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EP0662192B1 - An internal combustion engine - Google Patents

An internal combustion engine Download PDF

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Publication number
EP0662192B1
EP0662192B1 EP93903738A EP93903738A EP0662192B1 EP 0662192 B1 EP0662192 B1 EP 0662192B1 EP 93903738 A EP93903738 A EP 93903738A EP 93903738 A EP93903738 A EP 93903738A EP 0662192 B1 EP0662192 B1 EP 0662192B1
Authority
EP
European Patent Office
Prior art keywords
working piston
piston
cylindrical space
crankshaft
port
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.)
Expired - Lifetime
Application number
EP93903738A
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German (de)
French (fr)
Other versions
EP0662192A1 (en
Inventor
Kostadin Asenov Goleminov
Kostadin Kostadinov Goleminov
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0662192A1 publication Critical patent/EP0662192A1/en
Application granted granted Critical
Publication of EP0662192B1 publication Critical patent/EP0662192B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
    • F02B33/06—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps
    • F02B33/10—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with the pumping cylinder situated between working cylinder and crankcase, or with the pumping cylinder surrounding working cylinder
    • F02B33/16—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with the pumping cylinder situated between working cylinder and crankcase, or with the pumping cylinder surrounding working cylinder working and pumping pistons having differing movements
    • 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
    • F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F02B75/30—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with one working piston sliding inside another
    • 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
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • 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
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the present invention relates to an internal combustion engine finding application as a piston gasoline or diesel engine with supercharging for all kinds of transportation facilities such as motor vehicles, motor cycles, motor-boats, racing cars, industrial trucks, light-weight aircraft, as well as for water pumps, generators, hand tools, multistage piston compressors and others.
  • An internal combustion engine is known down GB-A-2 149 006 , consisting of a body in its upper hollow part performed as an internal cylindrical space whereas in its lower part is shaped a crankshaft casing with the crankshaft possessing a journal and a connecting rod,the said connecting rod fitted in its lower end to the crankshaft.
  • a compressor piston situated in a lower part of the cylindrical space whereas in an upper part of the cylindrical space is situated the working piston connected through a pipe to the compressor piston.
  • the working piston connected through a pipe to the compressor piston.
  • two horizontal valve plates forming a conduit connected through a throttle valve to the intake port.
  • Both valve plates have respectively an intake and an outlet port, symmetricaly disposed on both sides of the pipe between the pistons.
  • the outlet port from the one valve plate and the intake port from the other valve plate are connected through a conduit and an intermediate chamber to an intake valve in the uppermost part of the cylindrical space.
  • Next to the intake valve is situated an outlet valve whose port is also connected through a conduit.
  • the disadvantages of the known engine are as follows: complicated construction with large overall dimensions leading to great inertia of the moving parts which inertia is partialy balanced; complicated gas-distributing mechanism and valve system, using lamilar (plate) and bevelseated (conical) valves. long and complicated ways of the feeding and the discharging conduits leading to an enhancement of the resistance of the air-fuel mixture and of the exhaust gases accordingly;lower specific power per unit of working volume and weight having in mind that the engine is operating as a four-stroke internal combustion engine; as well as a worsened lubrication of the upper part of the inside cylindrical space and of the working piston.
  • the task of the present invention is the elaboration of an internal combustion engine possessing to a large degree a simplified construction,with reduced over all dimensions, a simplified gas-distribution mechanism using short and direct feeding and discharging ways of conduits, with increased specific power per unit of volume and weight, as well as a normal lubrication of the upper part of the inside cylindrical space and of the working piston.
  • the advantages of the internal combustion engine according to the invention are as follows: it operates as a two-stroke engine with no need for oil to be added into the fuel for lubricating the parts in the internal cylindrical space; there is no need of valve system and gas-distribution mechanism; the engine enables from 3 to 6 times the enhancement of the specific power per unit of volume and weight of the construction; during the pistons operation a counterstroke motion is used offering favourable conditions for relieving the dynamical balancing of the moving parts as well as a straightflow scavenging and charging of the combustion chamber.
  • Figure 1 shows a cross-section of the engine in the upper dead point of the working cylinder.
  • Figure 2 shows a cross-section of the engine while the working cylinder is in a moment of expansion/compression/ of the fuel-air mixture.
  • Figure 3 shows a cross-section of the engine in the B D C.
  • Figure 4 shows a cross-section of the engine illustrating application of intake and exhaust valve.
  • the internal combustion engine consists of an engine block (1) having a hollow cylindrical space therein,said cylindrical space comprising an upper cylinder and a lower cylinder having a larger diameter than the upper cylinder,the lower end of said engine block being shaped into a casing (11) containing a crankshaft (5),said crankshaft carrying the big ends of three conrods (3, 4, 6) on journals spaced along said crankshaft,the two outer conrods (3, 4) being journaled on crankshaft eccentrics (15, 16) which are axially in line with each other,the central conrod (6) being journaled on a crankshaft eccentric (14) diametrically opposite to the other eccentrics (15, 16) with respect to the crankshaft axis, the little ends of the two outer conrods being attached to a hollow working piston (2) having an upper part (13), the outer diameter of which is matched to the upper cilinder, and a lower part (12), the outer diameter of which is matched to lower
  • the engine operates as follows:
  • the working piston (2) of the engine is in the TDC, while the compressor piston (7) is in the BDC and owing to the vacuum created in the inside space of the working piston (2) a suction of fuel-air mixture is produced by the intake port (8) ( or as it is shown on figure 4 by the intake valve (20) ) of the body 1 and by the port (19) (or as it is shown on figure 4 by the port (22)) of the working piston (2).
  • the highly efficient performance of the engine according to the invention is achieved owing to the coordination of a great number of constructive and physical factors such as: the reduced length of the suction track; the absence of useless constructive spaces and the double space resulting from the countersense motion of the working piston (2) and the compressor piston (7), enabling the achievement of an exclusively favourable charging of the engine with the fuel-air mixture.
  • the high-velocity under pressure passing of the fuel-air mixture through the small port (19)(or through the port (22) as it is shown on figure 4 ) of the working piston (2) provokes an additional homogenizing, atomization and evaporation of the mixture.All this allows the achievement of a full economical and ecologicaly pure combustion process.
  • the straight-flow and the vortex-flow motion of the fuel-air mixture enables the complete scavenging of the burnt gases and at the same moment the cooling of the spark plug and its safe contacting with the combustion mixture.
  • the absence of valves, springs, camshafts, the utilisation of the classical two-stroke working principle,the supercharging with the fuel-air mixture as well as the abovementioned advantages which are missing in the known similar engines, enable an extremely high power per litre of displacement and efficiency to be achieved, other conditions such as volume,weight, turbo-compressors, computer control, fuel injection etc. being equal.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

According to its technical elements, kinematics and technology as well as to its construction the internal combustion engine relates to the crankshaft-piston type engines. Its field of application includes the entire usage range of the internal combustion engines but is especially appropriate for racing cars, including these one for Formula One. The characteristic feature is that the engine is a two-stroke one but operates with pure fuel without any addition of oil, whereupon the lubrication is forced as it is with the well known four-stroke engines, and possesses an inherent supercharging which enables to be employed as a gasoline or diesel engine.

Description

  • The present invention relates to an internal combustion engine finding application as a piston gasoline or diesel engine with supercharging for all kinds of transportation facilities such as motor vehicles, motor cycles, motor-boats, racing cars, industrial trucks, light-weight aircraft, as well as for water pumps, generators, hand tools, multistage piston compressors and others.
  • An internal combustion engine is known down GB-A-2 149 006 , consisting of a body in its upper hollow part performed as an internal cylindrical space whereas in its lower part is shaped a crankshaft casing with the crankshaft possessing a journal and a connecting rod,the said connecting rod fitted in its lower end to the crankshaft.
  • To the upper end of the connecting rod is suspended a compressor piston situated in a lower part of the cylindrical space whereas in an upper part of the cylindrical space is situated the working piston connected through a pipe to the compressor piston. In the zone between the compressor and the working pistons are shaped two horizontal valve plates forming a conduit connected through a throttle valve to the intake port.
  • Both valve plates have respectively an intake and an outlet port, symmetricaly disposed on both sides of the pipe between the pistons. The outlet port from the one valve plate and the intake port from the other valve plate are connected through a conduit and an intermediate chamber to an intake valve in the uppermost part of the cylindrical space.Next to the intake valve is situated an outlet valve whose port is also connected through a conduit.
  • The disadvantages of the known engine are as follows: complicated construction with large overall dimensions leading to great inertia of the moving parts which inertia is partialy balanced; complicated gas-distributing mechanism and valve system, using lamilar (plate) and bevelseated (conical) valves. long and complicated ways of the feeding and the discharging conduits leading to an enhancement of the resistance of the air-fuel mixture and of the exhaust gases accordingly;lower specific power per unit of working volume and weight having in mind that the engine is operating as a four-stroke internal combustion engine; as well as a worsened lubrication of the upper part of the inside cylindrical space and of the working piston.
  • The task of the present invention is the elaboration of an internal combustion engine possessing to a large degree a simplified construction,with reduced over all dimensions, a simplified gas-distribution mechanism using short and direct feeding and discharging ways of conduits, with increased specific power per unit of volume and weight, as well as a normal lubrication of the upper part of the inside cylindrical space and of the working piston.
  • This task is achieved with the internal combustion engine according to claim 1.
  • According to a first variant implementation of the engine in conformity with the invention,wherein the transfer port is below the piston rings in the upper end of the working piston and second variant wherein the transfer port is above the piston rings in the upper end of the working piston and the intake port and exhaust port in the engine block are fitted with an intake valve and an exhaust valve respectively.
  • The advantages of the internal combustion engine according to the invention are as follows: it operates as a two-stroke engine with no need for oil to be added into the fuel for lubricating the parts in the internal cylindrical space; there is no need of valve system and gas-distribution mechanism; the engine enables from 3 to 6 times the enhancement of the specific power per unit of volume and weight of the construction; during the pistons operation a counterstroke motion is used offering favourable conditions for relieving the dynamical balancing of the moving parts as well as a straightflow scavenging and charging of the combustion chamber.
  • The invention is explained is more detail refering to the enclosed figures as follows:
  • Figure 1 shows a cross-section of the engine in the upper dead point of the working cylinder.
  • Figure 2 shows a cross-section of the engine while the working cylinder is in a moment of expansion/compression/ of the fuel-air mixture.
  • Figure 3 shows a cross-section of the engine in the B D C.
  • Figure 4 shows a cross-section of the engine illustrating application of intake and exhaust valve.
  • As is shown in Figures 1,2 and 3 the internal combustion engine according to the invention consists of an engine block (1) having a hollow cylindrical space therein,said cylindrical space comprising an upper cylinder and a lower cylinder having a larger diameter than the upper cylinder,the lower end of said engine block being shaped into a casing (11) containing a crankshaft (5),said crankshaft carrying the big ends of three conrods (3, 4, 6) on journals spaced along said crankshaft,the two outer conrods (3, 4) being journaled on crankshaft eccentrics (15, 16) which are axially in line with each other,the central conrod (6) being journaled on a crankshaft eccentric (14) diametrically opposite to the other eccentrics (15, 16) with respect to the crankshaft axis, the little ends of the two outer conrods being attached to a hollow working piston (2) having an upper part (13), the outer diameter of which is matched to the upper cilinder, and a lower part (12), the outer diameter of which is matched to lower cylinder,the upper and lower parts of the working piston having piston rings (17) near their upper ends,the hollow inner space in the working piston (2) comprising an upper inner cylindrical space contained within the upper part of the working piston (13) and a lower inner cylindrical space contained within the lower part of the working piston (12) and a having a diameter greater than the upper inner cylindrical space, said engine block (1) further containing an inlet port (8) in communication with the upper cylinder and an exhaust port (9) and a spark plug (10) in communication with the lower cylinder,said upper part of the working piston (13) having a transfer port (19, 22) adapted to allow the upper inner cylindrical space to communicate with the inlet port (8) at its TDC and the lower cylinder at its BDC,said exhaust port (9) in the engine block (1) being located so as to be uncovered by the upper end of the lower part of the working piston (12) at its BDC,the little end of said central conrod (6)being attached to a compressor piston (7) the outer diameter of which is matched to the lower inner cylindrical space of the working piston (2).As it is shown on figure 4, the port (22) is situated beneath the intake valve (20) and after the exhaust (outlet) port (9) is situated the outlet valve (21).
  • The engine operates as follows:
  • As is shown in figure 1 the working piston (2) of the engine is in the TDC, while the compressor piston (7) is in the BDC and owing to the vacuum created in the inside space of the working piston (2) a suction of fuel-air mixture is produced by the intake port (8) ( or as it is shown on figure 4 by the intake valve (20) ) of the body 1 and by the port (19) (or as it is shown on figure 4 by the port (22)) of the working piston (2). All this fuel-air mixture is compressed as a result of the displacement of the working piston (2) downward to the BDC and the respective displacement of the compressor piston (7) toward the TDC, according to the figure 2.When reaching the BDC by the working piston (2) and the TDC by the compressor piston (7), as it is shown in figure 3, the compressed fuel-air mixture flows through the port (19) (or as it is shown on figure 4 through the port (22)) of the working piston (2) into the space formed between the upper part of the body 1 and the working piston (2) itself.The fuel-air mixture fallen into the combustion chamber of the engine is subjected to compression by the displacement of the working piston (2) toward the TDC and when reaching it according to the figure 1, the mixture is ignited during the working stroke.At the opening of the outlet port (9) according to the figure 3 ( or the valve (21) according to the figure 4 ) by the working piston (2) according to the figure 3, the burned gases flow out through the outlet port (9) and in the next moment the combustion chamber of the engine is filled with the fresh fuel-air mixture entering through the port (19) ( or as it is shown on the figure 4 through the port (22)) of the working piston (2). In this moment is accomplished a straight-flow and a vortex-flow high performance scavenging of the combustion chamber and afterwards the above described working process is cyclicaly, manifold repeated, during the operation of the engine.
  • The highly efficient performance of the engine according to the invention is achieved owing to the coordination of a great number of constructive and physical factors such as: the reduced length of the suction track; the absence of useless constructive spaces and the double space resulting from the countersense motion of the working piston (2) and the compressor piston (7), enabling the achievement of an exclusively favourable charging of the engine with the fuel-air mixture.The high-velocity under pressure passing of the fuel-air mixture through the small port (19)(or through the port (22) as it is shown on figure 4 ) of the working piston (2), provokes an additional homogenizing, atomization and evaporation of the mixture.All this allows the achievement of a full economical and ecologicaly pure combustion process.
  • The straight-flow and the vortex-flow motion of the fuel-air mixture enables the complete scavenging of the burnt gases and at the same moment the cooling of the spark plug and its safe contacting with the combustion mixture. The absence of valves, springs, camshafts, the utilisation of the classical two-stroke working principle,the supercharging with the fuel-air mixture as well as the abovementioned advantages which are missing in the known similar engines, enable an extremely high power per litre of displacement and efficiency to be achieved, other conditions such as volume,weight, turbo-compressors, computer control, fuel injection etc. being equal.
  • The complete mechanical separation of the spaces above the pistons, the intake port 8 and the outlet port (9) of the casing (11) housing the crankshaft (5) and the three conrods (3, 4 and 6) enable the forced lubrication of the engine using the casing (11) charged with oil and the oil pump, unshown on the figures, for lubricating the moving parts as it is done in the classical four-stroke engines.All this enables the increasing of the tightness of the working piston (2) and the compressor piston (7), the noiselessness of the engine and the additional cooling of the working piston (2) by means of the oil which is cooled from the inside by the sucked in fresh fuel-air mixture. The possibility of the engine according to the invention to operate as a two-stroke engine with a pure fuel-air mixture without an obligatory addition of oil creates the conditions for a highly ecological performance at a minimal cost.

Claims (3)

  1. An internal combustion engine comprising ;
    - an engine block (1) having a hollow cylindrical space therein,said cylindrical space comprising an upper cylinder and a lower cylinder having a larger diameter than the upper cylinder,
    - the lower end of said engine block being shaped into a casing (11) containing a crankshaft (5),
    - said crankshaft carring the big ends of three conrods (3, 4, 6) on journals spaced along said crankshaft,
    - the two outer conrods (3, 4) being journaled on crankshaft eccentrics (15, 16) which are axially in line with each other,the central conrod (6) being journaled on a crankshaft eccentric (14) diametrically opposite to the other eccentrics (15, 16) with respect to the crankshaft axis,
    - the little ends of the two outer conrods being attached to a hollow working piston (2) having an upper part (13) , the outer diameter of which is matched to the upper cylinder, and a lower part (12), the outer diameter of which is matched to lower cylinder, the upper and lower parts of the working piston having piston rings (17) near their upper ends,
    - the hollow inner space in the working piston (2) comprising an upper inner cylindrical space contained within the upper part of the working piston (13) and a lower inner cylindrical space contained within the lower part of the working piston (12) and a having a diameter greater than the upper inner cylindrical space,
    - said engine block (1) further containing an inlet port (8) in communication with the upper cylinder and an exhaust port (9) and a spark plug (10) in communication with the lower cylinder,
    - said upper part of the working piston (13) having a transfer port (19, 22) adapted to allow the upper inner cylindrical space to communicate with the inlet port (8) at its TDC and the lower cylinder at its BDC,
    - said exhaust port (9) in the engine block (1) being located so as to be uncovered by the upper end of the lower part of the working piston (12) at its BDC,
    - the little end of said central conrod (6) being attached to a compressor piston (7) the outer diameter of which is matched to the lower inner cylindrical space of the working piston (2).
  2. An internal combustion engine as claimed in claim 1 wherein the transfer port (19) is below the piston rings (17) in the upper end of the working piston (13).
  3. An internal combustion engine as claimed in claim 1 wherein the transfer port (22) is above the piston rings (17) in the upper ehd of the working piston (13) and the intake port (8) and exhaust port (9) in the engine block (1) are fitted with an intake valve (20) and an exhaust valve (21) respectively.
EP93903738A 1992-09-16 1993-01-14 An internal combustion engine Expired - Lifetime EP0662192B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
BG096881A BG60483B2 (en) 1992-09-16 1992-09-16 Internal combustion engine
BG96881/92 1992-09-16
PCT/BG1993/000004 WO1994007012A1 (en) 1992-09-16 1993-01-14 An internal combustion engine

Publications (2)

Publication Number Publication Date
EP0662192A1 EP0662192A1 (en) 1995-07-12
EP0662192B1 true EP0662192B1 (en) 1996-04-17

Family

ID=3924638

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93903738A Expired - Lifetime EP0662192B1 (en) 1992-09-16 1993-01-14 An internal combustion engine

Country Status (5)

Country Link
EP (1) EP0662192B1 (en)
AU (1) AU3487793A (en)
BG (1) BG60483B2 (en)
DE (1) DE69302283T2 (en)
WO (1) WO1994007012A1 (en)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5509382A (en) * 1995-05-17 1996-04-23 Noland; Ronald D. Tandem-differential-piston cursive-constant-volume internal-combustion engine
RU2291309C2 (en) * 2004-12-06 2007-01-10 Дмитрий Петрович Титов Two-stroke internal combustion engine without crankcase displacement scavenging
RU2310080C2 (en) * 2005-12-20 2007-11-10 Дмитрий Петрович Титов Four-stroke internal combustion engine with forced scavenging
RU2334884C2 (en) * 2006-02-08 2008-09-27 Баканев Альберт Георгиевич Diesel engine "backan"
FR2904042A1 (en) * 2006-07-21 2008-01-25 Peugeot Citroen Automobiles Sa Internal combustion engine e.g. diesel engine, has piston breaking down into internal and external pistons, which are connected to crank pin, where crank pin is provided under form of two sections parallel to each other and are off-centered
EE01274U1 (en) * 2013-05-17 2014-12-15 Georgi Vassiljev Two-stroke engine with a port-type gas distribution and crankcase scavenging
CN106030036B (en) * 2013-10-17 2019-03-05 考克斯传动有限公司 internal combustion engine
CN104005847B (en) * 2014-05-04 2017-04-26 何学文 Crankshaft connecting rod piston internal combustion engine with combustion chamber arranged in piston
CN110159424A (en) * 2019-05-24 2019-08-23 梁刚 A kind of direct current layered scavenging two-stroke engine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR525585A (en) * 1919-06-02 1921-09-24 Donald Scott Improvements to internal combustion engines
FR634984A (en) * 1926-09-28 1928-03-03 Ignition device for internal combustion and internal combustion engines
GB562964A (en) * 1943-01-15 1944-07-24 William Quilter Improvements in two-stroke internal combustion engines
WO1986004112A1 (en) * 1985-01-02 1986-07-17 Wone Adrian J Internal combustion engine gas transfer system

Also Published As

Publication number Publication date
DE69302283T2 (en) 1996-08-29
BG60483B2 (en) 1995-05-31
AU3487793A (en) 1994-04-12
EP0662192A1 (en) 1995-07-12
WO1994007012A1 (en) 1994-03-31
DE69302283D1 (en) 1996-05-23

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