CN102459828A - Rotary valve system for internal combustion engines - Google Patents
Rotary valve system for internal combustion engines Download PDFInfo
- Publication number
- CN102459828A CN102459828A CN2010800278981A CN201080027898A CN102459828A CN 102459828 A CN102459828 A CN 102459828A CN 2010800278981 A CN2010800278981 A CN 2010800278981A CN 201080027898 A CN201080027898 A CN 201080027898A CN 102459828 A CN102459828 A CN 102459828A
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- CN
- China
- Prior art keywords
- cylinder
- valve
- piston
- rotary valve
- passage
- 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.)
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Classifications
-
- 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
- F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
- F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
- F01L7/04—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves surrounding working cylinder or piston
-
- 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
- F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
- F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
-
- 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
- F01B29/00—Machines or engines with pertinent characteristics other than those provided for in preceding main groups
- F01B29/08—Reciprocating-piston machines or engines not otherwise provided for
- F01B29/10—Engines
- F01B29/12—Steam engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
- F01K7/36—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating the engines being of positive-displacement type
-
- 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
- F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
-
- 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
- F02B57/00—Internal-combustion aspects of rotary engines in which the combusted gases displace one or more reciprocating pistons
-
- 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
-
- 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
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D15/00—Varying compression ratio
- F02D15/02—Varying compression ratio by alteration or displacement of piston stroke
Abstract
A valve system is operated by rotating on the cam drive mechanism and the outer surface of the cylinder. Compression and combustion pressure is preserved by forming an oil film layer between the two surfaces that are in contact with each other when the flat surface of the valve air channels correspond to the channel located on the cylinder. Application of this system will provide a combustion start-up at crank angles wherein higher amount of torque will be obtained by forming compression at a point away from the upper dead center by positioning two corresponding pistons inside internal combustion engines.
Description
The present invention relates to internal-combustion engine air inlet, exhaust and squeeze operation required, that carry out by means of the rotation manifold system that is positioned on the cylinder sleeve.
In known internal-combustion engine, the required air of motor is carried via the suction valve of camshaft actuated, and because the formed gas of burning passes through the outlet valve discharge.Usually, because the motor that uses does not at present have the ability of crank angle conversion (crank angle shift), the top dead center of igniting for taking place in the peak of internal piston pressure.By means of the firing pressure of locating to produce in the upper corners (upper angle) of camshaft, motor can produce moment of torsion, and continues to produce moment of torsion along with piston moves downward.Because crank angle is quite little, therefore can not be sent to bent axle with the form of high momentum in the power of burning peak formation.Yet towards between the moving period of lower dead center, the high-pressure combustion gas that is formed by combustion mechanism is lost its pressure owing to volume increases at piston, and causes Engine torque to reduce at the 90 Shaft angle places (producing the highest momentum here) that write music.Because in the motor that uses at present, valve system is arranged on the top, firing chamber, so can not can improve the mechanism of engine efficiency to its installation.For this reason, the researcher studies with regard to producing the motor more efficiently with complex mechanism.Used similar rotary system among patent document US005205251A, US5000136, CA1279018 and the EP0295823, but these patent documents all openly do not provide the favourable mobile air movement from cylinder sleeve.In addition, the existing structure of these patent documents needs a large amount of mechanical parts.
In the system that the present invention proposes, the rotary valve system by around the cylinder sleeve location remains on closed state to be used for air inlet, exhaust and compression through making said valve, can discharge the top of cylinder.Second piston mechanism that is positioned at cylinder top makes that compression point can be through moving towards lower piston (lower piston) and being transformed to different points with respect to crank angle from top dead center.
Mechanism for realizing that the object of the invention uses has been shown in the accompanying drawing, in the accompanying drawing:
Fig. 1 is the three-dimensional sectional view of rotary valve mechanism.
Fig. 2 is that the air inlet of sectional view with double piston engine of rotary valve begins the view of (intake start interval) at interval.
Fig. 3 is the piston position-crank angle graph of a relation of this double piston engine, wherein crank angle generation conversion.
Fig. 4 is an available engine (it has identical piston diameter and compression ratio with respect to the momentum angle) and a comparison diagram with momentum-crank angle relation of the motor of conversion crank angle.
Parts in the accompanying drawing are by following numbering and definition.
The 1-rotary valve
2-cam following axle
The 3-cylinder
The 4-lower piston
The 5-upper piston
The 6-spark plug
The last engine cylinder-body of 7-
Engine cylinder-body under the 8-
The 9-bonnet
The 10-air-strainer
The 11-sparger
The 12-crankcase
13-lower piston crank
14-upper piston crank
The 15-lower link
The last connecting rod of 16-
Rotary valve mechanism is made up of 3 parts, these 3 parts are connected to each other and the top cover (7) and the bottom (8) that are positioned at motor gone up (Fig. 2), like Fig. 1 through shown in the 3-D view.Rotary valve with air flow passage and driving gear (1) is made up of cylinder sleeve, and this cylinder sleeve is through on it channels drive rotary valve of position, and this cylinder sleeve has air flow passage and fitted to be and has the gap, with can be towards cam following axle and valve assembly slip.Cam following axle (2) by crank-driven rotates the tooth that belongs to said valve by the passage consistent with the motor angle, and changes the position of rotary valve (1) on cylinder in this way.Thus, with regard to the motor angle,, carry out the charging stage (Fig. 2) of motor when said valve (1) rotates and is positioned at the air flow passage of air flow passage and cylinder (2) cover of its top part when overlapping.Open at the passage on the rotary valve with the inclination mode and to make air to get into rotation mode in the cylinder in the charging stage.In this way, fuel and AIR MIXTURES will evenly distribute in cylinder, and obtain more effective burning.When said valve (1) rotates so that the plat surface between last gas-entered passageway and following exhaust passage can begin to cover air passageways and the oil film of cylinder (2) when beginning to demonstrate impenetrability (impermeability), will compress; And, when said valve (1) rotates so that its lower channel can cover the air passageways of cylinder (2) time, carries out the exhaust phase of motor.
When carrying out air inlet and bleeding at the cylinder side wall place, can part arrange one second piston on the top of cylinder, this second piston can be transformed to different amount with crank, thereby when the burning beginning, produces bigger moment of torsion (Fig. 2).In this way, when lower piston (4) when the top dead center, second piston (motion stage is poor) can through the interior air of compression cylinder from top part (5) follow lower piston (Fig. 3).Fuel-air mixture (conversion through from top dead center is compressed in cylinder) is lighted a fire by the spark plug (6) that is positioned at similarly on the cylinder side wall, obtains firing pressure (Fig. 3---position I) in this way.The pressure that is obtained is able in cylinder by being positioned at out the oil film on the plat surface between the passage of passage on the casing surface and the valve (1) that contacts with cylinder (2) keep.At this constantly, along with upper piston (5) top is regional through air passageways, based on the effective pressure that impenetrability the provided decline of oil film.Pressure in the cylinder causes producing reverse momentum, and this is because lower piston promotes pressure downwards, and this pressure applies power upwards to the upper piston (5) that continues to move down.Yet, because than upper piston crank (14), lower piston crank (13) has the bigger arm of force and angle, so it continues to make engine rotation.This process continues as follows: the momentum difference has improved the momentum of lower piston, and upper piston moves towards lower dead center simultaneously.Then, along with upper piston (5) moves up, the power that forms in company with concentrating on the pressure on the upper piston (5) begins last bent axle (14) is produced moment of torsion.Thus, last bent axle (14) begins to provide and the proportional momentum of its stroke to engine crank.Descend along with the volumetric expansion of expansion stroke causes firing pressure, guaranteed when piston area doubles that the momentum in the motor descends to remaining to approach high level.In this way, the double piston engine with conversion crank angle has guaranteed that engine crankshaft corner provides long and high momentum at optimum 90 degree (approximative value), rather than will be converted into high momentum (Fig. 4) in the high pressure that the burning starting stage forms.In Fig. 4, show available engine and have the difference of the motor of the present invention of translation-angle according to crank angle calculated torque value with similar characteristic.When with available engine relatively the time and since conversion compression point, double piston engine has obtained higher torque value at the 60-110 Shaft angle place that writes music.Afterwards, when the cam following axle of valve (1) begins to rotate, and in this way when the passage that is positioned at lower surface when being positioned at passage on the cylinder and opening, beginning exhaust (Fig. 3---position II).When lower piston (4) and upper piston (5) beginning during at the passage track near across, exhaust phase is accomplished.When the cam following axle (2) of valve (1) begins through rotating according to suitable crank angle when changing its position, and in this way when the cylinder port and the passage of the upper surface that is connected to valve are overlapping, begin the charging stage (Fig. 3---position III).Motor is illustrated in Fig. 2 this moment.Because its position, valve (1) is in identical axis with passage on being positioned at cylinder (3).Along with lower piston (4) begins to move down, will begin air inlet, at the moment, air sucks from air-strainer (10), and is sent between engine cylinder-body (7) and the bonnet (9).Along with air moves towards cylinder, fuel will spray to the air that is inhaled into through sparger.When piston moved in opposite direction, cylinder will be through placing the passage filling fuel-air mixture equably on the valve (1) with the inclination mode.When valve (1) rotated and get back to its proper angle, the beginning compression stage had guaranteed between cylinder and valve surface, to form oil film (Fig. 3---position IV) in this way.Lower piston (4) and upper piston (5) are with the air in the compression cylinder.Fuel-air mixture in being compressed in cylinder will restart working stage (Fig. 3---position I) through placing spark plug (6) when igniting on the cylinder side wall.
The present invention realizes following improvement basically:
-when burning (late angle combustion) when comparing, with obtaining higher Engine torque with motor with similar piston diameter with delay-angle.
The poor efficiency of-available engine low speed rotation (being low to moderate 15%) will be able to overcome through low oil consumption and smooth combustion.
-when the pressure span doubles owing to moving upward of upper piston, no matter the decline of internal pressure of combustion chamber will obtain high value momentum curve.
-by means of crank angle, can make because quick flammability and the alternative fuel (such as hydrogen) of rough burning is suitably burnt with the mode of unanimity according to the top dead center conversion.
-have cylinder still less through producing high moment of torsion, can producing, more minor diameter piston and occupy the still less motor in space thus.
-compare with motor with similar power, through improving the thermal efficiency, will obtain low oil consumption.
Claims (according to the modification of the 19th of treaty)
1. rotary valve system that is used for internal-combustion engine; To be positioned at air passageways and the air passageways location that is positioned on the said rotary valve (1) on cylinder sleeve (3) outer surface through different amount at motor; And said rotary valve (1) rotatablely moves on the surface of said cylinder sleeve (3); This rotary valve system provides air movement at air inlet, compression and exhaust phase, and this rotary valve system is characterised in that it comprises:
-one cam following axle (2) with respect to lower crank axle (13) operation,
-be positioned at down the air passageways between engine cylinder-body (7) and the last engine cylinder-body (8),
-one cylinder (3) cover with air passageways, it firmly is positioned at said engine cylinder-body (7) down and said going up between the engine cylinder-body (8).
2. the cam follower shaft (2) that is used for rotary valve (1) system according to claim 1; It is characterized in that; Make the angular adjustment of motor consistent in order to make through by means of Contact Tooth rotation being passed to valve (1), valve (1) has the air passageways with said tooth coupling.
3. system according to claim 1 is characterized in that, for impenetrability is provided, during contact during the valve rotation, on the closed surface between the air passageways of the air passageways of cylinder (3) and valve (1), has oil film.
4. valve system according to claim 1 is characterized in that, this valve system has the piston (4,5) that can move discretely, and this piston is positioned on the top (5) and bottom (4) of cylinder sleeve (3).
5. according to each described system among the claim 1-4, it is characterized in that for higher torque curve is provided, during the moving upward of upper piston (5), when inner pressure of air cylinder was low, the piston face area doubled.
6. valve according to claim 1 (1) is characterized in that, in order in cylinder sleeve (3), more equally distributed fuel-air mixture to be provided, said valve has the air passageways of inclination mode.
Explain or state (according to the modification of the 19th of treaty)
Statement according to the 1st section of the 19th article
In this application,, at first specification and claims reference mark are in full revised in order to solve the problem of knowing that point out in the written comment at the 2nd.Revise the sentence structure in specification and claims simultaneously, made the application clearer.Carrying out above-mentioned modification is to have the part mistake because of the translation from Turkey's priority document to English, causes unclear problem.
Claims (6)
1. rotary valve system that is used for internal-combustion engine; It is characterized in that; This rotary valve system comprises cam following (a 2) axle and a cylinder sleeve (3) with respect to the operation of lower crank (13) axle; This cylinder liner has the lip-deep air passageways that is positioned at valve (1), and this rotary valve system also has the air flow passage that is positioned at down between engine cylinder-body (7) and the last engine cylinder-body (8), in this way; To be positioned at passage and the passage rotation and the location that are positioned on the said valve on cylinder (2) outer surface through the different amount at motor, this rotary valve system provides air movement at air inlet, compression and exhaust phase.
2. rotary valve according to claim 1 system; It will be delivered to said valve (1) from rotatablely moving of obtaining of crank angle; With the angle accuracy that to drive, and this rotary valve system has a cam following mechanism (2) that comprises passage, and said passage carries out servo-actuated through the valve tooth.
3. motor according to claim 1; It is characterized in that; The hole of cylinder is aimed at the plat surface at the air passageways of said valve place, and guarantees impenetrability through the oil film that is positioned at these two surfaces, thereby during engine operation, keeps the gas pressure that the burning back forms.
4. valve arrangement according to claim 1 wherein positions through the piston that can move to cylinder lower zone and upper area discretely, and the firing angle of motor is transformed to the angle of guaranteeing bigger momentum.
5. according to claim 1-4, wherein form the moment that moves upward and depart from of the upper piston of positive momentum, therefore when the pressure in the cylinder reduces, in this way, in motor, obtain high torque curve through piston surface area is doubled corresponding to piston.
6. valve according to claim 1 (1), wherein said valve have with the open passage of inclination mode, so that more equally distributed fuel-air mixture to be provided in cylinder.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| TR2009/03671 | 2009-05-12 | ||
| TR2009/03671A TR200903671A1 (en) | 2009-05-12 | 2009-05-12 | Rotary valve system for internal combustion engines. |
| PCT/TR2010/000093 WO2010151238A1 (en) | 2009-05-12 | 2010-05-10 | Rotary valve system-for internal combustion engines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102459828A true CN102459828A (en) | 2012-05-16 |
| CN102459828B CN102459828B (en) | 2014-11-12 |
Family
ID=43216428
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080027898.1A Expired - Fee Related CN102459828B (en) | 2009-05-12 | 2010-05-10 | Rotary valve system for internal combustion engines |
Country Status (5)
| Country | Link |
|---|---|
| KR (1) | KR20120016134A (en) |
| CN (1) | CN102459828B (en) |
| DE (1) | DE112010001995T5 (en) |
| TR (2) | TR200903671A1 (en) |
| WO (1) | WO2010151238A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103147855A (en) * | 2013-03-11 | 2013-06-12 | 范伟俊 | Energy-saving engine |
| CN111140352A (en) * | 2019-12-31 | 2020-05-12 | 江苏理工学院 | Rotation control method of cylinder sleeve rotary type piston engine |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012147088A1 (en) * | 2011-04-28 | 2012-11-01 | Jitendra Kumar Barthakur | Double piston internal combustion engine |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB191515059A (en) * | 1915-10-25 | 1916-08-10 | John Petter Carlson | Improvements in and connected with the Valve Mechanism of Internal-combustion Engines. |
| EP0086925A1 (en) * | 1982-02-23 | 1983-08-31 | Enrico Luigi Ferraro | Controlled ignition thermic engine with variable compression ratio and with low exhaust's pollution |
| EP0295823A2 (en) * | 1987-06-18 | 1988-12-21 | George M. Barrett | Internal combustion engine assembly |
| US5109810A (en) * | 1990-09-24 | 1992-05-05 | Christenson Howard W | Two cycle internal combustion hydrocycle engine |
| DE4318256C1 (en) * | 1993-06-02 | 1994-10-13 | Ruediger Kohls | Internal combustion engine with at least two cylinders arranged in a cylinder block |
| EP0799978A2 (en) * | 1996-04-03 | 1997-10-08 | Pierre Bourguignon | Two stroke internal combustion engine with crosshead and comprising rotary sleeve distribution |
| EP1437482B1 (en) * | 2003-01-07 | 2006-05-17 | Capossela, Domenico | Opposed pistons engine in only one rotating cylinder |
| WO2007006469A2 (en) * | 2005-07-08 | 2007-01-18 | Otto Daude | Gas flow control for opposed piston engine comprising sliding sleeves |
| US7341040B1 (en) * | 2005-07-14 | 2008-03-11 | Bernard Wiesen | Supercharged two-cycle engines employing novel single element reciprocating shuttle inlet valve mechanisms and with a variable compression ratio |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5000136A (en) | 1984-11-15 | 1991-03-19 | Hansen Craig N | Internal combustion engine with rotary valve assembly |
| CA1279018C (en) | 1986-09-12 | 1991-01-15 | Paul C. Cross | Internal combustion engine with rotary combustion chamber |
| US5205251A (en) | 1992-08-05 | 1993-04-27 | Ibex Technologies, Inc. | Rotary valve for internal combustion engine |
-
2009
- 2009-05-12 TR TR2009/03671A patent/TR200903671A1/en unknown
-
2010
- 2010-05-10 CN CN201080027898.1A patent/CN102459828B/en not_active Expired - Fee Related
- 2010-05-10 KR KR1020117029533A patent/KR20120016134A/en not_active Application Discontinuation
- 2010-05-10 DE DE112010001995T patent/DE112010001995T5/en not_active Withdrawn
- 2010-05-10 WO PCT/TR2010/000093 patent/WO2010151238A1/en active Application Filing
- 2010-05-10 TR TR2011/10855T patent/TR201110855T2/en unknown
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB191515059A (en) * | 1915-10-25 | 1916-08-10 | John Petter Carlson | Improvements in and connected with the Valve Mechanism of Internal-combustion Engines. |
| EP0086925A1 (en) * | 1982-02-23 | 1983-08-31 | Enrico Luigi Ferraro | Controlled ignition thermic engine with variable compression ratio and with low exhaust's pollution |
| EP0295823A2 (en) * | 1987-06-18 | 1988-12-21 | George M. Barrett | Internal combustion engine assembly |
| US5109810A (en) * | 1990-09-24 | 1992-05-05 | Christenson Howard W | Two cycle internal combustion hydrocycle engine |
| DE4318256C1 (en) * | 1993-06-02 | 1994-10-13 | Ruediger Kohls | Internal combustion engine with at least two cylinders arranged in a cylinder block |
| EP0799978A2 (en) * | 1996-04-03 | 1997-10-08 | Pierre Bourguignon | Two stroke internal combustion engine with crosshead and comprising rotary sleeve distribution |
| EP1437482B1 (en) * | 2003-01-07 | 2006-05-17 | Capossela, Domenico | Opposed pistons engine in only one rotating cylinder |
| WO2007006469A2 (en) * | 2005-07-08 | 2007-01-18 | Otto Daude | Gas flow control for opposed piston engine comprising sliding sleeves |
| US7341040B1 (en) * | 2005-07-14 | 2008-03-11 | Bernard Wiesen | Supercharged two-cycle engines employing novel single element reciprocating shuttle inlet valve mechanisms and with a variable compression ratio |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103147855A (en) * | 2013-03-11 | 2013-06-12 | 范伟俊 | Energy-saving engine |
| CN111140352A (en) * | 2019-12-31 | 2020-05-12 | 江苏理工学院 | Rotation control method of cylinder sleeve rotary type piston engine |
Also Published As
| Publication number | Publication date |
|---|---|
| TR201110855T2 (en) | 2012-01-23 |
| WO2010151238A4 (en) | 2011-04-28 |
| CN102459828B (en) | 2014-11-12 |
| KR20120016134A (en) | 2012-02-22 |
| DE112010001995T5 (en) | 2013-02-07 |
| WO2010151238A8 (en) | 2011-12-15 |
| TR200903671A1 (en) | 2010-12-21 |
| WO2010151238A1 (en) | 2010-12-29 |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20141112 Termination date: 20170510 |
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| CF01 | Termination of patent right due to non-payment of annual fee |