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Engine Components and Filters: Damage Profiles, Probable Causes and Prevention
ENGINE COMPONENTS AND FILTERS: DAMAGE PROFILES, PROBABLE CAUSES AND PREVENTION Technical Information AFTERMARKET Contents 1 Introduction 5 2 General topics 6 2.1 Engine wear caused by contamination 6 2.2 Fuel flooding 8 2.3 Hydraulic lock 10 2.4 Increased oil consumption 12 3 Top of the piston and piston ring belt 14 3.1 Hole burned through the top of the piston in gasoline and diesel engines 14 3.2 Melting at the top of the piston and the top land of a gasoline engine 16 3.3 Melting at the top of the piston and the top land of a diesel engine 18 3.4 Broken piston ring lands 20 3.5 Valve impacts at the top of the piston and piston hammering at the cylinder head 22 3.6 Cracks in the top of the piston 24 4 Piston skirt 26 4.1 Piston seizure on the thrust and opposite side (piston skirt area only) 26 4.2 Piston seizure on one side of the piston skirt 27 4.3 Diagonal piston seizure next to the pin bore 28 4.4 Asymmetrical wear pattern on the piston skirt 30 4.5 Piston seizure in the lower piston skirt area only 31 4.6 Heavy wear at the piston skirt with a rough, matte surface 32 4.7 Wear marks on one side of the piston skirt 33 5 Support – piston pin bushing 34 5.1 Seizure in the pin bore 34 5.2 Cratered piston wall in the pin boss area 35 6 Piston rings 36 6.1 Piston rings with burn marks and seizure marks on the 36 piston skirt 6.2 Damage to the ring belt due to fractured piston rings 37 6.3 Heavy wear of the piston ring grooves and piston rings 38 6.4 Heavy radial wear of the piston rings 39 7 Cylinder liners 40 7.1 Pitting on the outer -
United States Patent (19) (11) 4,364,353 Fiala 45) Dec
United States Patent (19) (11) 4,364,353 Fiala 45) Dec. 21, 1982 (54) ANTI-KNOCKING APPARATUS FOR AN 4,153,020 5/1979 King et al. .......................... 123/425 NTERNAL COMBUSTON ENGINE FOREIGN PATENT DOCUMENTS 75) Inventor: Ernst Fiala, Wolfsburg, Fed. Rep. of 2274796 1/1976 France. Germany 2337261 7/1977 France . 73) Assignee: Volkswagenwerk Aktiengesellschaft, Wolfsburg, Fed. Rep. of Germany OTHER PUBLICATIONS SAE-Paper No. 7901 73, "Energy Conservation with 21 Appl. No.: 219,352 Increased Compression Ratio and Electronic Knock 22 Filed: Dec. 22, 1980 Control', by Currie, Grossman and Gumbleton, 1979. (30) Foreign Application Priority Data Primary Examiner-Charles J. Myhre Assistant Examiner-Andrew M. Dolinar Dec. 20, 1979 DE Fed. Rep. of Germany ....... 2951321 Attorney, Agent, or Firm-Spencer & Kaye (5) Int. Cl............................ F02P 5/14; F02D 9/00 52 U.S.C. ..................................... 123/425; 123/435 57 ABSTRACT 58) Field of Search ............... 123/425, 419, 435, 436, For reducing knocking in an externally ignited, mix 123/198 A ture-compressing internal combustion engine, the mo ment of ignition is delayed up to a predetermined maxi (56) References Cited mum as a function of signals emitted by a knocking U.S. PATENT DOCUMENTS sensor. Thereafter, if engine knocking continues, the 2,401,563 6/1946 Hersey ................................ 123/425 throttle valve is moved in the closing sense. 2,595,524 5/1952 Henneman et al.................. 123/435 4,002,155 1/1977 Harned et al. ...................... 123/425 1 Claim, 2 Drawing Figures DEAD PONT 31 37 NDICATOR 32 23 25 26 SERVO DISTR MECHANISM KNOCKING ME SIGNAL AMPL SELECTOR BUTOR SENSOR WINDOW.COMPARATOR ER TCH SERVO THROTTLE 20 22 MECHANISM WAWE EVEL 24 ACCOMO CONTROL ;ARACTERSTC ACCELERATOR DATION LOGIC MEMORY PEDAL ENGINE THROTTLE SPEED ANGLE SENSOR NDICATOR 30 IGNITION ANGLE NDCATOR 29 U.S. -
A Method of Fuel Testing in a CFR Engine
Scholars' Mine Masters Theses Student Theses and Dissertations 1960 A method of fuel testing in a CFR engine George R. Baumgartner Follow this and additional works at: https://scholarsmine.mst.edu/masters_theses Part of the Mechanical Engineering Commons Department: Recommended Citation Baumgartner, George R., "A method of fuel testing in a CFR engine" (1960). Masters Theses. 5575. https://scholarsmine.mst.edu/masters_theses/5575 This thesis is brought to you by Scholars' Mine, a service of the Missouri S&T Library and Learning Resources. This work is protected by U. S. Copyright Law. Unauthorized use including reproduction for redistribution requires the permission of the copyright holder. For more information, please contact [email protected]. A METHOD OF FUEL TESTING IN A CFR ENGINE BY GEORGE R. BAUMGARTNER ----~--- A THESIS submitted to the faculty of the SCHOOL OF MINES AND METALLURGY OF THE UNIVERSITY OF MISSOURI in partial fulfillment of the work required for the Degree of MASTER OF SCIENCE IN MECHANICAL ENGINEERING Rolla, Missouri 1960 _____ .. ____ .. ii ACKNOWLEDGEMENT The author would like to express his appreciation to Dr. A. J• Miles, Chairman of tho Mechanical Engineering Department, and Professor G. L. Scofield, Mechanical Engineering Department, for their guidance and interest in this investigation. Thanks are also dua Mr. Douglas Kline for his constant assistance while conducting the tests. iii TABLE OF CONTENTS Acknowledgement •••••••••••••••••••••••••••••••••••••••••• ii Contents•••••••••••••••••••••••••••••••••••••o•••••••••• -
Motor Gasolines Technical Review Motor Gasolines Technical Review Chevron Products Company
fold Motor Gasolines Technical Review Motor Gasolines Technical Review Technical Gasolines Motor Chevron Products Company Products Chevron Chevron Products Company 6001 Bollinger Canyon Road San Ramon, CA 94583 www.chevron.com/products/ourfuels/prodserv/fuels/ technical_safety_bulletins/ Chevron Products Company is a division of a wholly owned subsidiary of Chevron Corporation. © 2009 Chevron Corporation. All rights reserved. Chevron is a trademark of Chevron Corporation. Recycled/RecyclableRecycled/recyclable paper paper 10M IDC 69083 06/09 MS-9889 (06-09) center The products and processes referred to in this document are trademarks, registered trademarks, or service marks of their respective companies or markholders. Motor Gasolines Technical Review Written, edited, and designed by employees and contractors of Chevron Corporation: Lew Gibbs, Bob Anderson, Kevin Barnes, Greg Engeler, John Freel, Jerry Horn, Mike Ingham, David Kohler, David Lesnini, Rory MacArthur, Mieke Mortier, Dick Peyla, Brian Taniguchi, Andrea Tiedemann, Steve Welstand, David Bernhardt, Karilyn Collini, Andrea Farr, Jacqueline Jones, John Lind, and Claire Tom. Chapter 5 prepared by Jack Benson of AFE Consulting Services. Motor Gasolines Technical Review (FTR-1) © 2009 Chevron Corporation. All rights reserved. center The products and processes referred to in this document are trademarks, registered trademarks, or service marks of their respective companies or markholders. Motor Gasolines Technical Review Written, edited, and designed by employees and contractors of Chevron Corporation: Lew Gibbs, Bob Anderson, Kevin Barnes, Greg Engeler, John Freel, Jerry Horn, Mike Ingham, David Kohler, David Lesnini, Rory MacArthur, Mieke Mortier, Dick Peyla, Brian Taniguchi, Andrea Tiedemann, Steve Welstand, David Bernhardt, Karilyn Collini, Andrea Farr, Jacqueline Jones, John Lind, and Claire Tom. -
Technical Report: Engine and Emission System Technology
Technical Report: Engine and Emission System Technology Spark Ignition Petrol: Euro 5 & Beyond - Light Duty V ehicles © Copyright 2016 ABMARC Disclaimer By accepting this report from ABMARC you acknowledge and agree to the terms as set out below. This Disclaimer and denial of Liability will continue and shall apply to all dealings of whatsoever nature conducted between ABMARC and yourselves relevant to this report unless specifically varied in writing. ABMARC has no means of knowing how the report’s recommendations and or information provide d to you will be applied and or used and therefore denies any liability for any losses, damages or otherwise as may be suffered by you as a result of your use of same. Reports, recommendations made or information provided to you by ABMARC are based on ext ensive and careful research of information some of which may be provided by yourselves and or third parties to ABMARC. Information is constantly changing and therefore ABMARC accepts no responsibility to you for its continuing accuracy and or reliability. Our Reports are based on the best available information obtainable at the time but due to circumstances and factors out of our control could change significantly very quickly. Care should be taken by you in ensuring that the report is appropriate for your needs and purposes and ABMARC makes no warranty that it is. You acknowledge and agree that this Disclaimer and Denial of Liability extends to all Employees and or Contractors working for ABMARC. You agree that any rights or remedies available to you pursuant to relevant Legislation shall be limited to the Laws of the State of Victoria and to the extent permitted by law shall be limited to such monies as paid by you for the re levant report, recommendations and or information. -
DEUTZ Pose Also Implies Compliance with the Con- Original Parts Is Prescribed
Operation Manual 914 Safety guidelines / Accident prevention ● Please read and observe the information given in this Operation Manual. This will ● Unauthorized engine modifications will in- enable you to avoid accidents, preserve the validate any liability claims against the manu- manufacturer’s warranty and maintain the facturer for resultant damage. engine in peak operating condition. Manipulations of the injection and regulating system may also influence the performance ● This engine has been built exclusively for of the engine, and its emissions. Adherence the application specified in the scope of to legislation on pollution cannot be guaran- supply, as described by the equipment manu- teed under such conditions. facturer and is to be used only for the intended purpose. Any use exceeding that ● Do not change, convert or adjust the cooling scope is considered to be contrary to the air intake area to the blower. intended purpose. The manufacturer will The manufacturer shall not be held respon- not assume responsibility for any damage sible for any damage which results from resulting therefrom. The risks involved are such work. to be borne solely by the user. ● When carrying out maintenance/repair op- ● Use in accordance with the intended pur- erations on the engine, the use of DEUTZ pose also implies compliance with the con- original parts is prescribed. These are spe- ditions laid down by the manufacturer for cially designed for your engine and guaran- operation, maintenance and servicing. The tee perfect operation. engine should only be operated by person- Non-compliance results in the expiry of the nel trained in its use and the hazards in- warranty! volved. -
High Pressure Ratio Intercooled Turboprop Study
E AMEICA SOCIEY O MECAICA EGIEES 92-GT-405 4 E. 4 S., ew Yok, .Y. 00 h St hll nt b rpnbl fr ttnt r pnn dvnd In ppr r n d n t tn f th St r f t vn r Stn, r prntd In t pbltn. n rnt nl f th ppr pblhd n n ASME rnl. pr r vlbl fr ASME fr fftn nth ftr th tn. rntd n USA Copyright © 1992 by ASME ig essue aio Iecooe uoo Suy C. OGES Downloaded from http://asmedigitalcollection.asme.org/GT/proceedings-pdf/GT1992/78941/V002T02A028/2401669/v002t02a028-92-gt-405.pdf by guest on 23 September 2021 Sundstrand Power Systems San Diego, CA ASAC NOMENCLATURE High altitude long endurance unmanned aircraft impose KFT Altitude Thousands Feet unique contraints on candidate engine propulsion systems and HP Horsepower types. Piston, rotary and gas turbine engines have been proposed for such special applications. Of prime importance is the HIPIT High Pressure Intercooled Turbine requirement for maximum thermal efficiency (minimum specific Mn Flight Mach Number fuel consumption) with minimum waste heat rejection. Engine weight, although secondary to fuel economy, must be evaluated Mls Inducer Mach Number when comparing various engine candidates. Weight can be Specific Speed (Dimensionless) minimized by either high degrees of turbocharging with the Ns piston and rotary engines, or by the high power density Exponent capabilities of the gas turbine. pps Airflow The design characteristics and features of a conceptual high SFC Specific Fuel Consumption pressure ratio intercooled turboprop are discussed. The intended application would be for long endurance aircraft flying TIT Turbine Inlet Temperature °F at an altitude of 60,000 ft.(18,300 m). -
Diesel Engine Starting Systems Are As Follows: a Diesel Engine Needs to Rotate Between 150 and 250 Rpm
chapter 7 DIESEL ENGINE STARTING SYSTEMS LEARNING OBJECTIVES KEY TERMS After reading this chapter, the student should Armature 220 Hold in 240 be able to: Field coil 220 Starter interlock 234 1. Identify all main components of a diesel engine Brushes 220 Starter relay 225 starting system Commutator 223 Disconnect switch 237 2. Describe the similarities and differences Pull in 240 between air, hydraulic, and electric starting systems 3. Identify all main components of an electric starter motor assembly 4. Describe how electrical current flows through an electric starter motor 5. Explain the purpose of starting systems interlocks 6. Identify the main components of a pneumatic starting system 7. Identify the main components of a hydraulic starting system 8. Describe a step-by-step diagnostic procedure for a slow cranking problem 9. Describe a step-by-step diagnostic procedure for a no crank problem 10. Explain how to test for excessive voltage drop in a starter circuit 216 M07_HEAR3623_01_SE_C07.indd 216 07/01/15 8:26 PM INTRODUCTION able to get the job done. Many large diesel engines will use a 24V starting system for even greater cranking power. ● SEE FIGURE 7–2 for a typical arrangement of a heavy-duty electric SAFETY FIRST Some specific safety concerns related to starter on a diesel engine. diesel engine starting systems are as follows: A diesel engine needs to rotate between 150 and 250 rpm ■ Battery explosion risk to start. The purpose of the starting system is to provide the torque needed to achieve the necessary minimum cranking ■ Burns from high current flow through battery cables speed. -
Calculating Compression Ratio/Engine Displacement Practice Small Power and Equipment Secti
Calculating Compression Ratio/Engine Displacement Practice Small Power and Equipment Section 1 – Compression Ratio Calculate the compression ratio for a small engine given the following information (SHOW ALL WORK!!!): Bore of the cylinder (B) = 105 mm Stroke of the engine (S) = 90 mm Compressed Gasket Thickness (Gt) = 3.5 mm Bore of the gasket (Gb) = 93.5 mm Volume of the combustion chamber in the cylinder head (Vcc) = 50 ml Gross Piston Head Volume (Vphg) = 80 ml Piston Depression (Pd) = 25 mm Item Symbol Formula Formula Result Applied Depression Vdp B x B x Pd x F Volume Net Piston Vph Vphg - Vdp Head Volume Gasket Volume Vg Gb x Gb x Gt x F TDC Volume Vtdc Vcc + Vg + Vph Swept Volum Vsw B x B x S x F e BDC Volume Vbdc Vtdc + Vsw Compression CR Vbdc / Vtdc Ratio Calculating Compression Ratio/Engine Displacement Practice Small Power and Equipment Bore of the cylinder (B) = 110 mm Stroke of the engine (S) = 75 mm Compressed Gasket Thickness (Gt) = 1.5 mm Bore of the gasket (Gb) = 80.5 mm Volume of the combustion chamber in the cylinder head (Vcc) = 50 ml Gross Piston Head Volume (Vphg) = 88 ml Piston Depression (Pd) = 15 mm Item Symbol Formula Formula Result Applied Depression Vdp B x B x Pd x F Volume Net Piston Vph Vphg - Vdp Head Volume Gasket Volume Vg Gb x Gb x Gt x F TDC Volume Vtdc Vcc + Vg + Vph Swept Volum Vsw B x B x S x F e BDC Volume Vbdc Vtdc + Vsw Compression CR Vbdc / Vtdc Ratio Section 2 – Engine Displacement (5 points each = 10 points) Calculate the engine displacement given the following information (SHOW ALL WORK!!!). -
High Efficiency VCR Engine with Variable Valve Actuation and New Supercharging Technology
AMR 2015 NETL/DOE Award No. DE-EE0005981 High Efficiency VCR Engine with Variable Valve Actuation and new Supercharging Technology June 12, 2015 Charles Mendler, ENVERA PD/PI David Yee, EATON Program Manager, PI, Supercharging Scott Brownell, EATON PI, Valvetrain This presentation does not contain any proprietary, confidential, or otherwise restricted information. ENVERA LLC Project ID Los Angeles, California ACE092 Tel. 415 381-0560 File 020408 2 Overview Timeline Barriers & Targets Vehicle-Technology Office Multi-Year Program Plan Start date1 April 11, 2013 End date2 December 31, 2017 Relevant Barriers from VT-Office Program Plan: Percent complete • Lack of effective engine controls to improve MPG Time 37% • Consumer appeal (MPG + Performance) Budget 33% Relevant Targets from VT-Office Program Plan: • Part-load brake thermal efficiency of 31% • Over 25% fuel economy improvement – SI Engines • (Future R&D: Enhanced alternative fuel capability) Budget Partners Total funding $ 2,784,127 Eaton Corporation Government $ 2,212,469 Contributing relevant advanced technology Contractor share $ 571,658 R&D as a cost-share partner Expenditure of Government funds Project Lead Year ending 12/31/14 $733,571 ENVERA LLC 1. Kick-off meeting 2. Includes no-cost time extension 3 Relevance Research and Development Focus Areas: Variable Compression Ratio (VCR) Approx. 8.5:1 to 18:1 Variable Valve Actuation (VVA) Atkinson cycle and Supercharging settings Advanced Supercharging High “launch” torque & low “stand-by” losses Systems integration Objectives 40% better mileage than V8 powered van or pickup truck without compromising performance. GMC Sierra 1500 baseline. Relevance to the VT-Office Program Plan: Advanced engine controls are being developed including VCR, VVA and boosting to attain high part-load brake thermal efficiency, and exceed VT-Office Program Plan mileage targets, while concurrently providing power and torque values needed for consumer appeal. -
Design and Assembly of a Throttle for an HCCI Engine
Design and assembly of a throttle for an HCCI engine ÀLEX POYO MUÑOZ Master of Science Thesis Stockholm, Sweden 2009 Design and assembly of a throttle for an HCCI engine Àlex Poyo Muñoz Master of Science Thesis MMK 2009:63 MFM129 KTH Industrial Engineering and Management Machine Design SE-100 44 STOCKHOLM Examensarbete MMK 2009:63 MFM129 Konstruktion och montering av ett gasspjäll för en HCCI-motor. Àlex Poyo Muñoz Godkänt Examinator Handledare 2009-Sept-18 Hans-Erik Ångström Hans-Erik Ångström Uppdragsgivare Kontaktperson KTH Hans-Erik Ångström Sammanfattning Denna rapport handlar om införandet av ett gasspjäll i den HCCI motor som utvecklas på Kungliga Tekniska Högskolan (KTH) i Stockholm. Detta gasspjäll styr effekten och arbetssättet i motorn. Med en gasspjäll är det möjligt att byta från gnistantändning till HCCI-läge. Under projektet har många andra områden förbättrats, till exempel luft- och oljepump. För att dra slutsatser är det nödvändigt att analysera några av motorns data som insamlats under utvecklingen, såsom cylindertryck, insprutningsdata och tändläge. Man analyserade data under olika tidpunkter av motorns utveckling, med olika komponenter, för att uppnå olika prestanda i varje enskilt fall. För att köra motorn i HCCI-läge är det nödvändigt att ha ett lambda-värde mellan 1,5 och 2. Även om resultaten visar att det är bättre att köra i "Pump + Throttle + Intake" kommer pumpen överbelastas på grund av ett extra tryckfall. Av detta skäl kommer är det nödvändigt att arbeta i "Throttle + Pump + Intake" i framtiden. Eftersom det är nödvändigt att minska insprutningstiden, av detta skäl, är det också viktigt att öka luftflödet. -
A Study of a Variable Compression Ratio and Displacement Mechanism Using Design of Experiments Methodology
A Study of a Variable Compression Ratio and Displacement Mechanism Using Design of Experiments Methodology Shugang Jiang, Michael H. Smith, Masanobu Takekoshi Abstract Due to the ever increasing requirements for engine performance, variable compression ratio and displacement are drawing great interest, since these features provide further degrees of freedom to optimize engine performance for various operating conditions. Different types of mechanisms are used to realize variable compression ratio and displacement. These mechanisms usually involve relatively complicated mechanical design compared with conventional engines. While the flexibility in these mechanisms introduces additional engine design and control possibilities, it also increases the challenges for the development and optimization, since how the geometry of the mechanisms affects the engine performance is not straightforward, and building prototype engines of various mechanical design parameters takes a long time with high cost. This paper presents a study of a multiple-link mechanism that realizes variable compression ratio and displacement by varying the piston motion, specifically the Top Dead Center (TDC) and Bottom Dead Center (BDC) positions relative to the crankshaft. The study focuses on obtaining desirable behavior for both compression ratio and displacement. It is determined a major requirement for the design of the mechanism is that when the control action changes monotonically over its whole range, the compression ratio and displacement should change in opposite directions monotonically. This paper gives an approach on how to achieve multiple-link mechanism designs that fulfill this requirement. First, a condition is obtained on how the TDC and BDC positions should change with respect to the control action to fulfill the design requirement.