GB2312242A - Variable stroke and compression ratio engine - Google Patents
Variable stroke and compression ratio engine Download PDFInfo
- Publication number
- GB2312242A GB2312242A GB9608185A GB9608185A GB2312242A GB 2312242 A GB2312242 A GB 2312242A GB 9608185 A GB9608185 A GB 9608185A GB 9608185 A GB9608185 A GB 9608185A GB 2312242 A GB2312242 A GB 2312242A
- Authority
- GB
- United Kingdom
- Prior art keywords
- axis
- piston
- engine
- mechanical arrangement
- movement
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Transmission Devices (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
The axis of the pivot 5 of a lever connecting a fixed throw crankshaft to a piston connecting rod 3 is movable axially Y along and perpendicularly X to the lever longitudinal axis.
Description
PATENT APPLICATION SPECIFICATION 1 Subject;
RECIPROCATING PISTON ENGINE MECHANISM 2 Scope;
A mechanism whereby the ratio of the piston stroke of a reciprocating piston engine can be varied from the fixed crankshaft throw.
The ratio can be varied in a continuous manner, from the maximum stroke, which need not be equal to the crankshaft throw, to a zero figure.
Means are also incorporated to maintain / adjust the compression pressures.
3 Introduction;
As applied to the internal combustion engine.
The present design of internal combustion engine has nearly reached its limit in efficiency in its present form. Any significant change in efficiency, must depend on a more radical design approach.
Basic engine design is generally determined by; 3.1 maximum power output - engine capacity - approx. 2% use 3.2 maximum compression ratio - full throttle - approx 3% use 3.3 part load - throttling inlet charge - approx 95% use
Items 3.1 and 3.2 produce maximum engine power / efficiency, and item 3.3 decreases efficiency. This decrease becomes larger as the throttling increases.
Clearly throttling is an extremely inefficient method of engine control, and is employed for the majority of the engine running time.
The decrease in efficiency is caused by the lowering of the achieved Compression Ratio ( CR ) and the increased pumping losses.
The criteria for improvement are therefore; a) avoid throttling or minimise, at part load running conditions b) retain the maximum amount of existing engine design, components and manufacturing equipment
In order to avoid throttling of the inlet charge the engine must be run at full power. To reduce this amount of power to the level required by the vehicle in the lower speed ranges efficiently, the amount of inlet charge must be reduced. This can only be achieved by reducing the engine capacity in a stepless manner ie. piston stroke. Providing the CR can be maintained at the required figure, this is a very effective method, as it allows the engine to operate in a much improved
Specific Fuel Consumption range, with reductions in:a) piston and ring friction b) heat loss to the cylinder wall c) induction and exhaust pumping losses d) exhaust gas quantity as these items are proportional to stroke.
4 DESIGN 4.1 BASIC PRINCIPLE see Fig 1 sheets 1 to 3
The purpose of the following mechanism is to extend the development of the well established existing reciprocating piston engine. The modifications to the layout of cylinder to crankshaft being self explanatory.
By introducing a Rocking Lever with a Movable Pivot such that the length ratio between the pivot and piston, and the pivot and crankshaft, can be varied, we can alter the ratio of the piston stroke to that of the fixed crankshaft throw.
As the Movable Pivot is also located in a Movable Guide
Block, see fig 5, it can be seen that:a) movement of the guide block in the Y AXIS varies the lever length ratios b) movement of the guide block in the X AXIS varies the location of the piston in the cylinder.
4.2 DESIGN VARIATIONS 4.2.1 Piston guided - fig 2; lever fixed in Y AXIS at piston end 4.2.2 Con-rod guided - fig 3; lever fixed in Y AXIS at crank end 4.2.3 Piston and Con-rod guided - fig 4 lever free to move with
Movable Guide Block - weight transfer of lever to
compensate engine balance at reduced strokes 4.2.4 Movable Guide Block - independent X and Y AXIS movement 4.2.5 Movable Guide Block - combined X and Y AXIS movement 4.3 DESIGN DESCRIPTION
Design Variation 4.2.1 and 4.2.5 see Fig 2
ie piston guided and combined X and Y axis movement
The engine arrangement consists of two main elements 4.3.1 Engine block - this represents present day engine technology with the piston / cylinder axis being transferred from the Y AXIS to X AXIS 4.3.2 Lever mechanism - arrangement whereby the the variations to stroke and piston location are carried out.
The following parts / nomenclature being used
1 ROCKING LEVER - with integral / separate guide system
note - fig 4 lever extended for engine
balance purposes
2 MOVABLE PIVOT / HOUSING - figs 2 and 3 - may be
asymmetric weighted to compensate
engine balance at reduced strokes
3 EXTENDED PISTON ROD / GUIDE system
4 CONNECTING ROD
5 MOVABLE GUIDE BLOCK / FULCRUM PIVOT system
6 OPERATING ROD - to connect to engine control system
7 PIVOT GUIDE SHOES - fig 4 only
The arrangement is made up of three separate functions 4.3.3 Piston to crankshaft movement transfer 4.3.4 Piston to crankshaft movement variations 4.3.5 Piston location in cylinder variations 4.3.3 by the introduction of a ROCKING LEVER 1 with a MOVABLE
PIVOT / HOUSING 2 , between a EXTENDED PISTON ROD GUIDE 3 , and the CONNECTING ROD 4 , little end.
Assume the MP/H 2 is at the mid point of RL 1 and fixed. The fixed crank throw movement is transferred via RL 1 into an equal but opposite movement at the piston.
4.3.4 by moving MSH 2 in the Y AXIS along RL 1 the ratio of the arm leverage can be varied from the maximum to zero.
By providing a MOVABLE GUIDE BLOCK / FULCRUM PIVOT 5 in the Y
AXIS , which is controlled by OPERATING ROD 6 , movement of OR 6, moves MGB/FP 5, moves MP/H 2, which varies the arm ratio, and thus, the piston stroke to the fixed crank throw.
4.3.5 if however MGB/FP 5 axis is offset in the X AXIS direction, at the piston end; a) by an amount equal to half the maximum piston stroke, the piston Top Dead Centre location in the cylinder remains unchanged.
b) by a further amount the compression pressure can be maintained / compensated for.
The sum of the two offsets provide the Guide Path line, for
MGB/FP 5.
4.3.6 the above system may be fitted singly; paired; or with shared components, between cylinders; or by any combination thereof.
Claims (5)
- 5 CLAIMS5.1 A mechanical arrangement, which can be incorporated into the basic design of conventional reciprocating piston engines, which enables; a) The piston stroke of a reciprocating piston engine with a fixed crankshaft throw, to be varied in a continuous manner from the maximum stroke, which need not necessary be equal to the crankshaft throw, to zero.b) The piston location in the cylinder to be varied.These movements maybe carried out as separate individual movements or in a combined manner.5.
- 2 As 5.1 with mechanical arrangement such that the ROCKING LEVER 1 is restrained in the Y AXIS by a guided piston rod assembly 5.
- 3 As 5.1 with mechanical arrangement such that the ROCKING LEVER 1 is restrained in the Y AXIS by a guided connecting rod assembly 5.
- 4 As 5.1 + 5.2 and 5.3 with mechanical arrangement such that the ROCKING LEVER 1 is free to move in the Y AXIS with the MOVABLE GUIDE BLOCK / FULCRUM PIVOT 5. GUIDE SHOES 7 being incorporated with the end pivot bearings.
- 5.6 As 5.1 to 5.4 with MGB/FP 5 movement with combined X and Y AXIS control.5.5 As 5.1 to 5.4 with MGB/FP 5 movement with independent control in the X and Y AXIS.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB9608185A GB2312242A (en) | 1996-04-19 | 1996-04-19 | Variable stroke and compression ratio engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB9608185A GB2312242A (en) | 1996-04-19 | 1996-04-19 | Variable stroke and compression ratio engine |
Publications (2)
Publication Number | Publication Date |
---|---|
GB9608185D0 GB9608185D0 (en) | 1996-06-26 |
GB2312242A true GB2312242A (en) | 1997-10-22 |
Family
ID=10792385
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
GB9608185A Withdrawn GB2312242A (en) | 1996-04-19 | 1996-04-19 | Variable stroke and compression ratio engine |
Country Status (1)
Country | Link |
---|---|
GB (1) | GB2312242A (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2004061270A1 (en) * | 2003-01-02 | 2004-07-22 | Scalzo Automotive Research Pty Ltd. | Mechanism for internal combustion piston engines |
FR2910545A1 (en) * | 2006-12-20 | 2008-06-27 | Inst Francais Du Petrole | Internal combustion engine for e.g. diesel engine, has cam follower mounted around articulation axle, displaced in translation along direction and connected to connecting rod and to crankshaft respectively by two ends of follower |
CN100432374C (en) * | 2003-01-02 | 2008-11-12 | 斯卡尔佐汽车研究股份有限公司 | Mechanism for internal combustion piston engines |
JP2012225164A (en) * | 2011-04-15 | 2012-11-15 | Nissan Motor Co Ltd | Double-link type piston-crank mechanism of internal combustion engine |
KR102053100B1 (en) * | 2018-07-24 | 2020-01-07 | 현대오트론 주식회사 | Variable compression ratio devcie |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB228706A (en) * | 1923-11-16 | 1925-02-16 | Percy George Tacchi | Improvements in the driving mechanism of internal combustion engines |
GB346867A (en) * | 1930-10-21 | 1931-04-23 | Arthur Hew Bradford Fanshawe | Improvements in variable stroke driving gear for use with internal combustion and other engines |
US4112826A (en) * | 1977-05-02 | 1978-09-12 | General Motors Corporation | Variable displacement reciprocating piston machine |
US4401010A (en) * | 1980-11-10 | 1983-08-30 | Eddington George D | Variable-torque-accommodating machine |
EP0248655A2 (en) * | 1986-06-04 | 1987-12-09 | The Trustees of Columbia University in the City of New York | Swing beam internal combustion engines |
GB2249131A (en) * | 1990-10-24 | 1992-04-29 | Ford Motor Co | Variable compression ratio i.c. engine |
-
1996
- 1996-04-19 GB GB9608185A patent/GB2312242A/en not_active Withdrawn
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB228706A (en) * | 1923-11-16 | 1925-02-16 | Percy George Tacchi | Improvements in the driving mechanism of internal combustion engines |
GB346867A (en) * | 1930-10-21 | 1931-04-23 | Arthur Hew Bradford Fanshawe | Improvements in variable stroke driving gear for use with internal combustion and other engines |
US4112826A (en) * | 1977-05-02 | 1978-09-12 | General Motors Corporation | Variable displacement reciprocating piston machine |
US4401010A (en) * | 1980-11-10 | 1983-08-30 | Eddington George D | Variable-torque-accommodating machine |
EP0248655A2 (en) * | 1986-06-04 | 1987-12-09 | The Trustees of Columbia University in the City of New York | Swing beam internal combustion engines |
GB2249131A (en) * | 1990-10-24 | 1992-04-29 | Ford Motor Co | Variable compression ratio i.c. engine |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2004061270A1 (en) * | 2003-01-02 | 2004-07-22 | Scalzo Automotive Research Pty Ltd. | Mechanism for internal combustion piston engines |
US7174863B2 (en) | 2003-01-02 | 2007-02-13 | Scalzo Automotive Research Pty Ltd | Mechanism for internal combustion piston engines |
CN100432374C (en) * | 2003-01-02 | 2008-11-12 | 斯卡尔佐汽车研究股份有限公司 | Mechanism for internal combustion piston engines |
FR2910545A1 (en) * | 2006-12-20 | 2008-06-27 | Inst Francais Du Petrole | Internal combustion engine for e.g. diesel engine, has cam follower mounted around articulation axle, displaced in translation along direction and connected to connecting rod and to crankshaft respectively by two ends of follower |
EP1939424A1 (en) * | 2006-12-20 | 2008-07-02 | Ifp | Internal combustion engine with variable swept volume and/or variable compression ratio with a swing follower between the crankshaft and the connecting rod and method for performing such variations |
JP2008175203A (en) * | 2006-12-20 | 2008-07-31 | Ifp | Internal combustion engine of variable swept volume and/or variable compression ratio with shift lever for changing swept volume and/or compression ratio between crankshaft and connecting rod |
US7578266B2 (en) | 2006-12-20 | 2009-08-25 | Institut Francais Du Petrole | Variable displacement and/or variable compression ratio engine |
JP2012225164A (en) * | 2011-04-15 | 2012-11-15 | Nissan Motor Co Ltd | Double-link type piston-crank mechanism of internal combustion engine |
KR102053100B1 (en) * | 2018-07-24 | 2020-01-07 | 현대오트론 주식회사 | Variable compression ratio devcie |
Also Published As
Publication number | Publication date |
---|---|
GB9608185D0 (en) | 1996-06-26 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |