. The website of the US Steel Company gives some of the data, indicating the advantages of the steel grades over aluminium. The information below was taken directly from the website xnet3.uss.com/auto/index.htm, in April, 20062. A formability chart in the website compares the formability of several steels and aluminium. The winner as far as formability is concerned is the IF steel, indicating up to 55% total elongation. Its tensile strength is low, however, at most nearly 350 MPa. The strongest steel is the martensitic type, as expected, possessing a ten- sile strength of almost 1700 MPa but at a total elongation of about 7%, subsequent plastic forming processes need to be designed with extreme care. Aluminium appears to be somewhere in the middle, with elongation varying from a low of 7% up to 30 32% and a maximum tensile strength of 600 MPa. TRIP steels have a strength between 600 and 1250 MPa and elongations of 18 40%. A very interesting compilation of stress strain curves for several steel and alu- minium alloys is also given in the United States Steel (USS) website. Obtained at fairly low (0.0005 s21) and somewhat higher rates of strain (9.8 s21), the figure indicates that the steel alloys’ strengths increase with increasing rates of strain while those of the aluminium don’t. Specifically, the maximum strength of the TRIP 590Y steel, at 9.8 s21, is near 750 MPa and at the lower rate of 0.0005 s21 it is 620 MPa. In the same strain rate range, the strength of the DP steel increases by about 100 MPa as the rate of strain is increased and that of the deep- drawing quality steel increases by about 150 MPa. The 5754-0 aluminium alloy indicates no rate sensitivity. Note, however, that there are several aluminium alloys whose strengths are in fact, strain rate sensitive; an example is the commercial purity aluminium alloy, 1100-H0. Of major importance, also observable from the figure of USS, is the total strain sustained by each of the metals, as this has a major impact on the design of subse- quent forming processes and will hence affect productivity. The clear winner here is the deep-drawing quality steel, deformed at the low strain rate note that the 0.0005 s21 is almost creep deforming to a fracture strain of 45%. The fracture strain of the TRIP steel at high rates B36% is near that of the 5754-0 alumin- ium, strained at the lower rate. Most of the steels appear to be more formable than the single aluminium alloy.
2An attempt was made to reproduce some of the excellent figures from the US Steel website, identified above. Copying and pasting proved unsuccessful as the results became hazy when printed. 170 Primer on Flat Rolling
Further data, also from the US Steel website, compares the strengths and the cost indices of the two metals. A quotation discussing the information is repro- duced below:
The figure... shows common metallurgical grades undergoing a pre-strain of 2% and typical automotive paint bake cycle on the left compared to their prospective cost index shown on the right. Pricing for steel grades is based on seven combined typical market sources and the ULSAB-AVC cost model. Aluminum pricing was gathered based on 2002 publications from the MIT Material Systems Lab and typi- cal market information, such as the American Metal Market (2002 2003).
The cost index of the aluminium alloys is more than five times that of the steels. For example, the 6111-T4 alloys yield strength is given as approximately 240 MPa and its cost index is 5.9. This may be compared to that of the deep-drawing quality steel, DP 600. The yield strength of this alloy is the highest among those shown, at 580 MPa but its cost index is 1.1. The Society of Automotive Engineers (SAE) grade 3 steel is demonstrating a yield strength of 250 MPa and a cost index of one. Information regarding aluminium alloys is also easily available from the Internet. Alcan’s website indicates the formation of a spin-off company, Novelis Inc., formed in 2005 and now dealing with rolled products and sheet metal opera- tions. Novelis.com lists the benefits of aluminium over that of other materials; the list below is copied directly from the website.
The benefits of using lightweight aluminum sheet in transport applications are clear:
Aluminum offers high potential for weight savings, thus reducing emissions through the life of the vehicle, improving fuel efficiency and also handling; The metal is easily and widely recycled, saving energy and raw materials; It has very good deformation characteristics and manufacturing properties; Aluminum will absorb the same amount of crash energy as steel, at a little more than half the weight; It has good corrosion resistance. Novelis’ product range for the transportation market includes: sheet for auto- motive vehicle structures and body panels; pre-painted and plain sheet for com- mercial vehicle applications such as dump bodies, cabs and trailer flooring; “shate” for ship hulls and decks, tippers, road tankers, etc; plain, heat-treated or painted slit strips and coils customized to the needs of automotive part suppli- ers; high specification foil (industrial finstock) and brazing sheet for heat exchan- gers; and foil for insulation applications.
8.4 The Independent Variables
The traditional approach in identifying the variables and parameters that affect the behaviour of metals is quite simple and works well in many cases. The usual Material Attributes 171 formulations indicate that in the cold deformation regime the resistance to deforma- tion is assumed to be an exclusive function of the strain, that is σcold 5 f ðεÞ, and in the high-temperature region, at a particular temperature, the only independent vari- able is the rate of strain, or σhot 5 gðε_Þ. While both relations are used regularly in the analyses of metal forming processes, they represent a much too simplified view of how the metals behave. A list of independent variables that affect the material attributes is much longer. It may include the strain, strain rate, temperature and metallurgical parameters (e.g. the grain size, Zener Hollomon parameter, chemical composition, activation energy, precipitation potential, amount of recrystallization, volume fraction of vari- ous phases). Arguably, it may also include the dependence of the results on the testing technique as it is very rare to see a successful comparison of stress strain curves of a metal, obtained in tension, compression and torsion. Of course, an equation that includes all of these variables would never be used by engineers, so, as always, a compromise is needed. As will be demonstrated below, adequate results are obtained when the resistance to deformation is given in terms of the strain, rate of strain, temperature and the activation energy:
σ 5 f ðε; ε_; T; QÞð8:1Þ where Q is the activation energy, to be discussed in more detail later in this chap- ter, and T is the temperature, usually expressed in Kelvin. There are two steps involved in determining an actual, useful and usable form of Eq. (8.1). The first step requires a systematic testing programme designed with the end-use of the resulting data in mind3. The multi-dimensional databank thus obtained is then employed to develop an appropriate mathematical model which describes the metal’s resistance to deformation. In what follows, these two steps are discussed in some detail.
8.5 Traditional Testing Techniques
The objectives of the tests are several and depend strongly on the objectives of the tester. The materials engineer wants to know how the sample of the metal will react to loads. The engineer dealing with metal forming wants to know how to use the results of the test in analysing a metal forming process in addition to deciding what test to use to enable that analysis. The objectives of the materials chemist and phys- icist also would have an effect on the choice of the test. While there are numerous experiments available for the determination of the metal’s resistance to deformation
3These may include examining the behaviour of the material or the design and analysis of a metal form- ing process. 172 Primer on Flat Rolling for use in planning, designing and analysing metal forming processes, three of them are used most often. They are as follows:
G the tension test G the torsion test G the compression test G the axially symmetrical sample G the plane sample (width . thickness). In each of these, constant strain rates and constant temperature conditions need to be established so the only variables to be monitored remain the force and the deformation. As well, the strains are to be high enough to allow a direct compari- son of the metals’ behaviour in the tests with those required in the actual process.
8.5.1 Tension Tests These are the easiest and simplest to perform, using samples of cylindrical or rect- angular cross-sections. The advantages are as follows:
G there are no frictional problems to be considered and G the tests are governed by American Society for Testing and Materials (ASTM) codes (ASTM Standards, E 8 and E 8 M) so inter-laboratory variability is minimized. The disadvantages indicate that tension testing is not the most suitable when the information gathered is to be used to study metal forming processes. They are as follows:
G only low strains are possible, at most 40 50%; G the uniaxial nature of the stress distribution is lost when diffuse straining ends and local- ized straining begins, subjecting the necked down region to triaxial tension; G in order to keep the rate of strain constant, increasing the cross-head velocity during the test is necessary; and G while it is possible, it is difficult to perform the test in isothermal conditions. A schematic diagram of a tension testing set-up is shown in Figure 8.7, repro- duced from Schey (2000). A universal testing machine is shown, along with a flat sample, the actuator that moves the cross head, a load cell, an extensometer and a recording device which plots, online, the force-deformation curve. In an up-to-date, modern variant of this set-up, the measurements would be collected using digital data acquisition and a stress strain curve would then be plotted in real time. Attention needs to be paid to the manner in which the sample is attached to the cross head. As shown in the figure, there are holes drilled in the sample and the attachment ensures the application of the force in the direction of its longitudinal centreline. At the same time, the effect of the stress concentration at the holes is to be considered carefully and the sample should be designed such that fracture doesn’t occur there. In many commercially available tensile testers, jaws attached to the machine through spherical seats are used to hold the sample and these also ensure appropriate alignment while minimizing the problems that may be caused by stress concentration. Material Attributes 173
Actuator
Displacement transducer
Extensometer
Moving P crosshead x–y recorder y
Test specimen x x y
P Voltage Voltage ∝Δl ∝P
Load cell
Figure 8.7 A tension test. Source: Schey (2000), reproduced with permission.
The comment made above, concerning the difficulties associated with providing isothermal conditions, may be appreciated by examining the figure. There are sev- eral possibilities, none easy. An openable, split furnace may be used which would enclose most of the sample and the extensometer. This would necessitate the use of very expensive extensometers that are capable of performing within the high- temperature furnace. A modern variation would make use of an optical device, focused on a deforming section of the sample, through a viewing hole of the fur- nace wall. In either case, the jaws would also need to withstand the high tempera- tures. The load cell and the rest of the testing machine would have to be protected from temperature damage, probably by installing in-line heat exchangers. Another possibility to heat the sample is the use of induction heaters and a coil which would cover only the reduced, deforming portion of the sample; however, induction hea- ters are bulky and very expensive.
8.5.2 Compression Testing These may be performed on cylindrical or plane samples; for details, see ASTM Standards E 9. Figure 8.8, again reproduced from Schey (2000), shows a schematic of the compression test, using a cylindrical sample, (A) and the force-deformation curve that results, (B). Note that the curve is increasing exponentially, reflecting 174 Primer on Flat Rolling
P A 0 A 400 1
300 0 h Displacement
1 transducer h (Δh) 200 , kN P Load 100 cell (P)
0 24681012 Δh h h (= 0 – 1), mm (A)P (B)
Figure 8.8 (A) The compression test (B) and the resulting force-deformation curve. Source: Schey (2000), reproduced with permission. the growing contact area and the attendant increase of frictional resistance. The advantages of the compression tests are as follows:
G Larger strains are possible, typically 120 140% when cylinders are compressed and up to 200% when plane samples are tested. G The state of stress is mostly compressive, as in bulk forming. The disadvantages are as follows:
G Frictional forces at the ram-sample interface grow as the test progresses and their effects must be controlled and removed from the data. G Tensile straining at the cylindrical surfaces or the edges of plane samples limits the level of straining (the circumferential strain may be calculated easily, making use of mass conservation). G The achievement of constant true strain rates during the tests requires careful feedback control, making the use of a cam-plastometer or in a modern setting, a computer- controlled servohydraulic testing system. G The distribution of the strains in the normal direction is not uniform. G When plane-strain compression is performed, isothermal conditions are difficult to achieve. It is relatively simple to conduct a compression test at high temperatures and to make sure that almost isothermal conditions exist within the furnace. An openable furnace is necessary with a fairly long heated length. The sample is to be com- pressed between flat platens, made of a material that retains its strength at the test temperature. For steels the platens are often made of silicon carbide. Various Inconel alloys may also be used. As well, it is important to place water-cooled heat exchangers between the compression platens and the rest of the testing system, that is the load cell and the actuator. The procedure followed is also of importance as is the location of the thermocouple, or the temperature measuring system that controls the furnace temperature. Material Attributes 175
Figure 8.9 The plane-strain compression test. Source: Schey (2000), reproduced with permission.
In the plane-strain compression test, shown schematically in Figure 8.9, a flat sample is compressed between two flat dies. As long as the shape factor in the plane-strain test is similar to the shape factor in a flat rolling process, the strain dis- tributions in the deforming portions within the two processes are similar (Pietrzyk et al., 1993). This allows one to recommend that in order to develop a mathemati- cal model of the resistance to deformation for use in a one-dimensional model of flat rolling, the plane-strain compression tests should be used. An experimental difficulty in developing isothermal data in the plane-strain compression test is immediately evident. Enclosing the complete apparatus in a fur- nace is not practical. Heating the sample only is possible but not easy since the uni- formity of the temperature distribution is difficult to maintain. Resistance heating, as performed in the Gleeble machines, or induction heating may be best, though in the latter, placing the coils may cause further difficulties.
8.5.3 Torsion Testing This type of testing materials is the most suitable when the data are to be used to analyse large-strain processes, such as a slab would experience during its journey through a hot strip mill, while it is being reduced from a thickness of about 300 mm to a final thickness of about 1 2 mm. Finite strains of 400 500% can be obtained easily, allowing the simulation of the complete history of hot rolling, including the phenomena at the roughing mill and the finishing train of hot strip mills. The advantages are as follows:
G very large strains are possible; G constant rate of strain is simple to achieve; and G no frictional problems exist. 176 Primer on Flat Rolling
The disadvantages are that
G the torsional stresses and strains vary over the cross-section and a considerable amount of analysis is necessary to extract the uniaxial normal stress strain data; and G the variation in the time it takes for different locations of the cross-section to experience metallurgical phenomena, specifically dynamic recovery and recrystallization, may cause a non-homogeneous structure. It is essential to allow the length of the sample to change without restrictions as the torsional testing proceeds, as constraining the length would induce longitudinal stresses in addition to the shearing stresses.
8.6 Potential Problems Encountered During the Testing Process
The usual approach to determine the metal’s resistance to deformation in order to simulate the hot or the cold rolling processes is to conduct compression tests, using plane or axially symmetrical samples4. While the test procedures are well under- stood and many of them are controlled by well-known standards, two areas of potential difficulties still exist: that of friction and that of temperature control. In what follows, these difficulties are discussed.
8.6.1 Friction Control This problem is encountered in the compression testing process, whether using axi- ally symmetrical or plane samples. As the samples are being flattened, the contact area grows and continuously increasing effort must be devoted to overcome the frictional resistance at the compression platens. Baragar and Crawley (1984) showed that frictional effects are not very pronounced when strains under approxi- mately 0.7 are considered. Above that level of deformation, however, the increas- ing frictional effects must be removed from the force-deformation data in order to obtain uniaxial behaviour. When using cylindrical samples, this may be accom- plished by adopting the relation: m d p 5 σf 1 1 pffiffiffi ð8:2Þ 3 3 h
where the uniaxial flow strength is σf,pis the interfacial normal pressure, m is the friction factor and d and h are the current diameter and height of the sample,
4This statement may cause an argument among material scientists, many of whom value the advantages provided by the torsion test more than the simplicity of the compression tests. Material Attributes 177
200 Figure 8.10 True stress true strain curves of ε (1/s) aNb V steel, at 950 C, under three different 1 conditions (Wang, 1989). 160 2
120 3 (MPa) σ 80 1. Specimen with flat ends 2. Specimen with recessed ends 40 3. Correction of curve-1 for friction (m = 0.18)
Nb–V steel, 950ºC, ε = 0.051/s 0 0.0 0.4 0.8 1.2 1.6 ε respectively. The friction factor is best determined in the ring compression test5 (Male and DePierre, 1970). Avitzur (1968) quotes Kudo’s (1960) formula, connect- ing the coefficientpffiffiffi of Coulomb friction and the friction factor in the form μðpave=σf Þ 5 m= 3. In room-temperature testing it is possible to minimize fric- tional problems by using a double layer of Teflon tape over the flat ends of the sample. In high-temperature tests a glass powder alcohol emulsion may be employed. Removing the effects of friction while the data obtained from plane-strain com- pression testing are analysed is equally important. In what follows, an example of the use of the above formula, Eq. (8.2), is pre- sented, considering the compression test performed on a Nb V microalloyed steel. Samples of the steel, measuring 10 mm in diameter and 15 mm long, were com- pressed under nearly isothermal conditions, at a constant true strain rate of 0.05 s21. The temperature of the sample was 950 C. Three tests were conducted, the results of which are shown in Figure 8.10 (Wang, 1989). In all three tests, glass powder in an alcohol emulsion (Deltaglaze 19) was used as the lubricant. The first experiment used a sample prepared with its ends machined flat and beyond a true strain of 0.8 the resulting stress strain curve indicated a steep rise which, if no ele- vated temperatures were employed, may be confused with strain hardening. In the second test, the well-known Rastegaev (1940) technique was followed, indenting the ends of the sample to a depth of 0.1 mm and leaving a ridge of about the same dimension. The objective was to trap the lubricant at the ram/sample interface. The resulting curve still indicated some rise. (It is noted that researchers often employ very shallow, concentric or spiral grooves on the flat ends to achieve the same objectives. The present writer’s experience indicates that multiple grooves are
5The ring compression test will discussed in detail in Chapter 9, Tribology. 178 Primer on Flat Rolling more difficult to machine without offering any significantly increased benefits over recessed ends in the reduction of friction.) In the third attempt, the value of the fric- tion factor was determined, under the same conditions in a ring-test, to be 0.18. The uniaxial flow strength was calculated by Eq. (8.2) and is shown in Figure 8.10, identified as curve #3. The curve demonstrates the steady-state behaviour expected of the steel at the test temperature and strain rate.
8.6.2 Temperature Control The need to control the temperature during the tests for strength is equally important at both low and high temperatures. While it is essential to do so, it is almost impossible to conduct a test for the stress strain curve under true isothermal conditions. It is equally difficult to measure the temperature of the sample accurately during the experiment. Overcoming the first difficulty is most important when the tests to determine the material’s resistance to deformation are conducted. The second problem is of significance when the test results are reported and mathematical models for use in subsequent analyses are to be developed6.
8.6.2.1 Isothermal Conditions The usual procedure in conducting a test is to preheat the furnace and the compres- sion rams to the desired temperature. This is followed by opening the furnace door, placing the sample on the bottom ram for a sufficient length of time to reach a steady state, bringing the top ram in contact with the sample and starting the compression process. The rams are usually of a larger diameter than the compression sample and are of significantly larger thermal mass. They are connected to the load cell and the actuator by water-cooled heat exchangers, and their lengths are considerable, even if the heated length of the furnace is not very long. Because of the heat exchangers, the rams’ temperature is not uniform along their lengths and typically they are lower than that of the furnace. The furnace temperature is usually monitored by a thermo- couple whose bead is a few millimetres away from the inner surface of the furnace’s insulation. The control of the furnace temperature is achieved by monitoring the out- put of this thermocouple. The average temperature within the furnace is quite cer- tainly lower than the indicated value. When the furnace is opened to allow the placing of the sample on the ram, considerable cooling takes place. While time consuming, expensive and labour intensive, thermocouples should always be embedded in the sample and in the loading rams. The thermocouple on the sample should be used to control the temperature of the furnace. The test is to commence when the sample and the ram temperatures are very close, within a pre-determined tolerance. (A modern alternative, of course, is the use of optical pyrometers through spy-holes in the furnace walls, instead of thermocouples).
6When reporting the results of the tests, many writers are guilty of not describing the equipment and the procedure in minute detail. Both of these are necessary if the tests are to be duplicated. Material Attributes 179
240 Figure 8.11 The temperature dependence of the peak stress of several steels. 200 Source: Lenard et al. (1999), reproduced with permission.
160
120
Peak stress (MPa) 0.120% Ti, 0.07% C 0.035% Ti, 0.06% C 80 0.028% Nb, 0.13% C AISI 5140 0.05% Nb, 0.12% C 40 600 800 1000 1200 Temperature (ºC)
The thermocouple in the sample will also indicate the temperature rise due to work done on it. In reporting the results this rise should be accounted for. Realizing that the work done per unit volume is almost exactly equal to the area under the true stress true strain curve, the temperature rise may be estimated by: Ð σ dε ΔT 5 ð8:3Þ cpρ where the specific heat is designated by cp and the density by ρ, both of which are tem- perature dependent; see Touloukian and Buyco (1970). Corrections to develop the flow curve under isothermal conditions require the determination of the temperature as the sample is being compressed and inter- and extrapolation to compute the appro- priate values of the stresses. In these calculations it is assumed that all work done is converted into heat, an assumption which is close enough though not quite correct.
8.6.2.2 Monitoring the Temperature The potential accuracy of the temperature measurements should be considered, as well. Manufacturers’ catalogues list the accuracy of a type K (chromel alumel) thermocouple as 60.5%, full scale7. If testing at 1000 C is considered, this indi- cates a potential error of 10 C. The effect of this error in the magnitude of the tem- perature needs to be understood in light of the temperature sensitivity of the resistance to deformation of steels. This varies over a large range, as shown in Figure 8.11 which indicates the dependence of the peak stresses of several steels on the temperature.
7Platinum rhodium thermocouples, type R, could be used, of course, and these are considerably more accurate (B0.1%) than the type K version. They are much more expensive, however. 180 Primer on Flat Rolling
In the worst-case scenario, consider the microalloyed steel, containing 0.028% Nb and 0.13% C. The graph shows a slope of 0.9 MPa/ C and the 10 C difference would then indicate an error in the strength of 9 MPa. As the steel’s strength at that temperature is about 130 MPa, the very small error in temperature measurements creates a very much more significant error of about 7% in the strength data. The implications of this 7% are evident when considering the sensitivity of the predicted roll separating forces and roll torques to variations of the material’s strengths. Several high-temperature furnaces are available with a spy-hole, allowing the use of optical pyrometers which, when focused on the sample, would monitor its temperature as the test is proceeding. This approach is preferred over the use of thermocouples which require a hole to be drilled into the sample to house the ther- mocouple. While the stress concentration around the hole and the embedded ther- mocouple is not expected to affect the material’s resistance to deformation in any significant manner, it is nevertheless an interruption and can be avoided by the use of optical devices. Further problems with the embedded thermocouples include the different strength of the bead and the sample in addition to the possible imperfect contact of the bead and the bottom of the hole. The latter may be eased somewhat, but not eliminated completely, by the use of high conductivity cement.
8.7 The Shape of Stress Strain Curves
The stress strain curves of metals differ greatly, depending on the temperature at which the test is performed. The two cases, low- and high-temperature behaviour, are treated below.
8.7.1 Low Temperatures Stress strain curves of an AISI 1008 steel, obtained in uniaxial tension and at room temperature, are given in Figure 8.12. Two curves are shown. In the first, the steel was tested as received. In the second, the results of cold working are evident, indicating that the steel’s strength increased by approximately 40% as a result of one cold-rolling pass in a two-high rolling mill, causing 58.5% reduction. Both curves indicate strain hardening. The steel is not highly ductile. Even in the annealed condition, the fracture occurred at a strain of 0.18. The stress strain curve following the 58.5% cold reduction exhibits the yield point extension.
8.7.2 High Temperatures The shape of a stress strain curve, obtained in a test, conducted at high tempera- tures, differs significantly from that at low temperatures, showing the effects of metallurgical phenomena on the resistance of the material to deformation. The dif- ference is illustrated in Figure 8.13, which shows the true stress true strain curves Material Attributes 181
400 Figure 8.12 The stress strain curves of an AISI 1008 steel.
300
200 AISI 1008 steel, annealed
As received Tensile stress (MPa) 100 58.5% reduction, single-stage
0 0.00 0.04 0.08 0.12 0.16 0.20 Strain obtained in compression testing of a 0.1% C, 0.0877% Nb, 0.0795% V steel. During the compression test, a glass-alcohol emulsion was used to cover the ends of the samples to minimize interfacial friction. While the curves have not been cor- rected for temperature rise, this omission is not expected to cause significant errors, since the rates of strain were not excessive. The curves demonstrate the traditionally expected behaviour of steels at high temperatures. Two metallurgical mechanisms, affecting the shape of the curves, are to be considered: these are the hardening and the restoration processes. The latter includes dynamic recovery and dynamic recrystallization. Since all samples were annealed prior to the tests, it may be safely assumed that the steels were initially fully recrystallized and that the austenite grains were uniform in size and were equiaxed8. As soon as the compression process begins, hardening due to the pan- caking of the grains begins and at a fairly small strain, say 3 5%, dynamic recov- ery also starts. A micrograph taken at that strain would indicate the flattened grains. The migration of the dislocations may also be observed but no changes to the grains, other than some flattening, are expected due to dynamic recovery. The loading is now continued and the hardening and the softening processes occur simultaneously. When the rate of softening exceeds that of hardening, the slope of the stress strain curve begins to decrease. At a particular strain, identified as the critical strain, usually denoted by εc, another restoration process, that of dynamic recrystallization, is initiated and the slope of the stress strain curve drops even more. A micrograph, taken just beyond the critical strain, would show the new, strain-free grains nucleating, usually at the grain boundaries. The process is still
8A perfectly equiaxed figure is the circle with its diameter constant. An equiaxed grain is usually hexag- onal; see, for example, Figure 8.1. 182 Primer on Flat Rolling
(A) 250 Figure 8.13 True ε (s–1) stress true strain curves of 2 a high Nb V steel, obtained 200 1 under nearly isothermal conditions and at strain rates 0.1 of 0.001 2s21. 150
0.01
100 0.001 True stress (MPa)
50 T = 900°C
0 0.00 0.40 0.80 1.20 True strain (B) 250
ε –1 200 (s ) 2 1 150 0.1 (MPa)
σ 0.01 100 0.001
50 T = 950°C
0 0.00 0.40 0.80 1.20 ε continuing and now all three metallurgical events are active at the same time. Further straining reaches the condition when the rate of hardening just equals the rate of softening and a plateau in the stress strain curve is reached, identified as the peak strain, εp. The stress at that location is referred to as the peak stress and is usually designated by σp. Further loading causes the softening rate to exceed the hardening rate and the material’s resistance to deformation falls until a steady state, at a strain identified as εss, is reached. Beyond that strain the stress strain curve becomes independent of the strain but is dependent on the strain rate and the temperature. Material Attributes 183
Grains elongate Figure 8.14 A schematic Dislocation density increases diagram of a stress strain Subgrains are created curve at high temperatures. Initial grains disappear Source Dynamically recrystallized grains are equaxial : Reproduced from εp Lenard et al. (1999), with permission; some changes Steady-state flow were introduced.
εc Stress ε ss ε = constant T = constant
Strain
Figure 8.15 The progress of dynamic recrystallization in a 0.1% C, 0.04% Nb steel. (A) shows the structure before deformation; (B) shows no recrystallization; (C) shows partial recrystallization; and (D) shows complete recrystallization (Cuddy, 1981).
A schematic diagram of a true stress true strain curve, obtained at high tem- peratures, is shown in Figure 8.14 (reproduced from Lenard et al., 1999, with some changes), with all three strains, εc, εp and εss indicated. Another set of micrographs (Figure 8.15A D) indicates the progress of dynamic recrystallization in a 0.1% C, 0.04% Nb steel (Cuddy, 1981). In Figure 8.15A, the structure before testing is shown. The austenite grains are large, measuring 370 μm on average. The structure, after straining to 0.4 at a temperature of 900 Cata 184 Primer on Flat Rolling strain rate of 0.017 s21, is shown in Figure 8.15B. The recrystallization process has not started yet. Deformation to a strain of 0.43 at a higher temperature of 1000 C and a strain rate of 0.05 s21 caused partial dynamic recrystallization (Figure 8.15C). The recrystallization process was completed when the sample was subjected to a strain of 0.55 at 1100 C and at a strain rate of 0.17 s21 (Figure 8.15D).
8.8 Mathematical Representation of Stress Strain Data
At this stage of the study, the necessary data on the metal’s resistance to deformation the stress, strain, rate of strain, temperature and hence, the Zener Hollomon parameter, defined as Z 5 ε_ expðQd=RTÞ are in hand. In the expression Qd repre- sents the activation energy for plastic deformation, R is the universal gas constant, 8.314 J/m/K and T is the temperature in Kelvin. The next step is to develop a mathematical model for further use in analysing a metal forming process. The traditional approach is to make use of non-linear regression analysis and then fit the experimental data, as best as possible, to a pre-determined relation. Another possi- bility is to place the experimental data in a multi-dimensional databank and when the stress values are needed in an application, inter- or extrapolate for them, at the actual strain, rate of strain and temperature. Two fairly recently developed possibilities to determine the material attributes have been developed, but so far they have not been employed extensively. One of them uses artificial intelligence, specifically neural networks, to estimate and pre- dict the metals’ behaviour. The other, parameter identification, is based on a com- bination of a finite-element simulation of a test in the present instance, that would be a rolling pass with the measurements of the overall parameters, such as the roll separating force or the roll torque (Gelin and Ghouati, 1994; Kusiak et al., 1995; Malinowski et al., 1995; Khoddam et al., 1996; Gavrus et al., 1995). The measurements of the process parameters are then compared with the predic- tions by the finite-element method. An error norm is defined as the vector of dis- tances between the measured and calculated values. The minimization of the error norm is used to determine the unknown parameters in the constitutive law. In the statistical method an equation is always obtained which can be used with more or less ease in the subsequent steps of the analysis. There are two difficulties. The first problem concerns the just-developed “best-fit curve” which may not fit all data points equally well, and therefore some carry-on errors are unavoidable. The second problem is encountered when additional material data are developed. The non-linear regression analysis needs then to be repeated and a new relation that fits the new data as well as before must be obtained. The latter deficiency, that of repeating the statistical re-development of the empirical relation, is overcome by the ability of the neural networks to renew them- selves. The disadvantage, often claimed by engineers, is that an equation is not obtained. Material Attributes 185
8.8.1 Material Models: Stress Strain Relations There is an infinite number of possibilities in formulating the constitutive relations, both at high and low temperatures. These equations are just that: they are chosen in an arbitrary manner to describe the metals’ observed behaviour. The choice of the form and the independent variables are up to the researcher. Some of the better known and accepted forms are given below.
8.8.1.1 Relations for Cold Rolling While the choice of the form for stress strain relations is practically infinite, two equations have been used regularly by researchers. Both relate the metal’s strength to strain only in addition to material constants which may depend on the rate of strain. The first is σ 5 Kεn, where the constants, K and n can be determined for any particular stress strain data, either by a least-squares minimization routine or by forcing the curve through two pairs of stress and strain values. Both approaches are acceptable. The other relation, more suitable for the analysis of metal forming and particularly for the rolling process, also relates the metal’s strength to the strain in the form σ 5 Yð11BεÞn, where the three material constants need to be determined by fitting to experimental data. This expression indicates that the metal possesses some strength at zero strain. In addition to the strain, the strengths of some metals (e.g. titanium) are also dependent on the rate of strain. A relationship that has been found useful in such cases is σ 5 Yð11BεÞnε_m, where the exponent m is the strain rate hardening coeffi- cient. Again, non-linear regression is needed to determine the coefficients and the exponents.
8.8.1.2 Relations for Use in Hot Rolling Statistical methods One of the simplest expressions, often used in the analysis of hot rolling problems, relates the metal’s strength to the average rate of strain and two material constants, in the form σ 5 Cε_m; values for the constants have been given by Altan and Boulger (1973) for a selection of ferrous and non-ferrous metals. An often-quoted source for stress strain strain rate relations is the compilation of experimental data, Suzuki et al. (1968). Stress strain curves for a large number of ferrous and non-ferrous metals have been given, at various temperatures and rates of strain. The chemical compositions of the metals have also been provided. Several somewhat more complex equations were listed by Lenard et al. (1999), some of which are repeated below. One of these, based on the hyperbolic sine func- tion, is due to Hatta et al. (1985). The hyperbolic sine law gives the strain rate in the form: Q ε_ 5 c sinh ðασÞn exp 2 ð8:4Þ RT 186 Primer on Flat Rolling
Hatta et al. (1985) define the various terms in Eq. (8.4), for a 0.16% C steel, as
c 5 exp ½24:4 2 1:69 ln C ðs21Þð8:5Þ
n 5 exp ½1:63 2 0:0375 ln C ð8:6Þ
α 5 exp ½2 4:822 1 0:0616 ln C ðin MPa21Þð8:7Þ and
Q 5 exp ½5:566 2 0:0502 ln C ðin kJ=moleÞð8:8Þ
While Hatta et al. (1985) determined the activation energy by non-linear regression analysis, a somewhat more fundamental approach, making use of experimental data, is likely to lead to more physically realistic values. The recommendations are to follow these steps:
G Re-write Eq. (8.4) in a different form: ε_ 5 Aσn expð2 ðQ=RTÞÞ; G perform a number of stress strain tests at several temperatures and rates of strain; G obtain the peak stresses and prepare a log log plot of the peak stresses versus the temperatures; G at an arbitrary stress level, obtain from the plot two temperatures and the corresponding rates of strain; and G determine the activation energy from the slope Q Δðlnðε_Þ=Δð21=RTÞ. The activation energy, thus determined for a 0.1% C, 1.093% Mn, 0.088% Nb, 0.0795% V steel, was 483 kJ/mole (Lenard et al., 1999). In general, higher alloy content leads to larger values of the activation energy. It is noted that the strain doesn’t appear in Hatta’s relations, indicating that they are strictly applicable in the steady-state region. Wang and Lenard (1991) included the strain in the exponents of Eq. (8.4) while developing a high-temperature model for the deformation of a Nb V steel. Another set of empirical relations have been presented by Shida (1969), giving the metal’s resistance to deformation as a function of the temperature, carbon con- tent, strain and strain rate. These equations have been used successfully in a num- ber of publications, concerned with hot rolling or hot forging of steels. The relations have been developed by Shida for carbon steels. It is expected that use of carbon equivalent instead of the carbon content may allow Shida’s formulae to be used for alloy steels, as well. The carbon equivalent may be calculated as a func- tion of the alloy content of the steel from the relation9:
Ceq 5 C 1 Mn=6 1 ðCu 1 NiÞ=15 1 ðCr 1 Mo 1 VÞ=5 ð8:9Þ
9There are several formulae available for “carbon equivalent”, mostly developed for the study and modelling of welding processes. Material Attributes 187
The flow strength of the steel, in kg/mm2, is given by Shida, in terms of the carbon content in %C, the rate of strain and the temperature: ε_ m σ 5 σ f ð8:10Þ f 10
The terms in Eq. (8.10) are defined, depending on the temperature of deformation. For
C 1 0:41 T $ 0:95 ð8:11Þ C 1 0:32 5 0:01 σ 5 0:28 exp 2 ð8:12Þ f T C 1 0:05 and
m 5 ð20:019C 1 0:126ÞT 1 ð0:075C 2 0:05Þð8:13Þ
For temperatures below that defined by Eq. (8.11), C 1 0:32 0:01 σ 5 0:28 qðC; TÞ exp 2 ð8:14Þ f 0:19 ðC 1 0:41Þ C 1 0:05
C10:49 2 C 1 0:06 qðC; TÞ 5 30ðC 1 0:9Þ T20:95 1 ð8:15Þ C10:42 C 1 0:09 and
0:027 m 5 ð0:081C 2 0:154ÞT 2 0:019C 1 0:207 1 ð8:16Þ C 1 0:32
The remaining parameters are
f 5 1:3ð5εÞn 2 1:5ε
n 5 0:41 2 0:07C and
T 5 ðT 1 273Þ=1000 188 Primer on Flat Rolling
320 Figure 8.16 A comparison of the Altan and Boulger predictions of several empirical relations, 280 Suzuki et al. designed for high-temperature behaviour. Shida 240 Hatta 800°C 200
160
120 Stress (MPa)
80 1200°C
40
0 0 4 8 12 16 Strain rate (s–1)
In the above relations, T is the temperature in C and C is the carbon content in weight %. The true strain is denoted by ε. Shida gives the limits of applicability of his empirical relations10 as C , 1.2%; T in between 700 C and 1200 C; ε_ in between 0.1 and 100 s21 and ε , 70%. While these equations have been used successfully in many instances, some cau- tion is needed in specific applications. The difficulties are illustrated in Figure 8.16 where the predictions of four previously published equations or measurements are compared, by plotting the predicted strength as a function of the rate of strain, at a temperature of 800 C (close to the transformation temperature) and 1200 C, where the steel is fully in the austenitic state. A carbon steel is chosen for the comparison. The curve denoted by the crosses is due to Altan and Boulger (1973). The equa- tions for a steel, containing 0.15% C, are, at a temperature of 800 C, σ 5 145:38ε_0:109 MPa and at a temperature of 1200 C, σ 5 39:27ε_0:181 MPa. The steel, closest to this and whose stress strain curves are given by Suzuki et al. (1968), contains 0.147% C. Non-linear regression analysis gave the equations of the curves, plotted in Figure 8.16 (denoted by the diamonds), at 800 C, σ 5 182:34ε0:1039 MPa and at 1200 C, σ 5 59:06ε0:1698 MPa. The parameters of the equation due Hatta et al. (1985) are given above; see Eqs. (8.4) (8.8). This curve is given by the upward triangles. Finally, the curve obtained using Shida’s relations for a steel containing 0.15% C is denoted by the squares. It is observed that all four curves give the expected trends. The differences of the predictions are quite large, though, reaching up to 35%.
10In several cases of empirical relations, developed to represent the metal’s resistance to deformation, the limits of applicability are not given a major omission. Material Attributes 189
50 Figure 8.17 The predictions of the flow strength of a commercially pure –1 Temperature ε = 7.58 s aluminium alloy (Chun et al., 1999). 40 400°C
30 450°C
500°C
20 Training Testing True stress (MPa)
10 Neural network Experiment
0 0.00 0.20 0.40 0.60 0.80 1.00 True strain
Developing a databank of data Use of a multi-dimensional databank was explored by Lenard et al. (1987). Stress values at particular strain, strain rate and temperature were stored and retrieved as needed in the analysis of the flat rolling process. The results compared favourably with data obtained by other approaches. While it is believed that using a large data- bank removes the need to develop arbitrary empirical relations and that it would remove one error-prone step from the analysis of the rolling process, no extensive use of the approach is evident in the technical literature.
Artificial neural networks The predictive capabilities of the method are demonstrated by considering the hot compression testing of an aluminium alloy (Chun et al., 1999). Cylindrical samples of the Al 1100-H14 alloy of 20 mm diameter and 30 mm height have been used to determine the metal’s resistance to deformation. The specimens have been machined from plates with the longitudinal direction parallel to the rolling direc- tion. The flat ends of each specimen were machined to a depth of 0.1B0.2 mm to retain the lubricant, boron nitride. A type K thermocouple in an INCONEL shield, with outside diameter of 1.54 and 0.26 mm thermocouple wires, was embedded centrally in each specimen. The compression tests were carried out on a servohy- draulic testing system, at a true constant strain rate of 7.58 s21 and at sample tem- peratures of 400 C, 450 C and 500 C. The results are shown in Figure 8.17. The network was trained using the data at the temperatures of 400 C and 500 C. Testing the network was performed by comparing the predictions to measurements obtained at 450 C. The good predictive ability of the network is evident.
Parameter identification The parameter identification method has been developed in the last decade and applied to problems of metal forming (Gavrus et al., 1995; Boyer and Massoni, 190 Primer on Flat Rolling
Figure 8.18 The stress strain 350°C 150 curves of an aluminium alloy, measured and compared to the calculations by the parameter 100 425°C identification technique (Lenard et al., 1999). 500°C
Stress (MPa) 50 Width of the platen 5 mm Experiment Thickness of the sample 10 mm Calculations Strain rate 1 s–1 0 0.0 0.2 0.4 0.6 0.8 1.0 Strain
2001; Gelin and Ghouati, 1999; Gelin and Ghouati, 1994; Kusiak et al., 1995). The details of the technique have been reviewed by Lenard et al. (1999). Pietrzyk (2001) used the technique to determine and predict the high-temperature behav- iour of a low-carbon steel and a 304 stainless steel; the predictions and the measurements compared very well. The ability of the method to predict the hot stress strain curves of a harder aluminium alloy, when subjectedtoplane-strain compression, is evident in Figure 8.18 (Lenard et al., 1999). A description of the experimental procedure and theresultsoftheanalysisweregivenbyPietrzykand Tibbals (1995). The experiments have been carried out at temperatures of 350 C, 420 C and 500 C and at a strain rate of 1 s21. The initial thickness of the alumin- ium alloy samples was 10 mm. The width of the platens and of the sample was 15 mm.
8.9 Choosing a Stress Strain Relation for Use in Modelling the Rolling Process
It is clear at this point that to satisfy the demands of its users the success of a math- ematical model of the flat rolling process depends on how well the tribological and material attributes are treated. Tribology is to be discussed in the next chapter. The choice of a stress strain equation will also contribute to success or failure and extreme caution is advised when that choice is made. While the researchers have several possible avenues to follow, one of the approaches, given below, will likely be chosen: 1. Conduct independent testing to determine the metal’s mechanical attributes and use non- linear regression analysis to develop a model for later use. 2. Search the existing technical literature for information on the attributes. It is strongly advised, however, that if at all possible, the first approach in the list should be followed. The reasons are clearly demonstrated in Figure 8.16. Material Attributes 191
8.10 Summary
The metals’ resistance to deformation was discussed in the chapter. First, the recently developed steels were presented and their micrographs were demonstrated. This was followed by a presentation of the perennial battle for supremacy between the steels and aluminium alloys. The most prevalent, traditional techniques avail- able to test the metal’s response to loading were given, including tension, compres- sion and the torsion tests. Their advantages and disadvantages were listed. Approaches towards the treatment of constitutive data were presented. The mathe- matical models, arrived at by statistical techniques, parameter identification and artificial intelligence methods, designed to describe the behaviour of the materials, were also included. A simple approach to determine the activation energy was mentioned. Recommendations concerning the determination of the metal’s resis- tance to deformation were given. 9 Tribology
9.1 Tribology A General Discussion
It is appropriate here to start with a quotation from Roberts (1997). He writes,
Of all the variables associated with rolling, none is more important than friction in the roll bite. Friction in rolling, as in many other mechanical processes can be a best friend or a mortal enemy, and its control within an optimum range for each process is essential.
While Roberts wrote about friction, it is further appropriate and even necessary to replace that term with “tribology”. The study of surfaces in relative motion, in contact and under pressure that of tribology is a very broad subject. It has been studied by scientists and applied by engineers for thousands of years. The points of view of its practitioners are equally wide, encompassing the disciplines of tribochemistry, tribophysics, chemistry, chemical engineering, nanotribology, surface analysis, surface engineering, fluid mechanics, heat transfer, mathematics and mechanical engineering and the list is far from complete. Attending a large, comprehensive conference, entitled “Tribology”, requires careful choice of the lectures to be attended and may easily lead to information overload. In the present context, that is, flat rolling of metals, the focus is on three interconnected phenomena: friction, lubrication and heat transfer at the contact surfaces. These, in turn, create roll wear, and in the metal rolling industry the costs associated with wear problems account for nearly 10% of total production costs. The cost of inappropriate understanding or application of tribological princi- ples has been estimated to be as high as 6% of the GDP in the United States (Rabinowicz, 1982). Interesting data have been given in a recently published book by Stachowiak and Batchelor (2005) concerning the same topic. They quote the Jost report (1966) which estimated that the correct application of the basic principles of tribology would save the UK economy d515 million per annum. A report by Dake et al. (1986) indicated that in the United States about 11% of the total annual energy could be saved in the areas of transportation, turbo machinery, power generation and industrial processes.
Primer on Flat Rolling. DOI: http://dx.doi.org/10.1016/B978-0-08-099418-5.00009-3 © 2014 Elsevier Ltd. All rights reserved. 194 Primer on Flat Rolling
A recent search on the Internet, using the word “Tribology”, yielded 237,000 results1. It is, of course, not realistic to check and evaluate all of these. One that appeared of potential interest was the Virtual Tribology Institute, a group of European organizations that deal with all aspects of the subject. Members are located in several European countries while the manager of the Institute is located in Belgium. Also found by the search is the Center for Tribology, identifying itself as the largest tribology testing laboratory in the world, located in Campbell, CA. Under “useful links” the site gives a list of universities where research on tribology is performed. Unfortunately, however, when checking the title “Northern American Universities”, schools in the United States only are mentioned, while Mexican and Canadian places are omitted. Probably and arguably the most complete website is the one provided by the University of Sheffield, checked in early 2007. The four sub-topics listed on the site are Research, Teaching, Tools and Information and Consultancy. Clicking on Tools and Information, a plethora of very useful items is found. The list of books dealing with the topic of tribology is likely the most complete available. The list of journals, periodicals and online resources are also most impressive. The list of “Tribologists Around the World” is very useful when one wants to know who is dealing with what in the field. It is evident that while the interactions of the components, parameters and variables of the field of tribology are beyond the capabilities of a single discipline, listing them is still valuable. For the most complete listing of the attributes of an interface, in addition to their interactions, the reader is referred to the table shown in Fig. 3.2 of “Tribology in Metalworking” by Schey (1983). The table was first presented at a conference in 1980, but to the best of the present writer’s knowledge, no better or more complete compilation has been given since. The three components of a metal working system are identified as the die, the work piece and the interface between the two, which includes the lubricant. The table is reproduced as Figure 9.1 and an examination of the interconnection of the parameters indicates the complexities of the process. As mentioned above, the phenomena of friction, lubrication and heat transfer will be discussed in turn in what follows, followed by a brief look at their combined effect: roll wear.
9.2 Friction
9.2.1 Real Surfaces An enlarged view of the cross-section of two surfaces is presented by Schey (1983) and the figure is reproduced here as Figure 9.2, clearly demonstrating the validity of the comment written by Batchelor and Stachowiak (1995), stating that surfaces
1The search was done in 2006. Tribology 195
Die Lubricant Workpiece Macrogeometry Rheology Macrogeometry MicrogeometryShear strength Microgeometry Roughness Temp. dependence Roughness Directionality Pressure dependence Directionality Mechanical properties Shear-rate dependence Mechanical properties Elastic Composition Elastic Plastic Bulk Plastic Ductile Carrier Ductile Fatigue Surface Fatigue CompositionBoundary and E.P. Composition Bulk Bulk Surface Surface Reaction product Temperature Reaction product Adsorbed film Adsorbed film Phases Application Phases Distribution Supply Distribution Interface Resupply Interface Temperature Temperature Atmosphere Velocity Velocity Process Process Geometry Surface extension Macro Virgin surfaces Micro Temperature Speed Contact time Approach Sliding Reactions Pressure Lubricant transfer Distribution Heat transfer
Friction Lubrication Adhesion Hydrodynamic Plastohydrodynamic Wear Mixed film Die Boundary Workpiece Dry
Equipment Product quality Pressures Surface finish Hydrodynamic Forces Deformation pattern lubrication Power requirements Metallurgical changes Plastohydrodynamic Mechanical properties lubrication Residual stresses Boundary Fracture lubrication
Figure 9.1 The tribological system. Source: Schey (1983), reproduced with permission. are never clean. An adsorbed film and an oxide layer are always present in industry as well as in a laboratory. It is, of course, possible, albeit difficult, to provide a controlled atmosphere while testing tribological attributes and this is often done. The results thus produced are of interest since the ability to control the independent variables is increased in a very significant manner; however, the applicability of 196 Primer on Flat Rolling
Die Figure 9.2 An enlarged view of the cross-section of two surfaces. Hard phases Source: Schey (1983), reproduced Matrix with permission. Adsorbed film ~ 30 Å
Reaction Workpiece (Oxide) film 20–100 Å Bulk
Surface layer 1–5 μm Disturbed enriched/depleted such data to a real-life, industrial environment is highly questionable. The surfaces are also never perfectly smooth2.
9.2.2 The Areas of Contact Two concepts need to be defined before any further discussion of the mechanisms of friction may be presented. The apparent area of contact, A, is the first and it is defined by the overall, outer dimensions of the contact surface. The real area of contact, usually denoted by Ar, affects the frictional phenomena in a much more fundamental manner and is defined as the totality of the areas in contact at the asperity tips. When the two surfaces approach one another, contact is first made at those tips, see Figure 9.3. It is to be realized that the shapes, dimensions, locations and contacts of the asperity tips are completely random; hence, the interactions may, most appropriately, be termed chaotic (Batchelor and Stachowiak, 1995). As the normal force increases, the asperities flatten and the real area of contact increases. If there is sufficient time note that no more than a few milliseconds, or even microseconds, are needed adhesive bonds are created, as described by the adhesion theory of Bowden and Tabor (1950) which gives the requirements for the establishment of adhesion: that the surfaces should be clean and close enough for interatomic contact. As the normal force increases and the asperity tips are flattened further, new, clean surfaces are created and the real area of contact approaches the apparent area. The rate of approach depends on the resistance to
2A strong criticism is offered here of the often-repeated statement “the surface is perfectly smooth” to imply a lack of friction. This comment was written very recently in a calculus text to be used in an introductory course. Exactly the opposite is correct as the smooth surfaces provide a large real contact area and lead to high frictional resistance. Moving two perfectly smooth surfaces in contact, relative to one another, would be difficult as the resistance to overcome would be at the maximum. The proper terminology, if no friction is to be assumed, should be “the surfaces are perfectly lubricated”, or better still, just write “the frictional resistance is taken to be zero”. Tribology 197
Flattened portions
Two surfaces are First contact is at The asperities approaching the asperity tips flatten and bonds are created
Figure 9.3 Asperities, valleys and the contact of two rough surfaces. deformation and the formability of the asperities. Relative movement of the contacting bodies is then possible only by applying a shear force, large enough to separate the contacting, flattened and bonded asperities.
9.2.2.1 The Relationship of the Apparent and the True Areas of Contact The definitions of the two areas, given above, are quite clear. The interest at this point is how A and Ar are related and how the true area may approach the apparent area when circumstances change. The implication of this is also clear: as the asperi- ties flatten while the loads are increased, the nature of the contact is changing and this will affect all of the interfacial phenomena. Schey (1983) classifies the reaction of asperities to the normal and shear stresses at the contact surfaces in the following manner:
G The average normal stress is below the flow strength of the work piece, creating elastic stresses within the bulk. The asperity tips are experiencing permanent deformation and the true area is approaching the apparent area. G In addition to the normal pressures, which are still below the flow strength, there is relative sliding in between the die and the work piece. G The normal pressures cause plastic flow of the bulk of the work piece. Bowden and Tabor (1964) discuss the events that occur when the asperity tips come into contact and there is a certain amount of normal force applied to the two bodies as they are approaching one another. While the average normal pressure may be well below the flow strength of either component, the stresses at the extremely small areas of the asperity tips will always be high enough to create permanent deformation. The tips will then deform and the load carried (W) will determine the true area of contact in terms of the flow strength of either body as:
W Ar 5 ð9:1Þ σfm where σfm, the flow strength, may well increase as the deformation is proceeding due to strain and strain rate hardening. The magnitude of the tangential force, (F), 198 Primer on Flat Rolling required to move one of the bodies with respect to the other, depends on the shear strength (τ) of the junction. That force may be a combination of adhesive and ploughing forces, depending on the nature of the contacting surfaces:
W F 5 Arτ 5 τ ð9:2Þ σfm
A more recent examination of the response of asperity tips to loads is reviewed by Stachowiak and Batchelor (2005). They quote the studies of Whitehouse and Archard (1970) and Onions and Archard (1973) which indicate that a large propor- tion of the contact between asperities is elastic under normal operating loads. They further mention, however, that an exception, that is, permanent asperity deforma- tion, may occur at the contact surfaces in metal working processes. Since the nor- mal pressures in bulk forming are significantly larger than in sheet metal forming processes, plastic deformation of the asperities there is an important contributor to surface phenomena. The first step is to determine if the contact is mostly elastic or is there a signifi- cant amount of plastic deformation of the tips of the asperities. This is accomplished by calculating the plasticity index, ψ. Stachowiak and Batchelor (2005) present three definitions for the plasticity index. They identify the first as due to Greenwood and Williamson (1966), followed by those of Whitehouse and Archard (1970) and by Bower and Johnson (1989). The three formulas give the index in terms of material and geometrical attributes. The easiest to use plasticity index is the one given by Bower and Johnson (1989) in the form: 0 ψ 5 E σκ 0:5 : s ð Þ ð9 3Þ ps
ψ σ where the plasticity index for repeated sliding is s, isthermssurfacerough- ness of the harder surface in m, κ is the curvature of the asperity tip in m21 and 3 ps is the shakedown pressure of the softer surface. If the stresses are below the shakedown pressure, the deformation is elastic; otherwise, plastic deformation is expected. The term E0 is the composite Young’s modulus for the two bodies in contact, a and b:
2 ν2 2 ν2 1 5 1 a 1 1 b : 0 ð9 4Þ E Ea Eb and ν is Poisson’s ratio.
3The shakedown pressure is a limit; when the magnitudes of stresses are below it, elastic deformation is present, while above it, plastic deformation occurs (Stachowiak and Batchelor, 2005). Tribology 199
The Whitehouse and Archard (1970) model defines the plasticity index as: E0 σ ψ 5 ð9:5Þ H β where H is the hardness of the deforming surface, and β is the correlation distance. When ψ , 0:6, elastic deformations are expected. When ψ . 1, most of the contacts experience plastic deformation. In the flat rolling process, especially where metals are concerned, significant plastic deformation of the asperities is certain to occur. To show that this is the case, consider the data of McConnell and Lenard (2000) where in each pass the average roll pressures are calculated to be in the range of 700 900 MPa while the yield strength of the rolled metal is in the order of 250 300 MPa; permanent deformation will be present. A relationship between the apparent area and the true area, when plastic deformation takes place has been given by Majumdar and Bhushan (1991) in the form:
W 5 KφA ð9:6Þ AE0 r
5 =σ φ 5 σ = 0 5 = σ where K H y, y E ,andAr Ar A and y is the yield strength. Re-substitution of these terms into Eq. (9.6) gives the true area of contact as a function of the load and the hardness of the deforming body, in a form similar to the Bowden and Tabor (1964) model, with the hardness replacing the flow strength:
W A 5 ð9:7Þ r H
Korzekwa et al. (1992), in stating the need for quantitative understanding of friction, present a model for the evolution of the contact area in a sheet undergo- ing a plastic forming process. A rate dependent material, subjected to large range of strains, is considered along with the effect of bulk deformation on asperity flattening, modelled as the indentation of a flat surface by a rigid punch. A visco- plastic finite-element model is used in the calculations of the changing true contact area as the deformation is continuing. While the results concentrate on low contact pressures which are appropriate in sheet metal forming operations, it is believed that with increasing loads the trends may not change markedly. The data are presented in the form of graphs, reproduced here as Figure 9.4, showing the changing contact area fraction, defined as the ratio of the half width of the rigid indenter to half the distance between the centres of the indenters, as a func- tion of the bulk effective strain. The deformation of stainless steel 304L was considered. The results indicate that the true area of contact increases as the normal pres- sures and the asperity slopes increase. As well, the straining directions also have a significant effect on the growth of the true contact area. 200 Primer on Flat Rolling
(A) Figure 9.4 Contact area 0.8 fraction as a function of the A bulk strain for a range 0.6 of normal pressures (A), asperity slopes (B) and straining directions (C). 0.4 Source: Korzekwa et al. (1992). 0.2 P = 8 MPa θ = 2° P Contact area fraction Contact area fraction = 20 MPa φ = 2.678 P = 40 MPa 0 0 0.1 0.2 0.3 0.4 0.5 Bulk effective strain (B) 0.8 A
0.6
0.4
0.2 θ = 1° P = 20 MPa Contact area fraction Contact area fraction θ = 2° φ = 2.678 θ = 5° 0 0 0.1 0.2 0.3 0.4 0.5 Bulk effective strain
Sutcliffe and co-workers have considered the problems associated with asperity deformation and the true and the apparent contact areas in flat rolling of metals. Their work is innovative and at the writing of the present manuscript, the most up to date. Sutcliffe (2000) lists two factors that affect frictional conditions: the manner in which the contacting surface asperities conform to each other while in contact and the frictional mechanisms at those contacting areas and at the valleys in between. He writes that in considering the deformation of the asperities, the effects of bulk deformation and of the wavelength need to be taken into account, as well. He writes that when sub-surface deformation is accounted for the realistic approach, especially in bulk metal forming and in flat rolling the asperities are shown to flatten more. Sutcliffe (2002) presents the rate of change of the ratio of contact areas as a function of the bulk strain. When the roll roughness is in the direction of rolling:
dA W 5 ð9:8Þ dε tan θ Tribology 201
1.0 Figure 9.5 The change of the area of contact ratio with bulk strain. 0.9 Source: Sutcliffe (2002), reproduced with permission. 0.8 P/2K = 1.0 0.66 0.7 A
0.6 P/2K = 0.40
0.5
0.4 Theory
Area of contact ratio ratio contact of Area 0.3 P/2K = 1.0 0.2 Experiments P/2K = 0.66 P/2K = 0.40 0.1
0 0.05 0.10 0.15 ε Bulk strain x
and when it is in the transverse direction: dA 1 W 5 2 A ð9:9Þ dε 1 1 ε tan θ where the bulk strain is designated by ε, the flattening rate is W and the slope of the asperities is θ. Integration of these relations yields the area of contact ratio as a function of the bulk strain and the normal pressure, shown in Figure 9.5. Reasonable agreement of the predictions and the measurements is observed in Figure 9.5. Stancu-Niederkorn et al. (1993) list some of the experimental techniques available to determine the real contact area. They classify them in two categories: off-process and in-process inspections. Off-process approaches, which cannot measure the elastic deformation, include measuring the profile after deformation by inspection or by inter- ferometry. The authors describe an experimental technique to measure the real contact area while the bulk of the work piece undergoes plastic deformation using ultrasound waves, the in-process inspection. Measurements were taken in free upsetting of steel samples and in closed-die upsetting, using copper specimens. Dry and lubricated conditions were examined. In the free upsetting tests, the real area of contact increased fast with increasing loads. In the closed-die upsetting, the real contact area reached about 95% of the apparent area at a normal load of 1100 MPa. Azushima (2000) used the finite-element method to analyse the deformation of the hills and 202 Primer on Flat Rolling valleys as a result of the pressure of the entrapped oil. He plotted the dependence of the contact area ratio on the reduction of the height of the asperities and found that without the oil the flattening is much more pronounced. The area ratio was found to remain relatively constant when the lubricant was entrapped in the valleys. Siegert et al. (1999) described the development of optical measurement techniques and computer workstation technology, using which they characterized the topography of sheet surfaces in three dimensions. The instrument is expected to be usable directly in the press shop.
9.2.3 Definitions of Frictional Resistance There are two traditional approaches to express the frictional phenomena in between two surfaces in contact, in relative movement and under pressure. In one of these, the coefficient of friction, as defined by Amonton and Coulomb and applied in most analyses of problems of metal forming, is given as the ratio of the interfacial shear stress to the normal pressure:
μ 5 τ=p ð9:10Þ
The friction factor, on the other hand, is given as the ratio of the interfacial shear stress and the yield strength in shear of the softer material in the contact:
m 5 τ=k where 0 # m # 1 ð9:11Þ
The existence of perfect lubrication is indicated when m 5 0 while m 5 1 points to sticking conditions. In developing mathematical models of bulk metal forming processes either coefficient may be used; however, both describe the interactions at the interface in a highly simplified manner and both involve some conceptual difficulties. Schey (1983) points out that the Amonton Coulomb definition becomes meaningless when the normal pressure is several times the flow strength of the metal. This is because the interfacial shear stress cannot rise beyond the yield strength in pure shear of the materials in contact and its ratio to the increasing normal pressure would continue to decrease and hence, the coefficient would also decrease. Mro´z and Stupkiewicz (1998) agree with Schey (1983), writing:
...the classical Amonton Coulomb model is not suitable for most metal forming processes...
The difficulty with the application of the friction factor is the lack of precise knowledge of the meaning of k, originally defined as the yield strength in pure shear of the softer material of the pair in contact, while ideally it should represent the strength of the interface. Again as pointed out by Schey (1983), the properties of the interface are not necessarily identical to the properties of the materials in contact. By examining Figure 9.2, which shows a realistic view of an interface, involving surface layers, oxides and adsorbed films, equating k of the interface to that of one of the materials may indeed be troublesome. Tribology 203
Wanheim (1973) was among the first researchers to write that the usual Coulomb Amonton model doesn’t apply at the high normal pressures which exist in bulk forming processes. In those cases he suggests that the frictional stress should be taken as a function of the normal pressure, surface topography, length of sliding, viscosity and the compressibility of the lubricant. Wanheim and Bay (1974, 1978) propose a general friction model, using the above-mentioned ideas. In their model, Coulomb friction is taken to be valid at low normal pressure whereas the friction stress approaches a constant value at high normal pressures. The approach was applied successfully to model the pressure distribution in plate rolling and the cross shear plate rolling process (Zhang and Bay, 1997). A mixed friction model was also used by Tamano and Yanagimoto (1978) with Coulomb friction at low pressures and sticking friction at high pressures. Another approach, mostly used in finite-element modelling, is to introduce a “friction layer” in between the con- tacting surfaces. Montmitonnet et al. (2000) discuss the wear mechanisms and the differential hardness of the tool and the work piece that create a third body in between the die and the worked metal, identified as the transfer layer. Regardless of the manner in which friction is to be modelled, some difficulties, uncertainties and unknowns will always remain. In Chapter 5, the friction factor was used in developing a 1D model of the flat rolling process, partially as the result of the comment of a reviewer of one of the present author’s recent manuscripts, questioning the use of the coefficient of friction in the flat rolling process. Several factors need to be considered when deciding to use “k”, the friction fac- tor. One is consideration of the pressure-sensitivity of lubricants4, which, for an Society of Automotive Engineering (SAE) 10 W oil, is given as 0.0229 MPa21 by Booser (1984), who also gives the viscosity as 32.6 mm2/s. If the roll pressure is 800 MPa, not an unreasonable magnitude when cold rolling steel, the Barus equa- tion (see Eq. (9.48)) gives the viscosity at that pressure as 2.9 3 109 mm2/s. This number, while possibly unrealistically high, indicates that shearing the lubricant at that pressure may well require as much of an effort as shearing the metal. The other is the comment, referred to above, concerning the level of stress at which the tung- sten nickel junction failed (Pashley et al., 1984) and the third, also mentioned above, is the conclusion that ploughing was the major frictional mechanism (Lenard, 2004; Dick and Lenard, 2005) when a sand-blasted roll was used. Carter (1994) and Montmitonnet et al. (2000) reinforce this last factor by indicating that ploughing may be as important as adhesion in understanding frictional resistance. The last consideration concerns the experimental difficulties in determining either the coefficient of friction or the friction factor. The coefficient is never measured directly in the many available tests that have been published; instead, the normal and the tangential forces are measured and their ratio yields the magnitudes. The friction factor, however, can be obtained easily by the well-known ring test5.
4The sensitivity of the lubricant to pressure will be discussed in Section 9.4.1.2. 5The ring test will be discussed in Section 9.3.1.3. 204 Primer on Flat Rolling
9.2.4 The Mechanisms of Friction The mechanisms of interface contact have been discussed with the aid of a very well prepared figure by Batchelor and Stachowiak (1995), reproduced here as Figure 9.6. They identify adhesion, ploughing and viscous shear as the main contributors to frictional resistance. In bulk forming processes the former two are the most likely events to occur, as complete separation of the surfaces and thus full hydro- dynamic conditions are rarely realized in practice. Montmitonnet et al. (2000) discuss surface interactions further and mention the possibility that particles will be detached from one of the contacting bodies, possibly resulting in micro- cutting. Further, a wave may be pushed along the surface, creating a bulge, or repeated contact may cause fatigue failure. The relative magnitudes of adhesion and ploughing have been examined by Mro´z and Stupkiewicz (1998). While developing a constitutive model for friction in metal forming processes, the authors indicate that friction forces include both adhesion and ploughing. They present a combined friction model, which simulates the interaction of the tool’s asperities with that of the work piece. In the mathematical model the effect of bulk plastic deformation is neglected; however, and as they write, experimental verification of the predictions is still required. Much depends on the angle of attack between the contacting surface asperities and on how the harder surface of the tool is prepared. Grinding, the traditional approach in preparing the rolls in the metal rolling industry, would produce relatively shallow angles while sand blasting would result in sharp asperities. Examining the effect of progressively rougher, sand-blasted rolls on the coefficient of friction and the resulting rolled surfaces, ploughing appeared to be the major component, contrib- uting to frictional forces and overwhelming the effects of adhesion (Lenard, 2004; Dick and Lenard, 2005).
Asperity of harder surface or trapped wear particle Ploughing Viscous drag
Body 1 Motion Shearing of film material body 1 Body 2 motion Wave of material Film material Plastically deformed layer body 2 Adhesion Adhesive bonding Deformed asperity Body 1 Motion
Figure 9.6 The major mechanisms of friction. Source: Batchelor and Stachowiak (1995). Tribology 205
9.3 Determining the Coefficient of Friction or the Friction Factor
Since the Coulomb coefficient of friction is defined as a ratio of forces and the friction factor is defined as a ratio of stresses, neither can be measured directly. Several experimental approaches are available, however, to determine various experimental parameters and thereby deduce the magnitude of the coefficient or the factor.
9.3.1 Experimental Methods Several methods for measuring interfacial frictional forces during plastic deformation have been developed, some of which have been listed by Wang and Lenard (1992). A more comprehensive list, applicable to other metal forming processes, including bulk and sheet metal forming, has been presented by Schey (1983). Some of the more useful approaches are described below.
9.3.1.1 The Embedded Pin Transducer Technique Originally suggested by Siebel and Lueg (1933) and adapted by van Rooyen and Backofen (1960) and Al-Salehi et al. (1973), the method has been applied to measure interfacial conditions in cold flat rolling (Karagiozis and Lenard, 1985; Lim and Lenard, 1984), warm rolling (Lenard and Malinowski, 1993) and hot rolling of steels (Lu et al., 2002) and aluminium (Hum et al., 1996). Variations of this procedure have been presented by Lenard (1990, 1991) and Yoneyama and Hatamura (1987). Typical results, obtained by this approach, are shown in Figures 9.7 and 9.8 for warm rolling of aluminium (Lenard and Malinowski, 1993) and hot rolling of
250 Figure 9.7 Roll pressure and friction 1100 H 14 Al 200 stress during warm rolling of an rolled at 100°C aluminium strip, obtained with the 150 12 rpm (157 mm/s) 39.5% reduction use of pins and transducers 100 embedded in the work roll. 50 Source: Lenard and Malinowski 0 (1993).
–50 Friction stress –100 –150 Roll pressure –200
Roll pressure and friction stress (MPa) –250 –300 048121620 Distance from exit (mm) 206 Primer on Flat Rolling
150 Figure 9.8 Roll pressure and Low-carbon steel friction stress during hot rolling 100 Friction stress Rolled at 1000°C 35 rpm (412 mm/s) of steel, obtained with the use of 20% reduction pins and transducers embedded 50 in the work roll. 0 Source: Lu et al. (2002).
–50
–100 Roll pressure –150
Roll pressure and friction stress (MPa) –200
–250 048121620 Distance from exit (mm)
steel (Lu et al., 2002), respectively. It is evident that the friction hill, derived by the traditional, 1D models of the flat rolling process and employing constant coefficients of friction, leads to unrealistic distribution of the roll pressures in the form of the friction hill. As Figures 9.7 and 9.8 show, detailed information of the distributions of interfacial frictional shear stresses and the work roll pressures may be obtained by these methods, but the experimental setup and the data acquisition are elabo- rate and costly. Since the major criticism concerns the possibility of some metal particle or oxide intruding into the clearance between the pins and their housing and invalidating the data, it is necessary to substantiate the resulting coefficients of friction by independent means. This substantiation has been performed successfully in several instances (see, e.g.,Humetal.,1996).Inthatstudy,the coefficients of friction, determined by the pin-transducer technique, were used in a model of the rolling process. The model calculated the roll forces and the roll torques which compared very well to the measured values, demonstrating that the technique leads to reliable data. Another difficulty encountered, when the embedded pins are used, is the interruption of the surface of the roll at the pins. The magnitude of the effect of this interruption is, at the present, unknown, but, considering the above described substantiation of the measurements, it is not expected to be significant. The use of the pins and transducers was reviewed quite some time ago by Cole and Sansome (1968). The authors concluded that the approach can provide reliable data as long as care is taken in the design, manufacture and calibration of the apparatus. A cantilever, machined out of the roll such that its tip is in the contact zone and fitted with strain gauges, and its various refinements were presented by Banerji and Rice (1972) and Jeswiet (1991). Tribology 207
9.3.1.2 The Refusal Technique Januszkiewicz and Sulek (1988) used the “refusal technique” to monitor the coeffi- cient of friction necessary to initiate entry of the strip into the roll gap in a study of the effects of contaminants on the lubricating properties of lubricants. This approach makes use of the minimum coefficient of friction, required to initiate the rolling process. Recalling Eq. (4.1), the coefficient needed to allow entry is dependent only on the bite angle. At small reductions the bite angle is small and the required coefficient is also small. This fact is employed in the rolling process in which progressively smaller reductions are attempted in each pass. The bite angle at which entry is first successful is then reported as the coefficient of friction.
9.3.1.3 The Ring Compression Test The most popular and most widely used technique to establish the friction factor, however, is the ring compression test (Kunogi, 1954; Male and Cockroft, 1964; Male and DePierre, 1970; DePierre and Gurney, 1974). In the test a ring of specific dimensions is compressed in between flat dies and the changes of its dimensions are related directly to the friction factor. Using calibration curves, the friction factor is obtained easily. The derivation of the calibration curves is well described by Avitzur (1968), who also presented a detailed set of calculations indicating how the curves are to be determined. The schematic diagram of the ring test and a typical calibration chart are shown in Figures 9.9 and 9.10. Bhattacharyya (1981) showed that under some circumstances the compressed rings develop tapering, with the top and bottom surfaces deforming in a different manner, most likely due to different tribological conditions on the two surfaces. The tapering disappeared when the samples were pre-compressed, and the true areas of the contact at the top and the bottom surfaces converged. Tan et al. (1998) used different ring geometries to study the ring compression process. Concave,
Figure 9.9 The ring compression test. P
OD
ID
H
P 208 Primer on Flat Rolling
80 Figure 9.10 A typical calibration chart for m the ring test. 0.8
0.4 40
(%) 0.2 D I Δ 0
0.1
0.05 –40
0 20406080 ΔH (%) rectangular and convex shaped cross-sections were employed. The results indicated that the influence of strain hardening on friction is complicated. Friction was affected by the normal pressure in a significant manner. Szyndler et al. (2003) compressed austenitic stainless steel rings at high tempera- tures, without lubrication, and used an inverse analysis to determine the friction factor. The factor’s dependence on the temperature was found to be well described by the relation m 5 3:511 3 1024T 2 0:01846, where the temperature is in C6, indicating that the friction factor increases with increasing temperatures.
9.3.2 Semi-Analytical Methods Numerous attempts to relate the coefficient of friction or the friction factor to various parameters have been presented in the literature, too many to be reviewed here. Only some, considered to be the more useful, are presented below.
9.3.2.1 Forward Slip Coefficient of Friction Relations Several formulae, connecting the forward slip to the average coefficient of friction, have been published in the technical literature. The predictive abilities of these relations have been studied (Lenard, 1992), and the results have been compared to data produced by the embedded-pin technique. While the conclusions indicated that the reviewed equations don’t work very well, they are presented below for completeness. It is recalled that the forward slip is given by:
vexit 2 vroll Sf 5 ð9:12Þ vroll
6The effect of the temperature on the coefficient of friction will be discussed in more detail in Sections 9.3.2.3 and 9.4.1.3. Tribology 209 where vexit stands for the exit velocity of the rolled strip and vroll designates the surface velocity of the work roll. Sims’ formula (1952) connects the forward slip to the reduction, r, the flattened 0 roll radius, R , the exit thickness, h2 and the coefficient of friction, μ: rffiffiffiffiffiffiffiffiffiffi pffiffiffiffi 1 r 1 1 tan21 S 5 tan21 2 ln ð9:13Þ f 2 1 2 r 2a 1 2 r where rffiffiffiffiffi μ R0 a 5 : 1 2 r h2
φ Ekelund’s (1933) formula gives the coefficient of friction in terms of the bite angle, 1, the roll radius and the forward slip as:
ðφ =2Þ2 μ 5 1 vffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi ð9:14Þ u 2S ðφ =2Þ 2 u f 1 t2R 2 1 h2
Bland and Ford (1948) use similar variables in giving the coefficient of friction as:
h 2 h μ 5 pffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi1 2 pffiffiffiffiffiffiffiffiffiffiffiffiffi ð9:15Þ 0 0 2 R ðh1 2 h2Þ 2 4 SfR h2
Roberts (1978) includes the roll force (Pr) and the torque for one roll (M/2) in addition to the reduction and the roll radius to define the coefficient of friction:
M=2 μ 5 "#rffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi ð9:16Þ S ð1 2 rÞ P R0 1 2 2 f r r
Another relationship, due to Inhaber (1966), includes the roll force and the roll torque, φ in addition to the neutral angle ( n), the arc of contact, the maximum pressure, P2, and the pressures at entry and the exit, P1 and P0, respectively. Note that in the absence of external tensions P1 equals the yield strength of the strip at the entry and the pressure at exit, P0, equals the yield strength there. The equation is
= 2 1 M 2 5 0 φ 2 φ P2 P1 : Pr 2R ð 1 nÞ ð9 17Þ Rμ lnðP2=P1Þ 210 Primer on Flat Rolling where the neutral angle is given in terms of the forward slip pffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi φ 5 = 0 : n Sf h2 R ð9 18Þ and the maximum pressure is calculated from c0 ln P0 2 c1 ln P1 1 P1 2 P0 P2 5 exp ð9:19Þ c0 2 c1 where 1 P M=2 c 5 r 2 ð9:20Þ 0 0 φ φ μ 2R n R n and
P 1 M=2R0μ c 5 r ð9:21Þ 1 0 α 2 φ 2R ð nÞ
In order to test the predictive abilities of the above listed formulae, the forward slip needs to be measured. This may be accomplished in several ways. One of the often used methods is to mark the roll surface with fine lines, parallel to the roll axis and placed uniformly around the roll. As the strip is rolled, these marks create impressions on the rolled surface. The forward slip may then be calculated by:
l 2 l S 5 1 ð9:22Þ f l where l1 is the average of the distances between the marks on the strip’s surface and l is the distance between the lines on the roll’s surface. It is expected that as long as the lines are created carefully, using sharp, hard tools, the resulting data on the forward slip is reasonably accurate. The predictions of Eqs. (9.13) (9.17) were compared to measurements of the coefficient friction and forward slip while rolling strips of commercially pure alu- minium (Lenard, 1992). The coefficients of friction were determined by force transducers embedded in the work rolls and the forward slip was obtained by the use of lines on the roll surface and by Eq. (9.22). The results are shown in Figure 9.11, plotting the coefficient of friction versus the forward slip. As Figure 9.11 shows, all relations predict realistic values for the coefficient of friction. However, the trends are not predicted well. Ekelund (1933), Sims (1952), Roberts (1978) and Bland and Ford (1948) all predict an increasing trend, reaching a plateau and then dropping; the measurements indicate an upward exponential. It is concluded that most of the formulae are not successful in providing reliable Tribology 211
0.3 Figure 9.11 Comparison of the calculated and the measured 0.25 forward slip. 0.2 Source: Lenard (1992).
0.15 Measurements Ekelund 0.1 Sims
Coefficient of friction Roberts 0.05 Inhaber Ford 0 0123456789101112 Forward slip
and consistent predictions. Arguably the best, though not perfect, approach is due to Inhaber (1966). Marking the roll’s surface, however carefully, may affect the interfacial condi- tions and hence, the frictional forces, although, as concluded when the embedded pins were used, these effects may not be very large. If lubricants are also present, the need to distribute them over the contact may also be compromised somewhat since the marks will act to retain some of the oils. There are alternatives for researchers who don’t want to mark the roll’s surface and these make use of optical devices. McConnell and Lenard (2000) used two photodiodes, located a known distance apart, to monitor the exit velocity of the rolled strip. The time interval between the signals of the diodes allowed the determination of the exit velocity and this, in turn, allowed the use of the original definition of the forward slip in terms of the roll’s and the strip’s speeds. Li et al. (2003) used laser Doppler velocimetry to mea- sure the relative velocities of the roll and the strip. It must be noted that measurements of the forward slip are often error prone. A simple examination of either Eq. (9.12) or (9.22) illustrates the difficulties. If, for example, the roll’s surface velocity is 900 mm/s and the strip’s exit velocity is 1000 mm/s, the forward slip is determined to be 0.11. If, however, the roll velocity is mistakenly measured to be 909 mm/s a 1% error the corresponding error is almost an order of magnitude higher. An interesting approach to determine the coefficient of friction using the for- ward and the backward slip was given by Silk and Li (1999). They use the original definition of the forward slip (see Eq. (9.12)), and the backward slip as the relative difference between the entry speed of the strip (v0) and speed of the roll:
v cos φ 2 v 5 r 1 0 ð : Þ Sb φ 9 23 vr cos 1
The authors make several assumptions which lead to simple expressions for the coefficient of friction in the forward slip zone, defined as the region between the 212 Primer on Flat Rolling
μ neutral point and the exit, f, and in the backward slip zone which is the region μ between the entry and the neutral point, b:
Δh=R0 μ 5 rffiffiffiffiffiffiffi rffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi ð9:24Þ f Δ h 2 2Sf hexit 2 0 4 0 R 2R 2 hexit and
Δ = 0 μ 5 rffiffiffiffiffiffiffi rffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffih R : b ð9 25Þ Δh h cos φ h 2 2 4 ð1 2 S Þ entry 1 2 exit R0 b 2R0 R0
These relations are subject to the following assumptions:
G Coulomb friction exists between the roll and the rolled metal; G the roll pressure is constant over the contact area; and G the angles are small compared to unity. In order to determine the coefficients, numerical values for the forward and the backward slips are necessary. Silk and Lee (1999) use information obtained from the instrumented loopers of the hot strip mill of Hoogovens7; their results refer to stands F2 and F3 of the Hoogovens hot strip mill. The magnitudes of the coeffi- cients of friction vary from 0.15 to 0.23 in both stands, realistic values considering the efficient lubrication applied in the mill.
9.3.2.2 Empirical Equations Cold Rolling The three well-known formulas, connecting the coefficient of friction to the roll separating force, rely on matching the measured and calculated forces and choosing the coefficient of friction to allow that match. One of the often-used formulae, given by Hill, is quoted by Hoffman and Sachs (1953) in the form: P h pffiffiffiffiffiffiffiffiffiffiffir 2 1:08 1 1:02 1 2 exit σ R0Δh hentry μ 5 sffiffiffiffiffiffiffiffiffiffi ð9:26Þ h R0 1:79 1 2 exit hentry hentry
where Pr is the roll separating force per unit width, σ is the average plane-strain flow strength in the pass and R0 is the radius of the flattened roll. Roberts (1967) derived a relationship for the coefficient of friction in terms of 0 the roll separating force Pr, the radius of the flattened roll R , the reduction r, the
7Hoogovens is a steel producer in the Netherlands. Tribology 213
average of the tensile stresses at the entry and exit σ1, the average flow strength of the metal in the pass, σ and the entry thickness of the strip, hentry: rffiffiffiffiffiffiffiffiffiffi"#sffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi 2 μ 5 hentry Prð1 rÞ 1 2 1 5r : 2 0 0 1 ð9 27Þ R r σ 2 σ1 R hentryr 4
Ekelund’s equation, given by Rowe (1977) in the form of the roll separating force in terms of material and geometrical parameters and the coefficient of friction, may be inverted to yield the coefficient of friction: Pr pffiffiffiffiffiffiffiffiffiffiffi 2 1 ðhentry 1 hexitÞ 1 1:2Δh σ R0Δh μ 5 pffiffiffiffiffiffiffiffiffiffiffi ð9:28Þ 1:6 R0Δh
A comparison of the predicted magnitudes of the coefficient by these formulae is shown in Figure 9.12, using data obtained while cold rolling steel strips lubricated with a light mineral seal oil (McConnell and Lenard, 2000). Two nominal reductions are considered. The first is for 15% and the second is for 50%, of originally 0.96 mm thick, 25 mm wide, AISI 1005 carbon steel strips. The metal’s uniaxial flow strength, : in MPa, is σ 5 150ð11234 εÞ0 251. The tests were repeated at progressively increasing roll surface velocities, from a low of 0.2 to 2.4 m/s. Care was taken to apply the same amount of lubricant in each test: 10 drops of the oil on each side of the strip, spread evenly. In Figure 9.12, the coefficient of friction is plotted versus the roll surface velocity, which does not appear in any of the above formulae in an explicit manner. However, the effect of increasing speed is felt by the roll force, which, as expected, is reduced as the relative velocity at the contact surface increases. Increasing velocity is expected to bring more lubricant to the entry to the contact zone. The dropping frictional
0.50 Figure 9.12 The coefficient of friction, as predicted by Hill’s, Roberts’ and 15% reduction Hill Roberts Ekelund’s formulae, for cold rolling 0.40 Ekelund of a low-carbon steel. Source: McConnell and Lenard (2000). 0.30
0.20 45% reduction Coefficient of friction
0.10
0.00 0 500 1000 1500 2000 2500 Roll surface speed (mm/s) 214 Primer on Flat Rolling resistance indicates the efficient entrainment of the lubricant and its distribution between the roll and the strip surfaces. No starvation of the contacting surfaces is observed. All three formulae give realistic, albeit somewhat high, numbers for the coefficient of friction and all predict the expected trend of decreasing coefficient with increasing velocity. As well, the coefficient of friction is indicated to decrease as the reductions increase, demonstrating the combined effects of the increasing number of contact points, the increasing temperature and the increasing normal pressures. The first two phenomena result in increasing frictional resistance with reduction. The third causes increasing viscosity and hence, decreasing friction and, as shown by the data, it has the dominant effect on the coefficient of friction. The magnitudes vary over a wide range, however, indicating that the mathematical model also influences the results in a significant manner. An analytical approach, to determine the coefficient of friction, has been pre- sented by Li (1999). Two approaches were given, both subject to several, a priori, assumptions: homogeneous plane-strain compression is present; the coefficient of friction is constant in the arc of contact; the strip is rigid-plastic; the neutral plane is within the arc of contact and the rate of strain is low. In the first approach, the roll pressure distribution, as predicted by Bland and Ford (1948), is used, the rolling strain is determined and the minimum coefficient of friction for steady-state rolling without skidding is obtained as: ε 2 μ 5 a : c ð9 29Þ H0 where H0 is the entry thickness and a is defined as a tension parameter in terms of the front and back tensions (σt;f and σt;b, respectively) and the rolled strip’s strength at the entry and exit (σ0 and σ1,respectively): σ ; σ ; a 5 ln 1 2 t b 2 ln 1 2 t f ð9:30Þ σ0 σ1
The coefficient of friction is then obtained in an iterative manner, until the measured and calculated rolling strains agree. In the second approach the forward slip is used. A relationship is then derived, in terms of the coefficient of friction, μ, the thickness at the entry and the exit, h0 and h1, the bite angle, α and the forward slip, Sf:
2 qffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi3 1 μ α μ α μ α μ cot α cot 1 2 cot α2 2μ2 2 φ cot cot h1 h1 ð1 cot 1Þh0 h1 4 5 5ðS 11Þh ð9:31Þ 11μ cot α f 1
Using the measured forward slip and iterating, the coefficient of friction is calcu- lated. The magnitudes of the calculated coefficients of friction are as measured or Tribology 215 predicted elsewhere. The results indicate that as the rolling strain increases, the coefficient also increases, a finding valid for cold rolling of aluminium but contra- dicting most experimental data, obtained while rolling steel, which indicate the increasing reductions result in dropping coefficients of friction. Beynon et al. (2000) studied friction and the formation of scales on the surfaces of hot rolled steels. They determined the coefficient of friction by using the forward and the backward slip data, measuring the speed of the roll and of the strip simultaneously and using the model of Li (1999), described previously. Their results indicate that mixed sliding/sticking conditions exist in the contact zone. Further, a neutral zone, rather than a neutral plane, is present there. Martin et al. (1999) analysed friction during finish rolling of steel strips. A com- bination of experimental data and a coupled thermomechanical model of the rolling process was used. Their conclusions are interesting in that they contradict existing beliefs: the frictional conditions exhibited weak correlation with rolling speed, temperature and reduction.
9.3.2.3 The Study of Tabary et al. (1994) A somewhat different approach was followed by Tabary et al. (1994) in determining the coefficient of friction during cold rolling of fairly soft, 1200 aluminium alloy strips. The authors mention the difficulties associated with the determination of the coefficient of friction in the roll bite. One of the difficulties is the changing direction of the friction force in the roll gap, aiding the movement of the strip until the no-slip region is reached and retarding its movement beyond, until the exit is reached. The location of the no-slip region may be manipulated by applying external tensions and that is the approach followed in this study. Using external tensions the neutral point is forced to be at the exit, causing the friction forces in the deformation zone to act only in one direction. The von Karman differential equation of equilibrium was then integrated with assumed values for the coefficient of friction and the inlet yield strength. Both of these were adjusted until the calculated and the measured roll forces matched and the boundary condition at the exit was satisfied, so the method is essen- tially one of the inverse analyses. A rare and most welcome section of Tabary et al.’s paper is the analysis of the errors in the reported values of the coefficient of friction. They also account for the μ contribution of the hydrodynamic action to the coefficient of friction, h, according to the relation: τ ηΔ μ 5 0 21 u : h sinh ð9 32Þ p τ0hs where p is the average roll pressure and η is the viscosity at p. The average relative speed is Δu, the smooth film thickness is hs and τ0 is the Eyring shear stress, estimated to be 2 MPa. The results indicate that the coefficient of friction is a strong function of the reduction and of the ratio of the smooth lubricant film thickness to the 216 Primer on Flat Rolling combined rms roughness (Λ). The coefficients increase with increasing reduc- tion and drop with increasing Λ, varying from a high of approximately 0.08 to a low of 0.02.
9.3.2.4 Empirical Equations and Experimental Data Hot Rolling Formulae, specifically intended for use in the analyses of flat, hot rolling of steel, have also been published. Those given by Roberts (1983) and by Geleji, as quoted by Wusatowski (1969), are presented below. Roberts’ formula indicates that the coefficient of friction increases with the temperature. Geleji’s relations indicate the opposite trend. Roberts (1983) combined the data obtained from an experimental two-high mill, an 84-in. hot strip mill and a 132-in. hot strip mill, all rolling well- descaled strips, and used a simple mathematical model to calculate the frictional coefficient. Linear regression analysis then led to the relation:
μ 5 2:7 3 1024T 2 0:08 ð9:33Þ where T is the temperature of the work piece in F. Geleji’s formulae, given below, have also been obtained by the inverse method, matching the measured and calculated roll forces. For steel rolls the coefficient of friction is given by:
μ 5 1:05 2 0:0005T 2 0:056v ð9:34Þ where the temperature is T, given here in C and v is the rolling velocity in m/s. For double poured and cast rolls the relevant formula is
μ 5 0:94 2 0:0005T 2 0:056v ð9:35Þ and for ground steel rolls:
μ 5 0:82 2 0:0005T 2 0:056v ð9:36Þ
It is observed that Geleji’s relations, indicating decreasing frictional resistance with increasing temperature and rolling speed, confirm experimental trends. Note also, that the predictions of Roberts see Eq. (9.33) indicate the opposite trend, agreeing with the results of Szyndler et al. (2003), who obtained the friction factor as a function of the temperature during ring compression of stainless steel samples. Rowe (1977) also gives Ekelund’s formula for the coefficient of friction in hot rolling of steel:
μ 5 0:84 2 0:0004T ð9:37Þ where the temperature is to be in excess of 700 C, again indicating that increasing temperatures lead to lower values of the coefficient of friction. Tribology 217
Underwood (1950) attributes another equation to Ekelund, similar to those above, giving the coefficient of friction as:
μ 5 1:05 2 0:0005T ð9:38Þ
Roberts (1977) presents a relationship for the coefficient of friction for a well- descaled strip of steel, in terms of the strip’s temperature T in F, obtained by fitting an empirical relationship to data, obtained by inverse calculations: 22:61 3 104 μ 5 2:77 3 104 exp 1 0:21 ð9:39Þ 459 1 T
A comparison of the predictions indicates that the relations may not be completely reliable in all instances. For example, using a steel work roll and a rolling a steel strip at a temperature of 1000 C and at a velocity of 3 m/s, Roberts’ equation predicts a coefficient of friction of 0.415 while Geleji’s relation gives 0.382, indicating that while the numbers are close, the difference, almost 8%, is not insignificant. When 900 C is considered, Roberts’ coefficient becomes 0.366 and Geleji’s increases to 0.432, creating a large difference. Ekelund’s predictions are 0.44 and 0.48, at 900 C and 1000 C, respectively. It is difficult to recommend any of these relations for use in modelling. Lenard and Barbulovic-Nad (2002) hot rolled low-carbon steel strips at entry temperatures varying from a low of 800 C to 1100 C, using an emulsion of Imperial Oil 8581 and distilled water, at a ratio of 1:1000. During heating, the strips were held in a furnace which was purged using oxygen-free nitrogen, allow- ing close control of the scale thickness. The roll separating forces, the roll torques, the roll speed and the entry and exit strip surface temperatures were measured in each pass. The coefficient of friction was obtained by inverse calculations, using the refined 1D model, presented in Section 5.4. Non-linear regression analysis led to the relationship: