High Efficiency VCR Engine with Variable Valve Actuation and New Supercharging Technology
Total Page:16
File Type:pdf, Size:1020Kb
Load more
Recommended publications
-
Executive Order D-425-50 Toyota Racing Development
State of California AIR RESOURCES BOARD EXECUTIVE ORDER D—425—50 Relating to Exemptions Under Section 27156 of the California Vehicle Code Toyota Racing Development TRD Supercharger System Pursuant to the authority vested in the Air Resources Board by Section 27156 of the Vehicle Code; and Pursuant to the authority vested in the undersigned by Section 39515 and Section 39516 of the Health and Safety Code and Executive Order G—14—012; IT IS ORDERED AND RESOLVED: That the installation of the TRD Supercharger System, manufactured and marketed by Toyota Racing Development, 19001 South Western Avenue, Torrance, California, has been found not to reduce the effectiveness of the applicable vehicle pollution control systems and, therefore, is exempt from the prohibitions of Section 27156 of the Vehicle Code for the following Toyota truck applications: Part No. Model Year Engine Disp. Model PTR29—34070 2007 to 2013 5.7L (3UR—FE) Tundra PTR29—00140 2014 to 2015 5.7L (3UR—FE) Tundra PTR29—34070 2008 to 2013 5.7L (3UR—FE) Sequoia PTR29—00140 2014 to 2015 5.7L (3UR—FE) Sequoia PTR29—60140 2008 to 2015 5.7L (3UR—FE) Land Cruiser/LX570 PTR29—35090 2005 to 2015 4.0L (1GR—FE) Tacoma PTR29—35090 2007 to 2009 4.0L (1GR—FE) FJ Cruiser PTR29—35090 2003 to 2009 4.0L (1GR—FE) 4—Runner PTR29—00130 2010 to 2014 4.0L (1GR—FE) FJ Cruiser PTR29—00130 2010 to 2015 4.0L (1GR—FE) 4—Runner The 5.7L Supercharger System includes a Magnuson supercharger (rated at a maximum boost of 8.5 psi.) with a 2.45 inch diameter supercharger pulley and the stock crankshaft pulley, high flow injectors to replace the stock injectors, a new ECU calibration, intercooler, intake manifold, an air bypass valve, and a new replacement fuel pump which is located in the fuel tank. -
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•••••••••• -
Poppet Valve
POPPET VALVE A poppet valve is a valve consisting of a hole, usually round or oval, and a tapered plug, usually a disk shape on the end of a shaft also called a valve stem. The shaft guides the plug portion by sliding through a valve guide. In most applications a pressure differential helps to seal the valve and in some applications also open it. Other types Presta and Schrader valves used on tires are examples of poppet valves. The Presta valve has no spring and relies on a pressure differential for opening and closing while being inflated. Uses Poppet valves are used in most piston engines to open and close the intake and exhaust ports. Poppet valves are also used in many industrial process from controlling the flow of rocket fuel to controlling the flow of milk[[1]]. The poppet valve was also used in a limited fashion in steam engines, particularly steam locomotives. Most steam locomotives used slide valves or piston valves, but these designs, although mechanically simpler and very rugged, were significantly less efficient than the poppet valve. A number of designs of locomotive poppet valve system were tried, the most popular being the Italian Caprotti valve gear[[2]], the British Caprotti valve gear[[3]] (an improvement of the Italian one), the German Lentz rotary-cam valve gear, and two American versions by Franklin, their oscillating-cam valve gear and rotary-cam valve gear. They were used with some success, but they were less ruggedly reliable than traditional valve gear and did not see widespread adoption. In internal combustion engine poppet valve The valve is usually a flat disk of metal with a long rod known as the valve stem out one end. -
Ignition System on the ZX750E
CD Ignition Interface for ZX750E1 Page 1 of 8 How to use an aftermarket CD (Capacitive Discharge) ignition system on the ZX750E. Art MacCarley Nipomo, California, USA February 2010. Background If you are only interested in the solution, not the background and explanation, please jump to the last section of this posting. While aftermarket electronic ignition systems and upgraded ignition coils are commonly used on the ZX750E, I could not find any case in which a Capacitive Discharge Ignition (CDI) system was used while retaining the stock ECU (Electronic Control Unit). With apologies to the experts on this forum that probably know everything I discuss below, this is for the benefit of those that, like myself, that had to figure it all out experimentally and come up with a solution. My personal motivation to use an ultimate ignition system was my conversion to methanol, which misfires and runs rough until fully warmed up. The higher energy output and multi-fire features of a CD system could possibly improve this. A typical inductive ignition system delivers about 100 mJ per spark, and electronic “points” and improved coils alone can only marginally improve upon this. A CD system can deliver theoretically much greater ignition energy, limited only by the size of the discharge capacitor, the charging voltage, and ultimately the internal breakdown voltage of the ignition coil. The output of the ARC-II is specified as 189mJ using a 500V charge voltage. My experience is based upon using the Dynatek Arc-II CD ignition system on my 1984 ZX-750E1. This CDI is advertised as having “the highest spark energy of any CDI on the market”. -
Lawn-Boy V-Engine Service Manual
LAWN-BOY V-ENGINE SERVICE MANUAL Table of Contents – Page 1 of 2 REFERENCE SECTION SAFETY SPECIFICATIONS - ENGINE SPECIFICATIONS SPECIFICATIONS - ENGINE FASTENER TORQUE REQUIREMENTS SPECIFICATIONS - CARBURETOR SPECIFICATIONS (WALBRO LMR-16) SPECIAL TOOL REQUIREMENTS TROUBLESHOOTING MAINTENANCE SECTION 1 WALBRO LMR-16 CARBURETOR LMR-16 CARBURETOR - IDENTIFICATION LMR-16 CARBURETOR - THEORY OF OPERATION LMR-16 CARBURETOR - GOVERNOR THEORY LMR-16 CARBURETOR - REMOVAL LMR-16 CARBURETOR - DISASSEMBLY LMR-16 CARBURETOR - CLEANING AND INSPECTION LMR-16 CARBURETOR - ASSEMBLY LMR-16 CARBURETOR - PRESETTING THE GOVERNOR LMR-16 CARBURETOR - ASSEMBLING AIR BOX TO CARBURETOR LMR-16 CARBURETOR - INSTALLATION LMR-16 CARBURETOR - FINAL CHECK LMR-16 CARBURETOR - CHOKE ADJUSTMENT LMR-16 CARBURETOR - SERVICING THE AIR FILTER LMR-16 CARBURETOR-TROUBLESHOOTING SECTION 2 PRIMER START CARBURETOR PRIMER START CARBURETOR - IDENTIFICATION PRIMER START CARBURETOR - THEORY OF OPERATION PRIMER START CARBURETOR - GOVERNOR THEORY PRIMER START CARBURETOR - REMOVAL PRIMER START CARBURETOR - DISASSEMBLY PRIMER START CARBURETOR - CLEANING AND INSPECTION PRIMER START CARBURETOR - ASSEMBLY PRIMER START CARBURETOR - INSTALLATION PRIMER START CARBURETOR - PRESETTING THE GOVERNOR PRIMER START CARBURETOR - FINAL CHECK PRIMER START CARBURETOR - SERVICING THE AIR FILTER PRIMER START CARBURETOR TROUBLESHOOTING ENGINE STARTS HARD ENGINE RUNS RICH ENGINE RUNS LEAN FUEL LEAKS FROM CARBURETOR LAWN-BOY V-ENGINE SERVICE MANUAL Table of Contents – Page 2 of 2 SECTION 3 FUEL SYSTEM FUEL -
Wärtsilä 32 PRODUCT GUIDE © Copyright by WÄRTSILÄ FINLAND OY
Wärtsilä 32 PRODUCT GUIDE © Copyright by WÄRTSILÄ FINLAND OY COPYRIGHT © 2021 by WÄRTSILÄ FINLAND OY All rights reserved. No part of this booklet may be reproduced or copied in any form or by any means (electronic, mechanical, graphic, photocopying, recording, taping or other information retrieval systems) without the prior written permission of the copyright owner. THIS PUBLICATION IS DESIGNED TO PROVIDE AN ACCURATE AND AUTHORITATIVE INFORMATION WITH REGARD TO THE SUBJECT-MATTER COVERED AS WAS AVAILABLE AT THE TIME OF PRINTING. HOWEVER, THE PUBLICATION DEALS WITH COMPLICATED TECHNICAL MATTERS SUITED ONLY FOR SPECIALISTS IN THE AREA, AND THE DESIGN OF THE SUBJECT-PRODUCTS IS SUBJECT TO REGULAR IMPROVEMENTS, MODIFICATIONS AND CHANGES. CONSEQUENTLY, THE PUBLISHER AND COPYRIGHT OWNER OF THIS PUBLICATION CAN NOT ACCEPT ANY RESPONSIBILITY OR LIABILITY FOR ANY EVENTUAL ERRORS OR OMISSIONS IN THIS BOOKLET OR FOR DISCREPANCIES ARISING FROM THE FEATURES OF ANY ACTUAL ITEM IN THE RESPECTIVE PRODUCT BEING DIFFERENT FROM THOSE SHOWN IN THIS PUBLICATION. THE PUBLISHER AND COPYRIGHT OWNER SHALL UNDER NO CIRCUMSTANCES BE HELD LIABLE FOR ANY FINANCIAL CONSEQUENTIAL DAMAGES OR OTHER LOSS, OR ANY OTHER DAMAGE OR INJURY, SUFFERED BY ANY PARTY MAKING USE OF THIS PUBLICATION OR THE INFORMATION CONTAINED HEREIN. Wärtsilä 32 Product Guide Introduction Introduction This Product Guide provides data and system proposals for the early design phase of marine engine installations. For contracted projects specific instructions for planning the installation are always delivered. Any data and information herein is subject to revision without notice. This 1/2021 issue replaces all previous issues of the Wärtsilä 32 Project Guides. Issue Published Updates 1/2021 15.03.2021 Technical data updated. -
MGA Supercharger System Installation Instructions for 1955 to 1962 MGA
MGA Supercharger System Installation Instructions For 1955 to 1962 MGA PART # 150-040 440 Rutherford St. P.O. Box 847 Goleta, CA 93117 1-800-667-7872 • FAX 805-692-2525 • www.mossmotors.com Please read and understand these valve between the barbed fitting and the instructions completely before you brake booster (closer to the booster) with begin the installation. the check valve arrow pointing toward the supercharger manifold. A few notes before you begin: Hose clamps: Re-use hose clamps, or Engine condition - Your car should have purchase new ones where necessary. Use a fresh tune up, including new spark plug new hose clamps on all fuel connections. wires, points, and a new distributor cap and rotor. Spark plugs are included in the If you have installed vacuum boosted supercharger system. brakes - you MUST install a check valve (Moss Part # 150-071) in the vacuum How superchargers work — line. This will prevent pressurized air from Superchargers compress the air/fuel mix- reaching the brake booster system and ture, filling cylinders with a greater charge damaging it. To install, remove the larger than when normally aspirated. Normally of the 3 plugs in the back of the super- aspirated engines produce vacuum, read charger manifold and install a barbed in inches of mercury, superchargers and fitting using teflon tape on the threads. turbochargers produce boost, read in posi- Using 3/8 in vacuum line, install the check tive pounds per square inch. 150-040 -1- Revised 1/11 Installation Instructions Boost capacity is determined by supercharger rod, jet, and slide have been altered to run prop- RPM which is, of course, affected by pulley size erly and safely on a wide range of supercharged, (the smaller the supercharger pulley, the faster unmodified engines. -
And Heavy-Duty Truck Fuel Efficiency Technology Study – Report #2
DOT HS 812 194 February 2016 Commercial Medium- and Heavy-Duty Truck Fuel Efficiency Technology Study – Report #2 This publication is distributed by the U.S. Department of Transportation, National Highway Traffic Safety Administration, in the interest of information exchange. The opinions, findings and conclusions expressed in this publication are those of the author and not necessarily those of the Department of Transportation or the National Highway Traffic Safety Administration. The United States Government assumes no liability for its content or use thereof. If trade or manufacturers’ names or products are mentioned, it is because they are considered essential to the object of the publication and should not be construed as an endorsement. The United States Government does not endorse products or manufacturers. Suggested APA Format Citation: Reinhart, T. E. (2016, February). Commercial medium- and heavy-duty truck fuel efficiency technology study – Report #2. (Report No. DOT HS 812 194). Washington, DC: National Highway Traffic Safety Administration. TECHNICAL REPORT DOCUMENTATION PAGE 1. Report No. 2. Government Accession No. 3. Recipient's Catalog No. DOT HS 812 194 4. Title and Subtitle 5. Report Date Commercial Medium- and Heavy-Duty Truck Fuel Efficiency February 2016 Technology Study – Report #2 6. Performing Organization Code 7. Author(s) 8. Performing Organization Report No. Thomas E. Reinhart, Institute Engineer SwRI Project No. 03.17869 9. Performing Organization Name and Address 10. Work Unit No. (TRAIS) Southwest Research Institute 6220 Culebra Rd. 11. Contract or Grant No. San Antonio, TX 78238 GS-23F-0006M/DTNH22- 12-F-00428 12. Sponsoring Agency Name and Address 13. -
HSDI Diesel Engines - Gas Exchange Optimization and the Impact on Reducing Emission
HSDI Diesel Engines - Gas Exchange Optimization and the Impact on Reducing Emission ABSTRACT All future powertrain developments must consider the primary tasks of achieving the required emission levels and CO2- values, while still providing comfort, good drivability, high reliability and affordable costs. One method for improving fuel economy in passenger vehicles that is beginning to be examined is the incorporation of downsizing. To achieve the levels of engine performance that will be required, increasing the boost pressure and/or rated speed is mandatory. When the boost pressure or the rated speed is increased, the result is an increase in the mass flow rate through the intake and exhaust ports and valves. Considering the impact of these changes, the port layout of the system has to be reanalyzed. The primary purpose of this study is to examine these effects on the port layout on a modern diesel combustion system and to present a promising concept. The study included flow measurements, PIV measurements of intake flow, CFD simulations of the flow field during intake and results from the thermodynamic test bench. One of the key aspects that needed to be examined was to demonstrate flow quality’s impact on combustion. A new port concept was developed as a result of this study that utilizes a variable valve lift to provide a highly variable swirl. This design enables a homogenous flow field in the cylinder, with excellent flow coefficient. The design also allows an increase in volumetric efficiency combined with a reduction in flow losses. INTRODUCTION The prerequisites for advanced concepts of High Speed Direct Injection (HSDI) Diesel Engines require that due to the rapidly increasing price of crude oil they must improve fuel economy and the heat-trapping ability of carbon dioxide emissions. -
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. -
Review of Advancement in Variable Valve Actuation of Internal Combustion Engines
applied sciences Review Review of Advancement in Variable Valve Actuation of Internal Combustion Engines Zheng Lou 1,* and Guoming Zhu 2 1 LGD Technology, LLC, 11200 Fellows Creek Drive, Plymouth, MI 48170, USA 2 Mechanical Engineering, Michigan State University, East Lansing, MI 48824, USA; [email protected] * Correspondence: [email protected] Received: 16 December 2019; Accepted: 22 January 2020; Published: 11 February 2020 Abstract: The increasing concerns of air pollution and energy usage led to the electrification of the vehicle powertrain system in recent years. On the other hand, internal combustion engines were the dominant vehicle power source for more than a century, and they will continue to be used in most vehicles for decades to come; thus, it is necessary to employ advanced technologies to replace traditional mechanical systems with mechatronic systems to meet the ever-increasing demand of continuously improving engine efficiency with reduced emissions, where engine intake and the exhaust valve system represent key subsystems that affect the engine combustion efficiency and emissions. This paper reviews variable engine valve systems, including hydraulic and electrical variable valve timing systems, hydraulic multistep lift systems, continuously variable lift and timing valve systems, lost-motion systems, and electro-magnetic, electro-hydraulic, and electro-pneumatic variable valve actuation systems. Keywords: engine valve systems; continuously variable valve systems; engine valve system control; combustion optimization 1. Introduction With growing concerns on energy security and global warming, there are global efforts to develop more efficient vehicles with lower regulated emissions, including hybrid electrical vehicles, electrical vehicles, and fuel cell vehicles. Hybrid electrical vehicles became a significant part of vehicle production because of their overall efficiency, and they still pose a significant cost penalty, resulting in a stagnant market penetration of 3.2% and 2.7% in 2013 and 2018, respectively, in the United States (US), for example [1]. -
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!!!).