IL163427A - Internal combustion engine with coupled cylinders and method for operating it - Google Patents
Internal combustion engine with coupled cylinders and method for operating itInfo
- Publication number
- IL163427A IL163427A IL163427A IL16342704A IL163427A IL 163427 A IL163427 A IL 163427A IL 163427 A IL163427 A IL 163427A IL 16342704 A IL16342704 A IL 16342704A IL 163427 A IL163427 A IL 163427A
- Authority
- IL
- Israel
- Prior art keywords
- toroidal
- rotor
- cylinders
- internal combustion
- combustion engine
- Prior art date
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
- F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
- F02B53/02—Methods of operating
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
- F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F01C1/3446—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
- F01C1/356—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F01C1/3568—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member with axially movable vanes
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Description
internal Coition Engine with Coupled Cylinders and «tnod for operating it APPLICATION FOR PATENT Inventor: Leonid Gerber Title: Internal Combustion Engine with Coupled Cylinders FIELD AND BACKGROUND OF THE INVENTION The present invention relates to internal combustion engines and, in particular, it concerns an internal combustion engine with coupled cylinders.
The basic principles of a four-stroke internal combustion engine may be equally applied to conventional reciprocating as well and rotary engines. In general, all four strokes of the cycle are preformed within the same cylinder. That is, a single piston deployed within a cylinder travels through the series of intake, compression, combustion/expansion and exhaust strokes. Therefore, the power is generated in only one of four strokes, unlike two -stroke engines in which power is generated in one of two strokes. However, two -stroke engines have historically been fuel inefficient due to the overlap of the exhaust and intake processes during a single stroke and the manner in which these processes occur.
In the move to rotary type engines, toroidal cylinder configurations have emerged in which pistons travel on a continuous path through a single toroidal chamber. In an attempt to increase power, the number of pistons has been increased. This has been done in the passed by increasing the number of pistons traveling through the same toroidal chamber. Alternatively, additional toroidal I chambers have been added, which include additional pistons. This alternative is basically linking two or more separate engines.
There is therefore a need for an engine in which first and second cylinders are configured in a common rotor deployed within a single toroidal chamber and all four strokes on the four-stroke cycle are preformed in a manner that allows for combustion and an expansion stroke on a two-stroke sequence, such that the intake and compression strokes are preformed in the first cylinder simultaneous to combustion and the expansion and exhaust strokes of a different cycle being preformed in the second cylinder.
SUMMARY OF THE INVENTION The present invention is an internal combustion engine with coupled cylinders.
According to the teachings of the present invention there is provided, [TO BE COPIED IN FROM CLAIMS WHEN FINALIZED] BRIEF DESCRIPTION OF THE DRAWINGS The invention is herein described, by way of example only, with reference to the accompanying drawings, wherein: FIG. 1 is a schematic cross section of a first preferred embodiment of an internal combustion engine constructed and operative according to the teachings of the present invention, taken along line 1 -1 in FIG. 3; FIG. 2 is a schematic cross section of the embodiment of FIG. 1, taken along line 2-2 in FIG. 4; FIGS. 3 and 4 are schematic cross sections of the embodiment of FIG. 1, taken along line 3-3 in FIG. 2; constructed and operative according to the teachings of the present invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention is an internal combustion engine with coupled cylinders.
The principles and operation of internal combustion engine according to the present invention may be better understood with reference to the drawings and the accompanying description.
By way of introduction, the principles of the present invention include providing coupled cylinders such that the intake and compression strokes are performed in a first cylinder, the pressurized fuel/air mixture is then transferred to a second cylinder for combustion, and the expansion and exhaust strokes.
Thusly configured, the first cylinder is performing an intake stroke at the same time the second cylinder is performing an expansion stroke. Similarly, the first cylinder is performing a compression stroke at the same time the second cylinder is performing an exhaust stroke. Therefore, all four strokes of the conventional four-stroke cycle are performed in a two -stroke sequence, which gives increase power over an engine in which all four strokes are performed in the same cylinder.
When applied to a toroidal engine configuration, the principles of the present invention also include structurally coupling the first and second cylinders by providing a stator containing a single toroidal volume and a common rotor, at least a portion of which travels a path defined by the toroidal volume. The rotor and the stator define between them the two toroidal cylinders. The toroidal cylinders may be configured on opposite sides of the rotor (as discussed below regarding Figures 1-4), along the peripheral edge of fhe rotor (as discussed below regarding Figures 5-10), or on the same side of rotor (as discussed below regarding Figure 11).
Referring now to the drawings, and a first preferred embodiment of the present invention as illustrated in Figures 1-4, the engine, generally referred to as 2, includes a stator 4, which may also be the engine housing, and a rotor 20.
The stator, therefore, contains a single toroidal volume, as illustrated by line 6, in which the rotor 20 is deployed. The stator 4 and the rotor 20 defined between them toroidal cylinders 22 and 24 that are configured as toroidal channels on opposite sides of the rotor 20. The toroidal cylinders 22 and 24 are configured with sloping cylinder end walls 26, 28, 30 and 32. Extending from the stator 4 into the cylinders 22 and 24 are reciprocating walls 10 and 12 that allow passage of the cylinder end walls when the rotor is turning. Reciprocating walls 10 and 12 are biased toward the rotor 20 by spring elements 8.
Thusly configured, the intake region I of toroidal cylinder 22 is located between cylinder end wall 32 and reciprocating wall 10. The compression region C is located between cylinder end wall 28 and reciprocating wall 10. The expansion region Ep of toroidal cylinder 24 is located between cylinder end wall 30 and reciprocating wall 12. The exhaust region Eh of toroidal cylinder 24 is located between cylinder end wall 26 and reciprocating wall 12. In operation, the fuel/air mixture is drawn into the intake region I through intake opening 14 as the rotor 20 turns and cylinder end wall 32 moves away form reciprocating wall 10 and the volume of the intake region I increases. When cylinder end wall 28 passes the intake opening 14 the intake region I is closed, the intake region I becomes the compression region C and the compression stroke begins as cylinder end wall 28 moves toward reciprocating wall 10. Since the charge transfer passageway 42 is closed by the stator extension 40 the fuel/mixture is trapped in the compression region C and compressed between cylinder end wall 28 and reciprocating wall 10.
An opening 40a is configured in the stator extension 40 at the point of rotation that cylinder end wall 30 passes reciprocating wall 12. This allows the charge of compressed fuel/air mixture to flow through the charge transfer passageway 42 and transfer to the expansion region Ep of toroidal cylinder 24. As cylinder end wall 28 passes reciprocating wall 10 the transfer is completed and the charge transfer passageway 42 is again closed by stator extension 40. When cylinder end wall 30 passes the igniter 46 the fuel/air mixture is ignited and the resulting Combustion drives cylinder end wall 30 away from reciprocating wall 12, thereby generating the rotational motion of the rotor 20. When cylinder end wall 30 passes the exhaust port 16, the expansion region Ep becomes the exhaust region Ex and the exhaust gases are pushed out through the exhaust port 16.
It will be readily understood that an intake stroke is occurring in the intake region I of toroidal cylinder 22 at the same time an expansion stroke of the previous cycle is occurring in the expansion region Ep of toroidal cylinder 24, and that a compression stroke is occurring in the compression region C of toroidal cylinder 22 at the same time an exhaust stroke of a previous cycle is occurring in the exhaust region Ex of toroidal cylinder 24. Therefore, all four strokes of the four-stroke process are occurring while combustion is occurring in the expansion region Ep of toroidal cylinder 24 in a two -stroke sequence.
It will be appreciated that while the discussion regarding Figures 1-4 has be directed to a single pair of coupled cylinders, this has been done for ease of understanding the principles of the present invention and is not intended as a limitation. Rather, it should be noted that a plurality of coupled cylinders may Although structurally different from the first embodiment described above, the principles of operation are the same. The fuel/air mixture is drawn into the intake region 1-200 through intake opening 214 as the rotor 220 turns and reciprocating wall 210 moves away form cylinder end wall 232 and the volume of the intake region 1-200 increases. When a subsequent reciprocating wall 210 passes the intake opening 214 the intake region 1-200 is closed and becomes the compression region C-200. At this point in the rotation, the compression stroke begins as reciprocating wall 210 moves toward cylinder end wall 228. Since the charge transfer passageway 242 is closed by flap valves 270 the fuel/mixture is trapped in the compression region C and compressed between cylinder end wall 228 and reciprocating wall 210.
Corresponding notches 272 and 274 configured in the rotor 220 permit the flap valves 270a and 270b, which are biased toward the rotor 220, to open so as to allow the charge of compressed fuel/air mixture to flow through the charge transfer passageway 242 and transfer to the expansion region Ep-200 of toroidal cylinder 224. As reciprocating wall 210 passes cylinder end wall 228 the transfer is completed and the flap valves 270a and 270b are again closed by the rotor 220. When reciprocating wall 212 passes the igniter 246 (seen only in Figure 8) the fuel/air mixture is ignited and the resulting combustion drives reciprocating wall 212 away from cylinder end wall 230, thereby generating the. rotational motion of the rotor 220. When reciprocating wall 212 passes the exhaust port 216, the expansion region Ep-200 becomes the exhaust region Ex-200 and the exhaust gases are pushed out through the exhaust port 216.
As described above, an intake stroke is occurring in the intake region I-200 of toroidal cylinder 222 at the same time an expansion stroke is occurring in the expansion region Ep-200 of toroidal cylinder 224, and a compression stroke is occurring in the compression region C-200 of toroidal cylinder 222 at the same time an exhaust stroke is occurring in the exhaust region Ex of toroidal cylinder 224. Here again, all four strokes of the four-stroke process are occurring while combustion is occurring in the expansion region Ep-200 of toroidal cylinder 224 in a two -stroke sequence.
A third preferred embodiment of a rotor 320 is schematically illustrated in Figure 1 1. In this embodiment, the coupled toroidal cylinders 322 and 324 are concentrically configured on the same side of the rotor 320. As in the embodiment of Figure 1 , the reciprocating walls are configured in the stator. The toroidal cylinders 322 and 324 may be coupled by charge transfer passageway 342 configured in the rotor, as illustrated. Alternatively, the charge transfer passageway may be configured in the stator.
It will be understood that introduction of the fuel/air mixture, engine cooling, and lubrication may be achieved by substantially any method and device known in the art.
It will be appreciated that the configurations herein describe do not require conventional intake and exhaust valves, nor the mechanisms required for their operation. This is seen as a substantially benefit of the present invention over engines of prior art. However, this should not be seen as a limitation of the present invention and the use of convention intake and exhaust valves in within the scope of the present invention.
It will be appreciated that the above descriptions are intended only to serve as examples and that many other embodiments are possible within the spirit and the scope of the present invention.
ABSTRACT OF THE DISCLOSURE The principles of the present invention include providing coupled cylinders such that the intake and compression strokes are performed in a first cylinder, the pressurized fuel/air mixture is then transferred to a second cylinder for combustion, and the expansion and exhaust strokes are preformed in the second cylinder. Thusly configured, the first cylinder is performing an intake stroke at the same time the second cylinder is performing an expansion stroke. Similarly, the first cylinder is performing a compression stroke at the same time the second cylinder is performing an exhaust stroke. Therefore, all four strokes of the conventional four-stroke cycle are performed in a two -stroke sequence, which gives increased power over an engine in which all four strokes are performed in the same cylinder. When applied to a toroidal engine configuration, the principles of the present invention also include structurally coupling the first and second cylinders by providing a stator containing a single toroidal volume and a common rotor, the rotor and the stator defining between them the two toroidal cylinders. The cylinders may be configured on opposite sides of the rotor, along the peripheral edge of the rotor, or on the same side of the rotor.
Claims (21)
1. A rotary internal combustion engine comprising^ (a) a stator containing a single toroidal volume; (b) a rotor, at least a portion of which travels a path defined by said toroidal volume; wherein said rotor and said stator define between them at least a first pair of toroidal cylinders deployed within said single toroidal volume, said pair of toroidal cylinders being in selective fluid communication such that a first of said pair of toroidal cylinders performs intake and compression strokes, a resultant compressed fuel/air mixture is transferred to a second of said pair of toroidal cylinders, in which combustion occurs and expansion and exhaust strokes are performed, and during each cycle there is at least one period when said first and second toroidal cylinders are isolated and at least one period when said selective fluid communication is established so as to allow said transfer of said compressed fuel/air mixture.
2. The rotary internal combustion engine of claim 1, wherein each of said toroidal cylinders is divided by a reciprocating wall such that said first toroidal cylinder is divided into intake and compression regions and said second toroidal cylinder is divided into combustion and exhaust regions, and each of said toroidal cylinders is configured with sloping cylinder end walls to allow passage of said reciprocating wall during rotor rotation. 1 1
3. The rotary internal combustion engine of claim 2, wherein said first and second toroidal cylinders are toroidal channels configured in said rotor and said reciprocating walls are configured in said stator.
4. The rotary internal combustion engine of claim 3, further including a passageway configured in said rotor so as to allow said selective fluid communication between said first and second toroidal cylinders.
5. The rotary internal combustion engine of claim 4, wherein said selective fluid communication is controlled by a stator extension that extends into a toroidal slot configured a peripheral edge of said rotor so as to substantially block said passageway, said stator extension having at least one gap that allows said transfer of said compressed fuel/air mixture.
6. The rotary internal combustion engine of claim 3, wherein said first and second toroidal cylinders are configured on opposite sides of said rotor.
7. The rotary internal combustion engine of claim 3, wherein said first and second toroidal cylinders are configured along a peripheral edge of said rotor.
8. The rotary internal combustion engine of claim 3, wherein said first and second toroidal cylinders are configured as concentric toroidal cylinders on the same side of the rotor of said rotor. 12
9. The rotary internal combustion engine of claim 2, wherein said first and second toroidal cylinders are toroidal channels configured in said stator and said reciprocating walls are configured in said rotor.
10. The rotary internal combustion engine of claim 9, further including a passageway configured in said stator so as to allow said selective fluid communication between said first and second toroidal cylinders.
11. The rotary internal combustion engine of claim 10, wherein said selective fluid communication is controlled by at least one flap valve deployed at one end of said passageway configured in said stator, said flap valve being biased toward an open position, said flap valve held in a closed position by said rotor and allowed to open by passage of a notch configured in said rotor.
12. The rotary internal combustion engine of claim 9, wherein said first and second toroidal cylinders are configured on opposite sides of said rotor.
13. The rotary internal combustion engine of claim 9, wherein said first and second toroidal cylinders are configured along a peripheral edge of said rotor.
14. The rotary internal combustion engine of claim 9, wherein said first and second toroidal cylinders are configured as concentric toroidal cylinders on a same side of said rotor. 13
15. The rotary internal combustion engine of claim 1, wherein said at least a first pair of toroidal cylinders is configured a plurality of pairs of toroidal cylinders.
16. A method for operating a rotary internal combustion engine, the method comprising: (a) providing a stator containing a single toroidal volume; (b) providing a rotor, at least a portion of which travels a path defined by said toroidal volume such that said rotor and said stator define between them at least a first pair of toroidal cylinders deployed within said single toroidal volume, (c) performing intake and compression strokes in a first of said pair of toroidal cylinders so as to produce a compressed fuel/air mixture; (d) establishing selective fluid communication between said first toroidal cylinder and a second toroidal cylinder such that said compressed fuel/air mixture is transferred from said first toroidal cylinder to said second toroidal cylinder; (e) isolating said first and second toroidal cylinders; (f) igniting said compressed fuel/air mixture; (g) performing expansion and exhaust strokes; (h) repeating steps c-g. 14
17. The method of claim 9, wherein said first and second toroidal cylinders are implemented on opposite sides of said rotor.
18. The method of claim 9, wherein said first and second toroidal cylinders are implemented along a peripheral edge of said rotor.
19. The method claim 9, wherein said first and second toroidal cylinders are implemented as concentric toroidal cylinders on a same side of said rotor.
20. The method claim 9, wherein said first and second toroidal cylinders are implemented as toroidal channels configured in said rotor.
21. The method claim 9, wherein said first and second toroidal cylinders are implemented as toroidal channels configured in said stator. 15
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| IL163427A IL163427A (en) | 2004-08-10 | 2004-08-10 | Internal combustion engine with coupled cylinders and method for operating it |
| PCT/IL2005/000855 WO2006016358A2 (en) | 2004-08-10 | 2005-08-09 | Rotary internal combustion engine with coupled cylinders |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| IL163427A IL163427A (en) | 2004-08-10 | 2004-08-10 | Internal combustion engine with coupled cylinders and method for operating it |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| IL163427A true IL163427A (en) | 2008-06-05 |
Family
ID=35839655
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| IL163427A IL163427A (en) | 2004-08-10 | 2004-08-10 | Internal combustion engine with coupled cylinders and method for operating it |
Country Status (2)
| Country | Link |
|---|---|
| IL (1) | IL163427A (en) |
| WO (1) | WO2006016358A2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BRPI0621488A2 (en) * | 2006-05-09 | 2013-02-13 | Okamura Yugen Kaisha | rotary piston internal combustion engine |
| CN101852124B (en) * | 2009-08-06 | 2013-04-24 | 尚世群 | Precession rotary engine |
| US20130004353A1 (en) * | 2009-09-29 | 2013-01-03 | Tiger Advanced Propulsion Technologies Ltd | Partition and partition chamber for rotary engines |
| RU2706092C2 (en) * | 2018-03-06 | 2019-11-13 | федеральное государственное бюджетное образовательное учреждение высшего образования "Алтайский государственный технический университет им. И.И. Ползунова" (АлтГТУ) | Rotary-piston internal combustion engine |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3909162A (en) * | 1970-12-03 | 1975-09-30 | Ata Nutku | Toroidal chamber rotating piston machine |
| US3798897A (en) * | 1970-12-03 | 1974-03-26 | A Nutku | Toroidal chamber rotating piston machine |
| US3773022A (en) * | 1972-01-17 | 1973-11-20 | C Constantinou | Rotary engine |
| US3871337A (en) * | 1972-09-05 | 1975-03-18 | Edward Howard Green | Rotating cylinder internal combustion engine |
| US3942484A (en) * | 1973-09-12 | 1976-03-09 | Pile Delbert W | Impeller type engine |
| DE3321461A1 (en) * | 1983-06-14 | 1985-04-04 | Arapis, Ioannis, Athen | INTERNAL COMBUSTION SATELLITE ENGINE WITH ROTATING PISTON |
| DE4324997A1 (en) * | 1993-07-26 | 1995-02-16 | Sabet Huschang | Mid-axis rotary piston internal combustion engine |
| GB2333561B (en) * | 1998-01-21 | 2002-03-20 | John Edward Archer | Rotary machine |
| GB0123809D0 (en) * | 2001-10-04 | 2001-11-21 | Masters Roy | An internal combustion engine |
| US6341590B1 (en) * | 2001-12-17 | 2002-01-29 | BARRERA RENé MANUEL | Rotary engine |
| US6880494B2 (en) * | 2003-07-22 | 2005-04-19 | Karl V. Hoose | Toroidal internal combustion engine |
-
2004
- 2004-08-10 IL IL163427A patent/IL163427A/en not_active IP Right Cessation
-
2005
- 2005-08-09 WO PCT/IL2005/000855 patent/WO2006016358A2/en active Application Filing
Also Published As
| Publication number | Publication date |
|---|---|
| WO2006016358A2 (en) | 2006-02-16 |
| WO2006016358A3 (en) | 2006-04-13 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FF | Patent granted | ||
| FF | Patent granted | ||
| MM9K | Patent not in force due to non-payment of renewal fees |