DOCSLIB.ORG

A Method of Fuel Testing in a CFR Engine

Total Page：16

File Type：pdf, Size：1020Kb

Download full-text PDF Read full-text
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•••••••••• iii List of Figures•••••••••••••••••••••••••••••a•••••••••••• iv Introduction ••••••••••••••••••••••••••• ~··•••••••••••••••• 1 History••••••••••••••••••••••••••••••••••••••••••••••••••• 3 Survey of Literature•••••••••••••••••••••••••••••••e•••••• 6 Discussion •••••••••••• a•••••••••••••••••••••••••••••••••e• 7 Preparation of the Test Engine•••••••••••••••••••••••• 7 Calibration of Associated Equipnent•••••••••••••••••• 20 Operation and Data Taking•••••••••••••••••••••••••••a 33 Conclusions •••••••••••••••••••••••••••••••••••••••••••••• 53 Bibliography••••••••••••••••••••••••••••••••••••••••••••• 54 Vita••••••••••••••e•••••••••••••••••••••••••••••••••••••• 56 iv LIST OF FIGURES Figure Page l CF R Engine dismantled for cleaning and modification 9 2 Electric dynamometcr and dial scale being used 10 to find engine brake horsepowar. 3 Adjustable metering jet 14 4 Crystal pickup with connecting cable, also 15 amplifier and oscillograph 5 Bottom view of variable compression ratio 17 cylinder with changing device, also carburetor with float bowls and fuel containers 6 Control panel board 18 1 Complete test apparatus and test engine as used 19 in the trials, and test engine in operation 8 Pressure-time diagram for normal combustion, on 21 the osoillograph screen 9 Calibration curve on the oscillograph screen 22 10 Pressure-time diagram for normal combustion 24 11 Pressure-time diagram for detonation 25 12 Pressure-time diagram for preignition 26 13 Compression ratio micrometer and quartz pressure 28 element in place on engine 14 Tilt method of calibrating compression ratio 29 micrO!lleter 15 Spark advance linkage and visual spark advance 30 indicator 16 Variation of spark advance with compression ratio 32 17 Compression ratio vs brake horsepowor for 1ooi 35 alcohol & at benzene by volume 18 Co:npression ratio vs brake horsepower for 901. 36 alcohol & lOt benzene by volume v Figure Page 19 Compression ratio vs brake horsepower for 8()1. 37 alcohol & 20% benzene by volume 20 Compression ratio vs brake horsepower for 701o 38 alcohol & 3C>i benzene by volume 21 Compression ratio vs brake horsepower for 601. 39 alcohol & 4oi benzene by volume 22 Compression ratio vs brake horsepower for soi 40 alcohol & 501, benzene by volume 23 Compression ratio vs brake horsepower for 401. 41 alcohol & soi benzene by volume 24 Compression ratio vs brake horsepower for 30% 42 alcohol & 7010 benzene by volume 25 Compression ratio vs brake horsepower for 201o 43 alcohol & soi benzene by volume 26 Compression ratio vs brake horsepower for 101, 44 alcohol & 9<n. benzene by volume 27 Compression ratio vs brake horsepower for O"Jo 45 alcohol & 10()1. benzene by volume 28 Compression ratio vs brake horsepower for 86 46 octane regular blend gasoline 29 Compression ratio vs brake horsepower for 100 47 octane pure ~ctane 30 Compression ratio vs brake horsepower for l001a 48 alcohol, soi alcohol & 4Di benzene, and 1ooi benzene by volume 31 Mixtures vs maximum brake horsepower 49 32 Fuel weighing device and time mechanism 51 33 Mixtures vs brake specific fuel consumption 52 INTRODUCTION At the present time, only a very small fraction of motor fuels produced for domestic use in the United States contain any alcohol in their blends. Soma foreign markets, notably the Phillipine Islands and South American Countries use high proportions of alcohol in their motor fuel blends. (1) (2) Special purpose fuels in the United States which have alcohol blended with other compounds, have been used for engines from 'Which maximum horsepower output is imperative. An example of this type of motor fuel blend might be found in the competitive motor sports involving motorcycles, stock automotive equipment, and special racing eqnip;o.ent. An extensive survey of literature brought to light the lack of scientific information and ba6ia for proper blending of alcohol blend fuel mixtures. The most apparent info:z:mation in the literature was the lack of any scientific approach to the compounding of these fuels. The author considers that this lack of scientific background is due to the difficulty of providing a satisfactory testing procedure to follow in making such an evaluation. This thesis reports the work involved in (a) preparing a suitable test engine for use in fuel research, (b) calibrating the associated equipment, (c) taking data, and (d) evaluating the resultant data in the light of the,objective of the tests. A standard ASTM-CFR single oylinder fuel research engine was used as the basic engine, with necessary modifications to achieve aa near actual operating conditions as possible and still allow (1) (2) All references are in the bibliography. 2 maximmn control over all tha variablesa These modifications and the reasons for them. are described in detail in the discussion section under ths preparation of the test engine. A piezoelectric crystal pickup was used to determine the cylinder pressures of the angina by electrically amplifying its output and using this output to drive an oscilloscope. The amplifier contained a special pressure evaluating device, and it, along with the pickup were calibrated as described in the discussion under the calibration of associated equipnent. Once the engine was prepared and the associated equipnent calibrated, the taking of data was begun in a relatively straight forward manner. However, since tho data was taken ovar a period of tima but was evaluated all at one time, it was necessary to maintain rigid control over tha variables and the calibrations as the data was taken. The necessary steps and precautions are described in the discussion under the section of operation and data taking. 3 HI5'TORY Experimentation with fuels and engines most certainly took place as soon as the first successful engines were developed. Not until 1919, however, when H. R. Ricardo first developed a semblance of the modern day fuel test enqine, was any scientific approach taken in testing of motor fuels. (3) Ricardo's later test engines, refinements of his first, were the basis for the development of a standard fuel research engine in the United States. (4) In 1928, a group of fuel producers and engine manufacturers who had formed the Cooperative Fuel Research Committee, assigned the problem of developing a test method and oquipnent for knock rating to a Detonation Sub-Committeo in recognition of the interdependence of engine performance upon compression ratio and fuel anti-knock property as first taught by Ricardo. (5) The advent of modern cracking processes disclosed the wide range of anti-knock quality existing in fuels and emphasized the necasoity for a standard fuel test method. The first meeting of the Detonation Sub-Committee disclosed three items essential to tho pursuit of a comprehensive motor fuel research: (1) a standardized engine and accessories; (2) a common reference fuel and/or rating scale; and (3) a uniform testing procedure. By 1931, all three had become realities and the first standardized test method and engine ware put to use. (6) In 1932, after a correlation of laboratory ratings and actual service ratings had been made, the test method was modified and improvements of the standard testing unit and its operating techniquo were made. (7) 4 At this tims the tests were given names, that of •c FR Research Method• for the original test, and that of ~c FR Motor Method• for the improved test. The proved reproducibility of results by the CF R methods compelled its acceptance and recognition as the industry's yardstick for gasoline motor fuel rating, so that in 1936, approval by tha American Society for Testing Materials resulted in its receiving AST M designation D - 357. (8) This desiQnation waa for the second or improved method of fuel testing; later, AST M designation D - 908 was given to the first or Research Method of testing. (9) The CF R ccxmnittee continued the developnent of the knock testing technique with numerous refinellents in equii;;ment and procedure. In 1940, the collmlittea completed the
Load more

Recommended publications
  • 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.
    [Show full text]
  • 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!!!).
    [Show full text]
  • 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.
    [Show full text]
  • 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.
    [Show full text]
  • 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.
    [Show full text]
  • Compression Ratio Effects on Performance, Efficiency, Emissions and Combustion in a Carbureted and PFI Small Engine
    2007-01-3623 Compression Ratio Effects on Performance, Efficiency, Emissions and Combustion in a Carbureted and PFI Small Engine William P. Attard, Steven Konidaris, Ferenc Hamori, Elisa Toulson and Harry C. Watson University of Melbourne Copyright © 2007 SAE International ABSTRACT little information exists on small engines of this scale (~400 cm3), particularly modern four valve, pent roof This paper compares the performance, efficiency, designs. Comparatively, engines found in small emissions and combustion parameters of a prototype 3 passenger vehicles in today’s marketplace are usually two cylinder 430 cm engine which has been tested in a more than twice the cylinder capacity of the test engine. variety of normally aspirated (NA) modes with Hence, whether the previously found performance, compression ratio (CR) variations. Experiments were efficiency and emissions quantitative results due to CR completed using 98-RON pump gasoline with modes variations from larger, lower speed engines hold to small defined by alterations to the induction system, which engines of this scale is questioned. Several important included carburetion and port fuel injection (PFI). differences involving in-cylinder flow, combustion and The results from this paper provide some insight into the frictional/temperature affects may be expected as a CR effects for small NA spark ignition (SI) engines. This result of the reduced bore size and increased engine information provides future direction for the development speed. of smaller engines as engine downsizing grows in Carburetion is explored together with PFI as the majority popularity due to rising oil prices and recent carbon of these small scale engines still operate with the dioxide (CO2) emission regulations.
    [Show full text]
  • The Nature of Heat Release in Gasoline PPCI Engines
    The Nature of Heat Release in Gasoline PPCI Engines The MIT Faculty has made this article openly available. Please share how this access benefits you. Your story matters. Citation Sang, Wenwen, Wai K. Cheng, and Amir Maria. “The Nature of Heat Release in Gasoline PPCI Engines.” SAE Technical Paper Series (April 1, 2014). As Published http://dx.doi.org/10.4271/2014-01-1295 Publisher SAE International Version Author's final manuscript Citable link http://hdl.handle.net/1721.1/98045 Terms of Use Creative Commons Attribution-Noncommercial-Share Alike Detailed Terms http://creativecommons.org/licenses/by-nc-sa/4.0/ 2014-01-1295 The Nature of Heat Release in Gasoline PPCI Engines Author, co-author (Do NOT enter this information. It will be pulled from participant tab in MyTechZone) Affiliation (Do NOT enter this information. It will be pulled from participant tab in MyTechZone) Copyright © 2014 SAE International Abstract such, the combustion phenomena studied here are different from the PPCI work using diesel fuel [5, 6], for which the vaporization and ignition delays are very different; from using The heat release characteristics in terms of the maximum single injection [7], for which the emphasis is not on putting a pressure rise rate (MPRR) and combustion phasing in a pilot fuel over a background nearly homogeneous charge; and partially premixed compression ignition (PPCI) engine are from using dual fuels such as the reactivity controlled studied using a calibration gasoline. Early port fuel injection compression ignition (RCCI) concept [8-10], for which the provides a nearly homogeneous charge, into which a reactivity of the local charge is controlled by using two fuels of secondary fuel pulse is added via direct injection (DI) to different reactivity.
    [Show full text]
  • High Compression Ratio Turbo Gasoline Engine Operation Using Alcohol Enhancement
    High Compression Ratio Turbo Gasoline Engine Operation Using Alcohol Enhancement PI: John B. Heywood Sloan Automotive Laboratory Massachusetts Institute of Technology June 19, 2014 Project ID FT016 This presentation does not contain any proprietary, confidential, or otherwise restricted information Overview Timeline Barriers • Project start date: 9/01/2011 • Barriers addressed • Project end date: 1/15/2015 – Peak thermal efficiency (LDV) (with no-cost extension) > 45% • Percent complete: 77% – Peak fuel efficiency improvement (LDV) > 25% – Emission control fuel penalty Budget < 1% • Total project funding:$1,203,122 – DOE share: $962,497 Partners – Contractor share: $240,625 • Cummins Inc • Funding received in FY13: • Project lead: MIT $168,748 • Funding for FY14: $167,337 2 Relevance/Objectives • Objectives: – To explore and assess the potential for higher efficiency gasoline engines through use of non-petroleum fuel components that remove existing constraints on such engines while meeting future emissions standards – Investigate the benefits of knock-free SI engines through the use of alcohol blending with gasoline – Substantially improve efficiency through raising the compression ratio, increasing boost (in turbocharged engines), and engine downsizing, enabled by knock-resisting properties of alcohols • FY13-14 goals – Experiments and simulations to demonstrate thermal efficiency improvement of > 25% over drive cycle for LDV – Determine means of decreasing use of high octane fuel 3 Approach/Strategy • Approach: Ethanol’s unique properties
    [Show full text]
  • Free-Piston Engine
    Free-Piston Engine Peter Van Blarigan Sandia National Laboratories 2010 DOE Vehicle Technologies Program Annual Merit Review Tuesday, June 8, 2010 Project ID: ACE008 Sponsors: Advanced Combustion Engine R&D and Fuel Technologies Program Managers: Gurpreet Singh and Kevin Stork This presentation does not contain any proprietary, confidential, or otherwise restricted information Overview Timeline Barriers • Project provides fundamental research • Increased thermal efficiency (>50%) that supports DOE/ industry advanced via high compression ratio engine development projects. • Petroleum displacement : multi-fuel • Project directions and continuation are capability via variable compression evaluated annually. ratio (hydrogen, ethanol, biofuels, Budget natural gas, propane) • Project funded by DOE • Reduced emissions: lean, premixed combustion (LTC/HCCI) • FY08: $300K (ACE) • Low cost and durability: port fuel • FY09: $100K (ACE) and $400K (FT) injection, uniflow port scavenging • FY10: $650K (ACE) and $250K (FT) Partners • General Motors/Univ. of Michigan CRL • Ronald Moses (LANL) • Stanford University 2 Relevance Goals of the Free-Piston Engine Research Prototype – Study the effects of continuous operation (i.e. gas exchange) on indicated thermal efficiency and emissions of an opposed free-piston engine utilizing HCCI combustion at high compression ratios (~20-40:1) – Concept validation of passively synchronizing the opposed free pistons via the linear alternators, providing a low cost and durable design – Proof of principle of electronic
    [Show full text]
  • (12) United States Patent (10) Patent No.: US 9,650,951 B2 Cleeves Et Al
    USOO9650951B2 (12) United States Patent (10) Patent No.: US 9,650,951 B2 Cleeves et al. (45) Date of Patent: May 16, 2017 (54) SINGLE PISTON SLEEVE VALVE WITH (56) References Cited OPTIONAL VARIABLE COMPRESSION RATO CAPABILITY U.S. PATENT DOCUMENTS 367,496 A 8, 1887 Atkinson (75) Inventors: James M. Cleeves, Redwood City, CA 12/1913 Anthony (US); Simon David Jackson, Redwood 1,082,004 A City, CA (US); Michael Hawkes, San (Continued) Francisco, CA (US); Michael A. FOREIGN PATENT DOCUMENTS Willcox, Redwood City, CA (US) CN 101427012. A 5, 2009 (73) Assignee: PINNACLE ENGINES, INC., San CN 102135040 A T/2011 Carlos, CA (US) (Continued) (*) Notice: Subject to any disclaimer, the term of this patent is extended or adjusted under 35 OTHER PUBLICATIONS U.S.C. 154(b) by 1315 days. Extended European Search Report issued in European Application (21) Appl. No.: 13/270,200 No. 11831731, mailed Oct. 9, 2014. (Continued) (22) Filed: Oct. 10, 2011 Primary Examiner — Hai Huynh (65) Prior Publication Data Assistant Examiner — Raza Najmuddin (74) Attorney, Agent, or Firm — Mintz Levin Cohn Ferris US 2012/OO8931.6 A1 Apr. 12, 2012 Glovsky and Popeo, P.C. Related U.S. Application Data (57) ABSTRACT (60) Provisional application No. 61/391,525, filed on Oct. 8, 2010, provisional application No. 61/501.462, filed An internal combustion engine can include a piston moving in a cylinder and a junk head disposed opposite the piston (Continued) head in the cylinder. The junk head can optionally be moveable between a higher compression ratio position (51) Int. Cl.
    [Show full text]
  • Partially Premixed Combustion
    Partially Premixed Combustion Arne Andersson Magnus Christensen DEER 2011 Conference High Load Low Temperature Combustion - enabled by introduction of “new” fuels RCCI PPC ´Reactivity Controlled CI´ Partially Premixed Combustion very high ON +very high CN in-between ON/CN i.e. neat ethanol + Diesel i.e. Naphtha or gasoline/diesel IMEP 17 bar w/o EGR reported IMEP 26 bar achieved Low load High load CETANE CETANE OCTANE OCTANE Power density - a prerequisite for downsizing and transport efficiency Volvo Technology Arne Andersson, DEER 2011 PPC use a gasoline type fuel 600 Single injection Prail = 2400bar Prail = 1500bar 500 • BSNOx ~ 0.5g/ Low Cetane 400 ignition delay reduce soot (more premix) 300 increase efficiency (faster heat release) 200 aRoHR [J/CAD] & Pcyl [bar] Low load problems (noise, HC+CO) 100 0 330 340 350 360 370 380 390 400 • High volatility Crank Angle Position [edeg] No wall wetting; Inject anytime! • Low viscosity A lubricity additive needed Volvo Technology Arne Andersson, DEER 2011 CR requirement for ignition HCCI test for PRF blends ignition becomes demanding for ON > 80 CR>17 needed for cold start? Diesel is similar to PRF 30 Port injected PRF0 to PRF100 Volvo Technology Arne Andersson, DEER 2011 Controlling CO and HC at low load uncooled EGR setting: Inlet Manifold Temp raised from 38 to 70 C We must do more at lower loads! Volvo Technology Arne Andersson, DEER 2011 Ways to improve temperature at TDC 50 1200 45 1100 40 1000 35 ε = 15.8 900 30 ε = 17.3 800 25 VVA 50° Pcyl (bar) Pcyl trottle 20 (K) Tcyl 700 hot
    [Show full text]
  • Development of a Two-Stage Variable Compression Ratio Engine
    Development of a Two-stage Variable Compression Ratio Engine ABSTRACT Fuel consumption can be reduced in highly boosted gasoline engines with a Variable Compression Ratio (VCR). The increase in fuel economy is the result of operating an engine with higher compression ratios at low load compared to an engine with fixed compression ratio. The two-stage VCR-system provides a high share of the potential fuel savings in comparison to fully variable system. The two-stage VCR system is proven to be the best concept, considering its low cost to manufacture and the benefit if integration into common engine architectures. The system uses a length-adjustable connecting rod with an eccentric piston pin in the small eye. The compression ratio adjustment is performed through a combination of gas and mass forces. This study outlines the design of the two-stage VCR-system and describes the functional testing that was conducted under motored and fired engine operating conditions. INTRODUCTION MOTIVATION AND POTENTIALS POTENTIAL FOR SI COMBUSTION PROCESSES Variable compression engine benefits have been widely acknowledged and documented [1, 2, 3, 8, 9, and 11]. Under full load conditions, the performance and efficiency of an engine with a compression ratio that is adapted to load demands is capable of reducing knock susceptibility. In addition, the risk of pre-ignition, mega-knocking effects and engine jerking, as the result of retarded combustion phases, can be reduced. The VCR also provides further potential to control the exhaust gas temperature, contributing to protecting component temperatures. The potential for fuel savings under part load conditions is shown in Figure 1.
    [Show full text]