CN102459828B - Rotary valve system for internal combustion engines - Google Patents
Rotary valve system for internal combustion engines Download PDFInfo
- Publication number
- CN102459828B CN102459828B CN201080027898.1A CN201080027898A CN102459828B CN 102459828 B CN102459828 B CN 102459828B CN 201080027898 A CN201080027898 A CN 201080027898A CN 102459828 B CN102459828 B CN 102459828B
- Authority
- CN
- China
- Prior art keywords
- rotary valve
- cylinder
- air
- valve system
- piston
- 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 - Fee Related
Links
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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
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 required, by means of the air inlet, exhaust and the squeeze operation that are positioned at rotation manifold system on cylinder sleeve and carry out.
In known internal-combustion engine, the required air of motor is carried via the suction valve of camshaft actuated, and because the gas forming that burns is discharged by outlet valve.Conventionally,, because the motor using at present does not have the ability of crank angle conversion (crank angle shift), the peak of internal piston pressure is the top dead center that igniting occurs.Locate the firing pressure producing by means of the upper corners at camshaft (upper angle), 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 the power forming at burning peak can not be sent to bent axle with the form of high momentum.But towards between the moving period of lower dead center, the high-pressure combustion gas being formed by combustion mechanism is lost its pressure because volume increases at piston, and cause Engine torque to reduce at the 90 Shaft angle places (produce the highest momentum) that write music herein.Because in the motor using at present, valve system is arranged on top, firing chamber, so can not can improve to its installation the mechanism of engine efficiency.For this reason, the more efficient motor that researcher has complex mechanism with regard to production is studied.In patent document US005205251A, US5000136, CA1279018 and EP0295823, used similar rotary system, 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 proposing in the present invention, by the rotary valve system around cylinder sleeve location, by making described valve remain on closed state for air inlet, exhaust and compression, can discharge the top of cylinder.Second piston mechanism that is positioned at cylinder top makes the compression point can be by mobile towards lower piston (lower piston) and be transformed to different points with respect to crank angle from top dead center.
Shown in the drawings of the mechanism using for realizing object of the present invention, in accompanying drawing:
The three-dimensional sectional view of Tu1Shi rotary valve mechanism.
Fig. 2 is the view that the air inlet with the sectional view of the double piston engine of rotary valve starts interval (intake start interval).
Fig. 3 is piston position-crank angle graph of a relation of this double piston engine, and wherein crank angle converts.
Fig. 4 is the comparison diagram that an available engine (it has identical piston diameter and compression ratio with respect to momentum angle) and have momentum-crank angle relation of the motor of conversion crank angle.
Parts in accompanying drawing are numbered as follows and define.
1-rotary valve
2-cam following axle
3-cylinder
4-lower piston
5-upper piston
6-spark plug
The upper engine cylinder-body of 7-
Engine cylinder-body under 8-
9-bonnet
10-air-strainer
11-sparger
12-crankcase
13-lower piston crank
14-upper piston crank
15-lower link
The upper connecting rod of 16-
Rotary valve mechanism is made up of 3 parts, and these 3 parts are connected to each other and are positioned at the top cover (7) of motor and bottom (8) upper (Fig. 2), as Fig. 1 illustrates by 3-D view.Described rotary valve mechanism comprises rotary valve (1), cam following axle (2) and cylinder sleeve (3), described rotary valve (1) has location air passageways and driving gear thereon, described cam following axle (2) drives rotary valve by the air passageways being located thereon, this cylinder sleeve fitted to be has gap, sliding towards the outer surface of valve assembly.
Cam following axle (2) by crank-driven rotates the tooth of described valve by the air passageways consistent with motor angle, and changes in this way the position of rotary valve (1) on cylinder.Thus, with regard to motor angle, in the time that described valve (1) rotates and the air passageways of the portion of being located thereon part and cylinder (3) overlap air passageways is overlapping, carry out the charging stage (Fig. 2) of motor.The air passageways of opening on rotary valve in inclination mode can enter in cylinder in the charging stage air with rotation mode.In this way, the mixture of fuel and air will be uniformly distributed in cylinder, and obtain more effective burning.When described valve (1) rotates air passageways closed surface between upper air passage and lower exhaust passage can be started cover cylinder (3) and oil film while starting to demonstrate impenetrability (impermeability), will compress; And, when described valve (1) rotates when making its lower channel can cover the air passageways of cylinder sleeve (3), carry out the exhaust phase of motor.
In the time carrying out air inlet and bleeding at cylinder side wall place, can arrange second piston in the top of cylinder part, this second piston can be different amount by crank-changing, thereby produces larger moment of torsion (Fig. 2) in the time that burning starts.In this way, in the time that lower piston (4) passes through top dead center, the second piston (motion stage is poor) can be followed lower piston (Fig. 3) from top part (5) by the air in compression cylinder.Fuel-air mixture (compressed in cylinder by the conversion from top dead center) is lighted a fire by the spark plug (6) being positioned at similarly on cylinder side wall, obtains in this way firing pressure (Fig. 3---position I).The pressure obtaining by be positioned at out air passageways on casing surface and and the passage of the valve (1) that contacts of cylinder (3) between closed surface on oil film and in cylinder, kept.In this moment, along with upper piston (5) top is by air passageways region, the effective pressure that the impenetrability based on oil film provides declines.Pressure in cylinder causes producing reverse momentum, and this is because lower piston promotes pressure downwards, and this pressure applies power upwards to the upper piston that continues to move down (5).But due to than upper piston crank (14), lower piston crank (13) has the larger arm of force and angle, therefore it continues to make engine rotation.This process continues as follows: the poor momentum that improves lower piston of momentum, upper piston moves towards lower dead center simultaneously.Then,, along with upper piston (5) moves up, the power forming in company with concentrating on the pressure on upper piston (5) starts upper bent axle (14) to produce moment of torsion.Thus, upper bent axle (14) starts to provide momentum proportional to its stroke to engine crank.Decline along with the volumetric expansion of expansion stroke causes firing pressure, in the time that piston area doubles, guaranteed that the momentum decline in motor remains close to 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), instead of the high pressure forming in the burning starting stage is converted into high momentum (Fig. 4).In Fig. 4, show the motor of the present invention that there is the available engine of similar characteristic and there is translation-angle according to the difference of crank angle calculated torque value.When with available engine relatively time, owing to having converted compression point, double piston engine has obtained higher torque value at the 60-110 Shaft angle place that writes music.Afterwards, in the time that the cam following axle of valve (1) starts to rotate, and in this way when the passage that is positioned at lower surface is when being positioned at passage on cylinder and opening, start exhaust (Fig. 3---position II).In the time that lower piston (4) and upper piston (5) start to skim near passage, exhaust phase completes.When the cam following axle (2) of valve (1) starts by rotating according to suitable crank angle while changing its position, and in this way in the time that cylinder port and the passage of upper surface that is connected to valve are overlapping, beginning charging stage (Fig. 3---position III).This moment motor be illustrated in Fig. 2.Due to its position, valve (1) be positioned at passage on cylinder (3) in identical axis.Along with lower piston (4) starts to move down, will start air inlet, at the moment, air sucks from air-strainer (10), and is sent between engine cylinder-body (7) and bonnet (9).Along with air moves towards cylinder, fuel will spray to the air being inhaled into by sparger.In the time that piston moves in opposite direction, cylinder will be by being placed in the passage filling fuel-air mixture equably on valve (1) in inclination mode.In the time that valve (1) rotates and gets back to its proper angle, start compression stage, guaranteed in this way to form oil film (Fig. 3---position IV) between cylinder and valve surface.Lower piston (4) and upper piston (5) are by the air in compression cylinder.When being compressed in fuel-air mixture in cylinder when being placed in spark plug (6) igniting on cylinder side wall, will restart working stage (Fig. 3---position I).
The present invention realizes following improvement substantially:
-in the time comparing with the motor with similar piston diameter with delay-angle burning (late angle combustion), will obtain higher Engine torque.
The poor efficiency (being low to moderate 15%) of-available engine low speed rotation will be overcome by low oil consumption and smooth combustion.
-in the time that pressure span doubles due 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 according to the crank angle of top dead center conversion, can make due to flammability fast and the alternative fuel (such as hydrogen) of rough burning is suitably burnt in consistent mode.
-there is cylinder still less by producing high moment of torsion, can producing, more minor diameter piston and occupy thus the still less motor in space.
-compared with thering is the motor of similar power, by improving the thermal efficiency, will obtain lower oil consumption.
Claims (4)
1. the rotary valve system for internal-combustion engine, to be positioned at the air passageways on cylinder sleeve (3) outer surface and be positioned at the air passageways location on described rotary valve (1) by the different amount at motor, and described rotary valve (1) is rotated on the surface of described cylinder sleeve (3), this rotary valve system provides air movement at air inlet, compression and exhaust phase, this rotary valve system is characterised in that, it comprises:
-mono-cam following axle (2) with respect to lower crank axle (13) operation,
-to be positioned at air between lower engine cylinder-body (8) and upper engine cylinder-body (7) logical
Road,
Wherein, in order to make rotation is passed to rotary valve (1) makes the angular adjustment of motor consistent by be positioned at driving gear on described rotary valve by means of contact, described cam following axle (2) has the air passageways consistent with the angle of motor.
2. rotary valve system according to claim 1, is characterized in that, for impenetrability is provided, when contact during rotary valve rotation, on the closed surface between the air passageways of cylinder sleeve (3) and the air passageways of rotary valve (1), has oil film.
3. rotary valve system according to claim 1, it is characterized in that, this rotary valve system has lower piston (4) and upper piston (5) that can be mobile discretely, and this upper piston (5) is positioned on the top of cylinder sleeve (3), and this lower piston (4) is positioned on the bottom of cylinder sleeve (3).
4. rotary valve system according to claim 1, is characterized in that, in order to provide more equally distributed fuel-air mixture in cylinder sleeve (3), described rotary valve (1) has the air passageways of inclination mode.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| TR2009/03671A TR200903671A1 (en) | 2009-05-12 | 2009-05-12 | Rotary valve system for internal combustion engines. |
| TR2009/03671 | 2009-05-12 | ||
| 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 CN102459828A (en) | 2012-05-16 |
| CN102459828B true 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) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012147088A1 (en) * | 2011-04-28 | 2012-11-01 | Jitendra Kumar Barthakur | Double piston internal combustion engine |
| CN103147855B (en) * | 2013-03-11 | 2015-02-18 | 范伟俊 | Energy-saving engine |
| CN111140352B (en) * | 2019-12-31 | 2021-06-25 | 江苏理工学院 | Rotation control method of cylinder sleeve rotary type piston 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 WO PCT/TR2010/000093 patent/WO2010151238A1/en active Application Filing
- 2010-05-10 CN CN201080027898.1A patent/CN102459828B/en not_active Expired - Fee Related
- 2010-05-10 DE DE112010001995T patent/DE112010001995T5/en not_active Withdrawn
- 2010-05-10 TR TR2011/10855T patent/TR201110855T2/en unknown
- 2010-05-10 KR KR1020117029533A patent/KR20120016134A/en not_active Application Discontinuation
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 |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2010151238A4 (en) | 2011-04-28 |
| DE112010001995T5 (en) | 2013-02-07 |
| TR201110855T2 (en) | 2012-01-23 |
| KR20120016134A (en) | 2012-02-22 |
| TR200903671A1 (en) | 2010-12-21 |
| CN102459828A (en) | 2012-05-16 |
| WO2010151238A1 (en) | 2010-12-29 |
| WO2010151238A8 (en) | 2011-12-15 |
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| 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 |