WO2018044995A1 - A two stroke engine with valves actuated by air pressure near bottom dead center - Google Patents

A two stroke engine with valves actuated by air pressure near bottom dead center Download PDF

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Publication number
WO2018044995A1
WO2018044995A1 PCT/US2017/049307 US2017049307W WO2018044995A1 WO 2018044995 A1 WO2018044995 A1 WO 2018044995A1 US 2017049307 W US2017049307 W US 2017049307W WO 2018044995 A1 WO2018044995 A1 WO 2018044995A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
stroke engine
dead center
combustion chamber
engine according
Prior art date
Application number
PCT/US2017/049307
Other languages
French (fr)
Inventor
Cesar MERCIER
Original Assignee
Mercier Cesar
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mercier Cesar filed Critical Mercier Cesar
Priority to CN201780053046.1A priority Critical patent/CN109642489B/en
Priority to RU2019108875A priority patent/RU2752214C2/en
Priority to US16/328,385 priority patent/US11280254B2/en
Priority to EP17847441.7A priority patent/EP3507471A4/en
Publication of WO2018044995A1 publication Critical patent/WO2018044995A1/en

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
    • F02B25/16—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 the charge flowing upward essentially along cylinder wall opposite the inlet ports
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B7/00—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F01B7/20—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with two or more pistons reciprocating one within another, e.g. one piston forming cylinder of the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/06—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces
    • 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
    • F02B25/20—Means for reducing the mixing of charge and combustion residues or for preventing escape of fresh charge through outlet ports not provided for in, or of interest apart from, subgroups F02B25/02 - F02B25/18
    • 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
    • F02B25/20—Means for reducing the mixing of charge and combustion residues or for preventing escape of fresh charge through outlet ports not provided for in, or of interest apart from, subgroups F02B25/02 - F02B25/18
    • F02B25/24—Inlet or outlet openings being timed asymmetrically relative to bottom dead-centre
    • 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
    • F02B33/12—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 the rear face of working piston acting as pumping member and co-operating with a pumping chamber isolated from crankcase, the connecting-rod passing through the chamber and co-operating with movable isolating member
    • 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
    • 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
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
    • 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
    • F02B2700/00—Measures relating to the combustion process without indication of the kind of fuel or with more than one fuel
    • F02B2700/03—Two stroke engines
    • F02B2700/037—Scavenging or charging channels or openings

Definitions

  • This engine provides a new configuration for a two stroke engine to incorporate advantages found in a four stroke engine, such as: oil sump, exhaust and intake valve. This engine also incorporates advantages found in a two stroke engine as well, such as forced induction without the need for a turbo or super charger.
  • FIG. 1 A shows a bottom view of an engine module made of a cylinder liner with valves, a movable piston, and a stationary piston.
  • FIG. 1 B also shows a bottom view of an engine module comprising a cylinder liner with valves, a movable piston, and a stationary piston.
  • FIG. 1 C shows a cross section view of the engine module in FIG. 1 B.
  • FIG. 1 D is a cross section view taken from the side to illustrate exhaust and air intakes while the movable is near bottom dead center.
  • FIG. 1 E is a cross section view of the engine module to illustrate air intake charge flow while the movable is near top dead center.
  • FIG. 1 F is a side view of the engine module to illustrate the valves 4.
  • FIG. 1A is a bottom view of the preferred embodiment of a new engine module which incorporates the advantages of both two-stroke and four-stroke combined.
  • Component 4 are new valves added to this new engine which will be discussed later.
  • FIG. 1 B is also a bottom view of this new engine.
  • a movable piston 2 functions within a cylinder liner 1 , which is designed to function inside of an engine block.
  • the cylinder liner can be adapted to become the engine block as well.
  • FIG 1 C is a cross section view taken from the side to illustrate the flow of the exhausts 2e and air or intake charge 1 a.
  • the valves 4 pivot on a mounted point on the cylinder liner 1 to open and close transfer ports and exhaust ports respectively. Note that the valves may pivot on other components, and more than one valve may be used in connection with rockers to open and close exhaust and intake ports located near bottom dead center.
  • the valves have two sides: one is adapted to close the exhaust port, while the other side is adapted to close the transfer ports.
  • the valve side on the exhaust side is longer, but not necessary, in order to facilitate the exhaust pressure to push the valve open.
  • valves may be coupled with a rocker assemble.
  • the exhaust pressure pushes on one side of the valve to push it open and to escape.
  • the intake charge from the rear compression chamber pushes on the other side of the valve to push it open to allow the charge to escape to the combustion chamber. This in turn closes the exhaust ports trapping the intake charge in the combustion chamber to be compressed and ignited near top dead center.
  • a scavenging process takes place as some of the exhaust is left in the combustion chamber.
  • the forced induction due to the compressed charge from the rear compression chamber pushes the valve open while at the same time closes the exhaust ports to trap and to allow the intake charge to be transferred or injected into the combustion chamber. Greater compression ratio is achieved due to the fact that the intake charge is injected under pressure into the combustion chamber. This eliminates the need to have a turbo charger or super charger.
  • a spring 5 is used to push on a rocker 6 to seat in a cavity 4h in valve 4. This action causes the valves to remain shut, closing the exhaust ports and preventing the intake charge from escaping with the exhaust while the movable piston 2 moves up towards Top Dead Center (TDC).
  • Cavity 1 h is used to lubricate the respective components.
  • FIG. 1 D is a cross section view showing exhaust 2e leaving the exhaust ports on the cylinder liner 1. This cross section view also shows the intake charge 1a being transferred to the combustion chamber. A port near the crown of the movable piston 2 is open to allow the compressed charge that was trapped within the rear compression chamber which is formed underneath the movable piston and above the stationary piston 3.
  • FIG. 1 E is a cross section view of the engine module showing intake charge 1 a passing through the stationary piston and into the rear compression chamber. Intake charge is sucked in the rear compression chamber as the sealed chamber underneath the movable piston is increased when the movable piston moves up towards TDC.
  • the intake charge may enter the rear compression chamber through a reed valve or check valve.
  • the intake charge may enter the rear compression chamber through transfer ports on the cylinder walls and through ports on the skirt of the movable piston.
  • FIG. 1 F is a side view of the engine module showing exhausts 2e escaping the cylinder liner 1 pushing through the valves 4.
  • the grooves on the cylinder liner 1 are cavities to allow coolants to cool the cylinder liner and engine block.
  • a piston seat that is adapted to transfer the force from the combustion event to the engine shaft via transmission gears or cam follower.
  • This piston seat is equipped with bearing to glide on the engine block and substantially provide a force normal to a rotatable bearing, forming a follower, with an adjacent face to a cam that turns the engine shaft directly or indirectly, wherein the follower face curve matches that of the cam profile curve when the follower is about bottom dead center which is the location on the cam profile which is further from the axis of the cam.
  • the movable piston seats on the piston seat component.
  • a follower component seats on the piston seat to push a cam which turns a shaft directly or indirectly.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)

Abstract

A new engine which incorporates the advantages found in a two-stroke with the advantages found in a four-stroke engine combined.

Description

A two stroke engine with valves actuated by air pressure near bottom dead center
BACKGROUND OF THE INVENTION:
[001] This engine provides a new configuration for a two stroke engine to incorporate advantages found in a four stroke engine, such as: oil sump, exhaust and intake valve. This engine also incorporates advantages found in a two stroke engine as well, such as forced induction without the need for a turbo or super charger.
SUMMARY OF THE INVENTION
[003] It is an object of this invention to provide a two-stroke engine with a separate lubrication system that works substantially identical to that of a four-stroke, whereas no need to pre-mix fuel and oil in order to lubricate moving parts.
[004] It is another object of this invention to use valves to control exhaust and air intake charge with forced induction to achieve a high compression ratio without intake charge escaping to the exhaust ports.
[005] It is another object of this invention to provide a piston seat that provides a normal force to support a follower or a connected rod to a shaft while managing the side thrusts of the piston throws by redirecting the related forces to the engine block rather to the cylinder walls.
BRIEF DESCRIPTION OF THE DRAWINGS:
[006] FIG. 1 A shows a bottom view of an engine module made of a cylinder liner with valves, a movable piston, and a stationary piston.
[007] FIG. 1 B also shows a bottom view of an engine module comprising a cylinder liner with valves, a movable piston, and a stationary piston.
[008] FIG. 1 C shows a cross section view of the engine module in FIG. 1 B. [009] FIG. 1 D is a cross section view taken from the side to illustrate exhaust and air intakes while the movable is near bottom dead center.
[010] FIG. 1 E is a cross section view of the engine module to illustrate air intake charge flow while the movable is near top dead center.
[011] FIG. 1 F is a side view of the engine module to illustrate the valves 4.
DETAIL DESCRIPTION OF THE PREFERRED EMBODIMENTS:
[012] FIG. 1A is a bottom view of the preferred embodiment of a new engine module which incorporates the advantages of both two-stroke and four-stroke combined. Component 4 are new valves added to this new engine which will be discussed later.
[013] FIG. 1 B is also a bottom view of this new engine. A movable piston 2, functions within a cylinder liner 1 , which is designed to function inside of an engine block. The cylinder liner can be adapted to become the engine block as well.
[014] FIG 1 C is a cross section view taken from the side to illustrate the flow of the exhausts 2e and air or intake charge 1 a. The valves 4 pivot on a mounted point on the cylinder liner 1 to open and close transfer ports and exhaust ports respectively. Note that the valves may pivot on other components, and more than one valve may be used in connection with rockers to open and close exhaust and intake ports located near bottom dead center. The valves have two sides: one is adapted to close the exhaust port, while the other side is adapted to close the transfer ports. The valve side on the exhaust side is longer, but not necessary, in order to facilitate the exhaust pressure to push the valve open. Due to inertia, the valve side facing the exhaust ports will continue to keep the exhaust ports closed as the movable piston moves up towards top dead center. Optionally, the valves may be coupled with a rocker assemble. At the end of a combustion event, the exhaust pressure pushes on one side of the valve to push it open and to escape. At the same time, the intake charge from the rear compression chamber pushes on the other side of the valve to push it open to allow the charge to escape to the combustion chamber. This in turn closes the exhaust ports trapping the intake charge in the combustion chamber to be compressed and ignited near top dead center. A scavenging process takes place as some of the exhaust is left in the combustion chamber. The forced induction, due to the compressed charge from the rear compression chamber pushes the valve open while at the same time closes the exhaust ports to trap and to allow the intake charge to be transferred or injected into the combustion chamber. Greater compression ratio is achieved due to the fact that the intake charge is injected under pressure into the combustion chamber. This eliminates the need to have a turbo charger or super charger. Optionally, a spring 5 is used to push on a rocker 6 to seat in a cavity 4h in valve 4. This action causes the valves to remain shut, closing the exhaust ports and preventing the intake charge from escaping with the exhaust while the movable piston 2 moves up towards Top Dead Center (TDC). Cavity 1 h is used to lubricate the respective components.
[015] FIG. 1 D is a cross section view showing exhaust 2e leaving the exhaust ports on the cylinder liner 1. This cross section view also shows the intake charge 1a being transferred to the combustion chamber. A port near the crown of the movable piston 2 is open to allow the compressed charge that was trapped within the rear compression chamber which is formed underneath the movable piston and above the stationary piston 3.
[016] FIG. 1 E is a cross section view of the engine module showing intake charge 1 a passing through the stationary piston and into the rear compression chamber. Intake charge is sucked in the rear compression chamber as the sealed chamber underneath the movable piston is increased when the movable piston moves up towards TDC. Optionally, the intake charge may enter the rear compression chamber through a reed valve or check valve. The intake charge may enter the rear compression chamber through transfer ports on the cylinder walls and through ports on the skirt of the movable piston.
[017] FIG. 1 F is a side view of the engine module showing exhausts 2e escaping the cylinder liner 1 pushing through the valves 4. The grooves on the cylinder liner 1 are cavities to allow coolants to cool the cylinder liner and engine block.
[018] Not included in this drawing page is a piston seat that is adapted to transfer the force from the combustion event to the engine shaft via transmission gears or cam follower. This piston seat is equipped with bearing to glide on the engine block and substantially provide a force normal to a rotatable bearing, forming a follower, with an adjacent face to a cam that turns the engine shaft directly or indirectly, wherein the follower face curve matches that of the cam profile curve when the follower is about bottom dead center which is the location on the cam profile which is further from the axis of the cam. The movable piston seats on the piston seat component. A follower component seats on the piston seat to push a cam which turns a shaft directly or indirectly.

Claims

CLAIMS:
A two stroke engine comprising:
a) A cylinder with at least one exhaust port near bottom dead center,
b) a movable piston operating within the cylinder forming a combustion chamber and adapted to indirectly transmit the force from the combustion event towards a rotary shaft, c) a stationary piston operating within the movable piston forming a rear compression
chamber other than that of the engine crank case,
d) at least one valve, mounted near bottom dead center to close the at least one exhaust port, and adapted to trap the intake charge from the rear compression chamber into the combustion chamber, wherein the at least one valve is pushed open by the exhaust pressure leaving the combustion chamber, wherein the at least one valve is then pushed back, closing the at least one exhaust port, trapping the intake charge entering the combustion chamber from the rear compression chamber due to dropping pressure in the combustion chamber from exhaust escaping.
A two stroke engine according to claim 1 , wherein intake charge enters the rear compression chamber through at least one intake port near bottom of the stationary piston, then through at least one transfer port near the crown of the stationary piston, then through at least one port on the bottom skirt of the movable piston.
A two stroke engine according to claim 1 , wherein intake charge enters the rear compression chamber through at least one intake port near bottom of the stationary piston, then through at least one check valve on the crown of the stationary piston.
A two stroke engine according to claim 1 , wherein intake charge enters the rear compression chamber through at least one transfer port near bottom of the skirt of the movable piston. A two stroke engine according to claim 1 , wherein intake charge enters the combustion chamber through at least one transfer port near the crown of the movable piston while near bottom dead center, then by pushing on the other side of the at least one valve to close the at least one exhaust port.
A two stroke engine according to claim 1 , wherein intake charge enters the combustion chamber through at least one transfer port on the cylinder wall near the crown of the movable piston while near bottom dead center, then by pushing on the other side of the at least one valve to close the at least one exhaust port. 7) A two stroke engine according to claim 1 , wherein intake charge enters the combustion chamber through at least one transfer port on the cylinder wall near the crown of the movable piston while near bottom dead center, then by pushing on the other side of the at least one valve to close the at least one exhaust port, wherein crankcase is used as rear compression chamber.
8) a two stroke engine according to claim 1 wherein the at least one valve is located near bottom dead center and is actuated by air pressure difference between exhaust gas pressure and intake charge pressure, wherein the at least one valve has two sides and pivots about the center of the two sides, wherein one side of the valve is adapted to close the exhaust port while the other side of the valve opens the at least one transfer port so as to allow the compressed charge to push the exhaust ports close then enter the combustion chamber.
9) a two stroke engine according to claim 1 wherein the at least one valve is actuated by a rocker assembly.
10) a two stroke engine according to claim 1 wherein the movable piston seats on a piston seat assembly, and this is adapted to support substantially a force normal to a rotatable bearing which forms a follower, transmitting the force from the movable piston to an adjacent cam face that ultimately turns the engine shaft, wherein the follower face curve matches that of the cam profile curve when the follower is about bottom dead center which is the location on the cam profile which is further from the axis of the cam.
PCT/US2017/049307 2016-08-30 2017-08-30 A two stroke engine with valves actuated by air pressure near bottom dead center WO2018044995A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN201780053046.1A CN109642489B (en) 2016-08-30 2017-08-30 Two-stroke engine with valve actuated by gas pressure near bottom dead center
RU2019108875A RU2752214C2 (en) 2016-08-30 2017-08-30 Two-stroke engine with valves activated by air pressure near the bottom dead point
US16/328,385 US11280254B2 (en) 2016-08-30 2017-08-30 Two stroke engine with valves actuated by air pressure near bottom dead center
EP17847441.7A EP3507471A4 (en) 2016-08-30 2017-08-30 A two stroke engine with valves actuated by air pressure near bottom dead center

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201662381260P 2016-08-30 2016-08-30
US62/381,260 2016-08-30

Publications (1)

Publication Number Publication Date
WO2018044995A1 true WO2018044995A1 (en) 2018-03-08

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ID=61301602

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2017/049307 WO2018044995A1 (en) 2016-08-30 2017-08-30 A two stroke engine with valves actuated by air pressure near bottom dead center

Country Status (5)

Country Link
US (1) US11280254B2 (en)
EP (1) EP3507471A4 (en)
CN (1) CN109642489B (en)
RU (1) RU2752214C2 (en)
WO (1) WO2018044995A1 (en)

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Publication number Priority date Publication date Assignee Title
US5050570A (en) * 1989-04-05 1991-09-24 Thring Robert H Open cycle, internal combustion Stirling engine
US20060124086A1 (en) * 2004-11-17 2006-06-15 Fabrega Juana E Controlled auto-ignition two-stroke engine
US20100108037A1 (en) * 2008-11-06 2010-05-06 Ford Global Technologies, Llc Pressurized air variable compression ratio engine system

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US1461948A (en) * 1921-05-02 1923-07-17 Stosik Boleslaw Internal-combustion engine
US1521220A (en) * 1924-04-12 1924-12-30 Friend Bentley Elements Compan Internal-combustion engine
US1744310A (en) * 1926-11-09 1930-01-21 Leonard V Hosford Internal-combustion engine
US1851530A (en) * 1929-10-02 1932-03-29 Stewart Walter Scott Internal combustion engine
US2063666A (en) * 1935-10-04 1936-12-08 Exel George Two-cycle engine
US2645214A (en) * 1949-09-05 1953-07-14 Birnstiel Eduard Two-cycle rear piston compression engine
US3885386A (en) * 1973-05-23 1975-05-27 William V Bachmann Annular piston engine with afterburner and separable power turbine
DE4234941C2 (en) * 1992-10-16 1995-05-18 Franz Rupp Internal combustion engine
DE4311620A1 (en) * 1993-04-08 1994-10-13 Frank Schmidt Two-stroke engine
RU2117787C1 (en) * 1996-08-01 1998-08-20 Анфиноген Алексеевич Лесников Internal combustion engine
CA2297393A1 (en) * 2000-02-02 2001-08-02 Normand Beaudoin Filtered exhaust engine
US8215268B2 (en) * 2008-12-19 2012-07-10 Claudio Barberato Three-stroke internal combustion engine, cycle and components
GB2533619B (en) * 2014-12-23 2017-01-25 Pattakos John A two-stroke engine having variable volume chambers within the piston

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5050570A (en) * 1989-04-05 1991-09-24 Thring Robert H Open cycle, internal combustion Stirling engine
US20060124086A1 (en) * 2004-11-17 2006-06-15 Fabrega Juana E Controlled auto-ignition two-stroke engine
US20100108037A1 (en) * 2008-11-06 2010-05-06 Ford Global Technologies, Llc Pressurized air variable compression ratio engine system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3507471A4 *

Also Published As

Publication number Publication date
US11280254B2 (en) 2022-03-22
RU2019108875A3 (en) 2021-01-15
EP3507471A4 (en) 2020-06-03
US20210293177A1 (en) 2021-09-23
RU2752214C2 (en) 2021-07-23
CN109642489A (en) 2019-04-16
RU2019108875A (en) 2020-10-02
CN109642489B (en) 2021-08-06
EP3507471A1 (en) 2019-07-10

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