EP0475947A1 - Moteur a combustion interne - Google Patents
Moteur a combustion interneInfo
- Publication number
- EP0475947A1 EP0475947A1 EP90905168A EP90905168A EP0475947A1 EP 0475947 A1 EP0475947 A1 EP 0475947A1 EP 90905168 A EP90905168 A EP 90905168A EP 90905168 A EP90905168 A EP 90905168A EP 0475947 A1 EP0475947 A1 EP 0475947A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- chamber
- piston
- pumping
- cylinder
- valve
- 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- Withdrawn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
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/14—Engines characterised by using fresh charge for scavenging cylinders using reverse-flow scavenging, e.g. with both outlet and inlet ports arranged near bottom of piston stroke
- F02B25/145—Engines characterised by using fresh charge for scavenging cylinders using reverse-flow scavenging, e.g. with both outlet and inlet ports arranged near bottom of piston stroke with intake and exhaust valves exclusively in the cylinder head
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L11/00—Valve arrangements in working piston or piston-rod
- F01L11/02—Valve arrangements in working piston or piston-rod in piston
-
- 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
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
-
- 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
- F02B33/14—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 forming stepped piston
-
- 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
- F02B33/44—Passages conducting the charge from the pump to the engine inlet, e.g. reservoirs
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/107—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive pneumatic drive, e.g. crankcase pressure drive
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
- F04B19/003—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 free-piston type pumps
Definitions
- THIS INVENTION relates to an internal combustion engine.
- the invention has been devised particularly, although not solely, for use as an internal combustion engine operating on a two-stroke cycle.
- the present invention when applied as a two-stroke engine seeks to provide an engine having an improved process of clearing combustion products from the combustion chamber in comparison to the common arrangement described hereinbefore.
- the invention resides in an internal combustion engine comprising a cylinder and a piston mounted for reciprocation in the cylinder, the piston and the cylinder co-operating to define a combustion chamber and a pumping chamber each of which varies in volume upon reciprocation .of the piston in the cylinder, an inlet means to admit fluid into the pumping chamber, a transfer chamber defined within the piston for receiving and containing fluid from the pumping chamber, and a control means for controlling discharge of the fluid from the transfer chamber into the combustion chamber.
- the piston includes a transfer passage controlled by a non-return valve to allow delivery of fluid from the pumping chamber to the transfer chamber upon volume reduction of the pumping chamber.
- the control means may be of any suitable form such as a discharge passage including a discharge port opening onto the combustion chamber and a valve means for controlling flow through the discharge passage.
- the valve means may comprise a self-acting valve or valve operable under external control to open and close the discharge port. Where the valve is self-acting valve, it may for example be arranged to operate in response to a predetermined difference in pressure between the combustion and transfer chambers. Where the valve is operable under external control, a control mechanism may for example be provided to operate the valve according to the relative position of the piston in the cylinder.
- a control mechanism may comprise a push-rod for operating the valve, the push rod being operatively connected to a cam on a crankshaft to which the piston is operatively connected.
- the cylinder comprises two cylinder portions being a cylinder working portion and a cylinder pumping portion, the cylinder pumping portion being larger in cross- sectional area than the cylinder working portion, the cylinder working portion having a wall at one of its ends and opening onto the cylinder pumping portion at the other of its ends, and a further wall interconnecting the adjacent ends of the cylinder working and pumping portions;
- the piston comprises a piston working portion and a piston pumping portion, the piston working portion being received in the cylinder working portion and the piston pumping portion being received in the cylinder pumping portion;
- the pumping chamber is of annular configuration, the outer circumferential wall of the annular pumping chamber being defined by the circumferential wall of the cylinder pumping portion and the inner circumferential wall of the annular pumping chamber being defined the circumferential wall of the piston working portion.
- a charge of air introduced into the combustion chamber from the transfer chamber in the piston performs a scavenging function in the combustion chamber.
- a combustible mixture may be introduced into the combustion chamber by any suitable arrangement such as an inlet port successively opened and closed by a valve.
- the products of combustion can be exhausted by way of an exhaust port also successively opened and closed by valve.
- a stratified charge can be created in the combustion chamber by introducing a fuel-rich combustible mixture into the chamber through the inlet port.
- the fuel-rich mixture combines with the air introduced via the transfer chamber in the piston to create a combustible mixture which is fuel-rich in the vicinity of ignition means at the time of ignition.
- inlet and exhaust ports may be opened and closed by the piston.
- a combustible mixture may be introduced into the combustion chamber from the transfer chamber .
- This combustible mixture may be the sole combustible mixture in the combustion chamber or may be supplemented either by an additional mixture introduced into the chamber by way of an inlet port or by injected fuel.
- the invention has been devised particularly for use as a two-stroke engine, it may be applied as a four- stroke engine. Where the invention is applied as a four- stroke engine, a charge of combustible mixture or at least air for combustion may be introduced into the combustion chamber from the pumping chamber via the transfer chamber in the piston.
- Fig. 1 is a sectional view of an engine according to a first embodiment
- Fig. 2 is a schematic plan view of the engine of
- Fig. 3 to 7 are a series of schematic sectional views illustrating the operational sequence of the engine
- Fig. 8 to 11 are a series of schematic sectional views illustrating the operational sequence of an engine according to a second embodiment.
- Fig. 12 is a schematic sectional view of part of an engine according to a third embodiment.
- FIG. 1 to 7 of the drawings The embodiment shown in Figs 1 to 7 of the drawings is directed to an international combustion engine comprising a housing 1 having a block portion 3, a head portion 5 and a removable cover 7 defining a space 9.
- a plurality of cylinders 11 are defined within the housing and each has a piston 13 mounted for reciprocation in it.
- Each piston 13 is operatively connected to a drive shaft 15 by way of a rigid connecting rod 17 and a swash plate 18.
- the connecting rod 17 is fixed at one end to the piston ajid is provided with a foot 19 at the other end.
- the foot 19 is received in a shoe 20 on the swash plate.
- the cylinder 11 is of stepped configuration so as to comprise two portions, being a cylinder working portion 21 and a cylinder pumping portion 22.
- the cylinder pumping portion 22 is of larger cross-sectional area than the cylinder working portion 21, as shown in the drawings.
- the cylinder working portion 21 has a wall 23 at one of its ends and the two cylinder portions open onto each other at the other end of the cylinder working portion. Where the two cylinder portions open onto each other they are interconnected by a further wall 25 which provides a step in the cylinder 11.
- the piston 13 is also of stepped configuration so as to comprise two portions being a piston working portion 31 and a piston pumping portion 32.
- the piston working portion 31 is received in the cylinder working portion 21 and the piston pumping portion 32 is received in the cylinder pumping portion 22.
- the combustion chamber 35 is defined by the piston working portion 31 and the cylinder working portion 21 in co ⁇ operation.
- An annular pumping chamber 37 is defined by said further wall 25, the cylinder pumping portion 22 and the piston working and pumping portions in co-operation.
- the combustion chamber 35 and the pumping chamber 37 vary in volume as the piston 13 undergoes reciprocation in the cylinder 11.
- An inlet means 41 is provided to admit air into the pumping chamber 37 as it undergoes an expansion in volume.
- the inlet means 41 includes an inlet duct 43 opening into the pumping chamber and a valve 45 associated with inlet duct and operable to permit air to flow along the inlet duct into the pumping chamber upon expansion of the pumping chamber while preventing return flow upon volume reduction of the pumping chamber.
- a transfer system 44 is provided for selectively transferring air from the pumping chamber 37 to the combustion chamber 35.
- the transfer system 44 comprises a transfer chamber 47 within the piston 13 to receive air under pressure from the pumping chamber 37 as the latter undergoes a reduction in volume and to contain such air.
- the transfer chamber 47 receives air from the pumping chamber by way of a plurality of transfer passages 49 formed within the piston 11.
- Each transfer passage is in the form of a bore extending through the piston, one end of the bore opening onto the pumping chamber 37 and the other end opening onto the transfer chamber 47 within the piston.
- a one-way vale 50 is provided in association with the transfer passages 49 for permitting air to flow along the transfer passages from the pumping chamber to the transfer chamber while preventing return flow.
- the one ⁇ way valve 50 comprises a valve member 51 movable into and out of engagement with a valve seat 52 defined within the transfer chamber and closely adjacent the transfer passages 49.
- the valve member 51 is urged into sealing engagement with the valve seat under the influence of a valve spring 53.
- the valve member 51 is arranged to be deflected out of engagement with the valve seat 52 under the influence of air pressure generated upon compression of the pumping chamber 37 so as to permit air flow from the pumping chamber to the transfer chamber.
- the valve member returns into sealing engagement with the valve seat upon termination of the air flow thereby to prevent return flow.
- a control means 54 is provided for controlling discharge of air form within the transfer chamber 47 to the combustion chamber 35.
- the control means 54 comprises a plurality of discharge passages 55 formed in the piston and terminating at a discharge port 57 opening onto the combustion chamber.
- the control means 53 further comprises a discharge valve 59 for opening and closing the discharge port.
- the valve 59 is a self-acting valve which opens and closes according to a predetermined pressure difference between the transfer chamber and the combustion chamber.
- a spring means (not shown) may be provided for biassing the discharge valve 59 into the position in which it closes the discharge port 57.
- Air introduced into the combustion chamber 35 from the pumping chamber 37 serves a scavenging function and may also be used for combustion purposes, as will be explained later.
- a combustible mixture which is rich in fuel is introduced into the combustion chamber by means of a delivery system 61 including an inlet port 63 which is opened and closed in timed sequence by a valve 65 operated by a cam 66 mounted on the drive shaft within space 9.
- a delivery system 61 further includes a delivery pump 63 operable pneumatically under the influence of the pumping chamber 37.
- the delivery pump 63 comprises a delivery cylinder 65 and a delivery piston 67 mounted for reciprocatory movement along the cylinder.
- the piston comprises a piston head 69 and a piston rod 71.
- the piston head 69 divides the cylinder 65 into an intake chamber 73 and a delivery chamber 75.
- the delivery piston 67 is formed with a plurality of axial passages 77 each controlled by a non-return valve 79 to allow the passage of a fuel-rich mixture from the intake chamber 73 to the delivery chamber 75, as will be explained later.
- the delivery chamber 75 communicates with the inlet port 63 by way of a delivery passage 76.
- a one-way valve 74 is provided in the delivery passage.
- An inlet means 77 including an inlet passage 78 is provided for introducing the fuel-rich mixture into the intake chamber 73.
- Non-return valves 80 are provided to prevent return flow.
- the delivery piston 67 is movable along the cylinder in response to differences in fluid pressure acting on the piston.
- the piston rod 71 is slidably supported and guided by guide means 80.
- the guide means 80 define a conduit 81 which opens onto the pumping chamber 37 so as to expose the delivery piston 67 to fluid pressure in the pumping chamber.
- fluid pressure developed in the pumping chamber upon volume reduction of that chamber acts on the delivery piston to influence it to move along the delivery cylinder 65 so as to cause volume reduction of the delivery chamber 75 in order to compress the fuel-rich mixture contained therein.
- Reversal of the pressure differential on the delivery piston following volume expansion of the pumping chamber influences the delivery piston to move in the reverse direction so as to cause volume expansion of the delivery chamber 75 and volume reduction of the intake chamber 73.
- fuel-rich mixture contained therein flows through the axial passages 77 in the piston head 69 and into the delivery chamber 75.
- the valves 79 prevent return flow on subsequent volume reduction of the delivery chamber.
- Fig. 3 the piston 13 has completed its descent in the cylinder 11 and is shown at its bottom dead centre position.
- the pumping chamber 37 has expanded to its maximum volume condition.
- the valve 45 opened and air was induced into the pumping chamber through the inlet port 43.
- fluid pressure acting on delivery piston 67 causes it to move along the delivery cylinder to effect volume reduction of the intake chamber 73. This has the effect of causing a quantity of fuel- rich mixture which was previously admitted into the intake chamber 73 to be transferred into the delivery chamber.
- the piston 13 commences to ascend in the cylinder thereby causing the pumping and combustion chambers to each undergo a progressive reduction in volume, as shown in Fig. 4.
- the progressive reduction in volume of the pumping chamber causes air contained therein to be forced under pressure along the transfer passages 49 into the transfer chamber 47.
- the air accumulates in the transfer chamber because at this stage the combustion chamber is undergoing a compression stroke and fluid pressure within the combustion chamber prevents the discharge valve 59 from opening.
- the progressive reduction of the pumping chamber 37 produces fluid pressure on the delivery piston with the result that it is caused to move along the delivery cylinder to cause volume reduction of the delivery chamber 75.
- inlet port 63 is closed by valve 65 and so the fuel-rich mixture is compressed in the delivery chamber and delivery passage 76.
- the piston 13 is shown ⁇ n Fig. 5 approaching its top dead-centre position.
- the inlet port 63 opens to deliver the fuel-rich mixture under pressure into the combustion chamber.
- the fuel-rich mixture combines with combustion air which was previously introduced and compressed in the combustion chamber, to create a stratified charge.
- the inlet valve then closes and ignition occurs in the combustion chamber under the action of an ignition means 89 (such as a spark plug) and expanding combustion gases in the combustion chamber force the piston to descend in the cylinder.
- an ignition means 89 such as a spark plug
- the exhaust ' port 69 opens to permit the products of combustion to exhaust from the combustion chamber, as shown in Fig. 7.
- the pumping chamber 37 undergoes volume expansion and so air is induced into it through the inlet port 43. The cycle is then repeated.
- the air which enters the combustion chamber from the transfer chamber in the piston is very effective in scavenging the combustion chamber. Additionally, there is little or no f el loss ' during scavenging as fuel is introduced separately after scavenging has been completed or at least almost completed.
- the internal combustion engine according to the second embodiment is similar to the engine of the first embodiment except for operation of the discharge vale 59 and employment of a crank assembly.
- the discharge valve 59 is not self acting as was the case within the first embodiment but rather is operated under external control. Specifically, the discharge valve 59 is biassed into a closed position by a spring 91 and is cause to open in time sequence by a push rod 93 which acts on the valve. The push rod is accommodated in a passage within the connecting rod 17 and is actuated by a cam 95 mounted on the crankshaft 15.
- the engine according to the second embodiment operates in a manner similar to the engine of the first embodiment, as can be seen from the drawings.
- a further embodiment which is similar to the first embodiment with the exception that the combustion chamber 35 includes an auxiliary region 97 into which the fuel- rich mixture is delivered so that the combustible mixture is controlled to be rich in fuel in the vicinity of the ignition means 99 at the time of ignition.
Abstract
Un moteur à combustion interne comprend un cylindre de configuration étagée, comportant une partie de travail (21) et une partie de pompage (22), ainsi qu'un piston de configuration étagée comportant une partie de travail (31) et une partie de pompage (32), lesdites parties de travail (21, 31) et de pompage (22, 32) coopérant respectivement pour définir une chambre de combustion (35) ainsi qu'une chambre de pompage (37), chacune de ces dernières variant en volume selon le mouvement de va et vient du piston dans le cylindre. L'air est admis dans ladite chambre de pompage (37) par un conduit (43) d'où, lors de la réduction en volume de cette dernière, il passe par l'intermédiaire d'une pluralité de passages (49) et d'une soupape unidirectionnelle (50) dans une chambre de transfert (47). Lors de l'expansion en volume de ladite chambre de combustion (35), l'air se trouvant dans ladite chambre (47) est déchargé de cette dernière via une pluralité de passages (55), d'un orifice de décharge commun (57) et d'une soupape (59), afin de procéder au balayage de ladite chambre de combustion (35) et de produire de l'air de combustion. Ladite soupape (59) peut être automatique ou être actionnée par un poussoir de soupape commandé par un arbre coudé. L'invention concerne également une pompe d'acheminement (63) actionnée de manière pneumatique sous l'effet de ladite chambre de pompage (37), afin d'acheminer du carburant ou un mélange combustible dans le passage d'admission (76).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AUPJ462389 | 1989-06-07 | ||
AU4623/89 | 1989-06-07 | ||
AU53446/90A AU628965B2 (en) | 1989-06-07 | 1990-03-20 | Internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0475947A1 true EP0475947A1 (fr) | 1992-03-25 |
EP0475947A4 EP0475947A4 (en) | 1992-04-01 |
Family
ID=25630069
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19900905168 Withdrawn EP0475947A4 (en) | 1989-06-07 | 1990-03-20 | Internal combustion engine |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0475947A4 (fr) |
CN (1) | CN1032326C (fr) |
WO (1) | WO1990015230A1 (fr) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL1005155C2 (nl) * | 1997-01-31 | 1998-08-03 | Bob Hoogenboom | Zuigermotor. |
AU2003303833A1 (en) * | 2003-01-27 | 2004-08-23 | Tihomir Sic | Two stroke engine with valve distribution system |
FI120212B (fi) * | 2007-03-08 | 2009-07-31 | Waertsilae Finland Oy | Parannettu kaksitahtimoottori |
RU180225U1 (ru) * | 2017-11-28 | 2018-06-06 | Александр Николаевич Черноштанов | Двухтактный двигатель с поршнем обратного действия |
CN109268274B (zh) * | 2018-12-06 | 2020-04-28 | 山东金鹏石化设备有限公司 | 一种离心泵及其装配方法 |
US11692478B2 (en) * | 2020-01-31 | 2023-07-04 | Intelline Inc. | Linear combustion engines with valve in piston |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2215793A (en) * | 1938-11-29 | 1940-09-24 | Mayes Graham | Internal combustion engine |
US2952252A (en) * | 1959-02-24 | 1960-09-13 | Charles F Geatty | Automatic fuel injection system |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB140598A (en) * | 1919-03-27 | 1920-04-01 | John Wildsmith Snarry | Improvements in, or relating to valve gear for internal combustion engines |
FR629451A (fr) * | 1926-05-04 | 1927-11-10 | Moteur à explosions à deux temps à admission forcée | |
DE596147C (de) * | 1933-03-24 | 1934-04-27 | Hermann Goebbels | Zweitaktbrennkraftmaschine mit Stufenkolben |
BE751769A (fr) * | 1970-06-10 | 1970-11-16 | Walls Patrick J | Perfectionnements aux moteurs a combustion interne et aux compresseurs |
-
1990
- 1990-03-20 WO PCT/AU1990/000114 patent/WO1990015230A1/fr not_active Application Discontinuation
- 1990-03-20 EP EP19900905168 patent/EP0475947A4/en not_active Withdrawn
- 1990-06-07 CN CN90104140A patent/CN1032326C/zh not_active Expired - Fee Related
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2215793A (en) * | 1938-11-29 | 1940-09-24 | Mayes Graham | Internal combustion engine |
US2952252A (en) * | 1959-02-24 | 1960-09-13 | Charles F Geatty | Automatic fuel injection system |
Non-Patent Citations (1)
Title |
---|
See also references of WO9015230A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN1047907A (zh) | 1990-12-19 |
WO1990015230A1 (fr) | 1990-12-13 |
EP0475947A4 (en) | 1992-04-01 |
CN1032326C (zh) | 1996-07-17 |
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