EP1339952B1 - Moteur a combustion interne a piston rotatif - Google Patents

Moteur a combustion interne a piston rotatif Download PDF

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Publication number
EP1339952B1
EP1339952B1 EP01993746A EP01993746A EP1339952B1 EP 1339952 B1 EP1339952 B1 EP 1339952B1 EP 01993746 A EP01993746 A EP 01993746A EP 01993746 A EP01993746 A EP 01993746A EP 1339952 B1 EP1339952 B1 EP 1339952B1
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EP
European Patent Office
Prior art keywords
working
wheel
air
internal combustion
combustion engine
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EP01993746A
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German (de)
English (en)
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EP1339952A1 (fr
Inventor
Hubert Winterpacht
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Individual
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Individual
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Classifications

    • 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
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/006—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle
    • F01C11/008—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle and of complementary function, e.g. internal combustion engine with supercharger
    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/20—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with dissimilar tooth forms
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/06—Heating; Cooling; Heat insulation
    • 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
    • F02B2053/005—Wankel engines

Definitions

  • the invention relates to a rotary piston internal combustion engine.
  • the Invention a rotary piston internal combustion engine with a housing, at least a work wheel rotatable about an axis of rotation in the housing, at least a working piston provided on the working wheel for suction and compression of air or a fuel-air mixture and for the implementation of the Combustion of a fuel-air mixture resulting gas pressure in mechanical Energy, at least one counter wheel with at least one working piston recess, a number of rotatably drivable first air blades for the pre-compression of air or a fuel-air mixture and at least one combustion chamber Combustion of a fuel-air mixture.
  • axis of rotation around which the The working wheel and the piston or pistons rotate, not one physically trained axis (such is hereinafter referred to as “shaft”), but understood the physical line through the center of the rotary motion becomes.
  • Internal combustion engines are based on the type of movement of the working piston, that is of the moving part caused by the combustion of a fuel-air mixture emerging gas pressure is pushed away in reciprocating engines and Differentiated rotary lobe motors.
  • rotary piston internal combustion engines come without translational moved pistons and connecting rods, and the piston or pistons move in the Operation on a circular path always in the same direction so that it doesn't like Pistons are continuously braked and accelerated in the opposite direction have to.
  • the best-known representative of the type of rotary piston internal combustion engine is the Wankel engine named after its inventor.
  • a piston rotates on the Wankel engine with a triangular cross section in a specially shaped cylinder. Due to sealing problems and the resulting high fuel consumption the engine was not able to assert itself despite the design-related advantages.
  • a rotary lobe internal combustion engine is known from German Offenlegungsschrift 29 31 943 A1 known in which rotatably mounted in a housing Working wheel two working pistons are arranged, the working wheel in its Broken area near the axis of rotation and by means of attached webs as Fan wheel is formed so that the work wheel is advantageously cooled from the inside.
  • the combustion of the fuel-air mixture takes place in one with this engine separate combustion chamber, which leads to a complex construction of the engine.
  • a rotary piston internal combustion engine is known from German published patent application 31 31 258 A1 known with a work wheel and a compression wheel that are arranged on a common shaft.
  • the compression wheel carries several Compression piston for compressing a fuel-air mixture, which is then in a combustion chamber formed between the compression wheel and the impeller is pressed where the ignition takes place. From the combustion chamber, the Combustion gases are fed to the working wheel, where they act on the working pistons can. Inlet and outlet into the combustion chamber take place via a relatively complex Valve control. In addition, the cooling of the working wheel and the working pistons is problematic with this engine.
  • a rotary piston internal combustion engine which has a housing, at least one work wheel rotatable in the housing about an axis of rotation, at least one working piston provided on the working wheel for compressing Air or a fuel-air mixture and for the implementation of the combustion a gas-pressure mixture resulting in gas pressure into mechanical energy, at least one counter wheel with at least one working piston recess, a number of rotatable first air blades for pre-compression of air or one Fuel-air mixture and at least one combustion chamber for the combustion of a Has fuel-air mixture, wherein the at least one combustion chamber in operation continuously newly formed between the working piston, working wheel, counter wheel and housing will and form the first air blades like spokes part of the working wheel and in operation the fuel-air mixture or the air substantially parallel to Suction the axis of rotation of the work wheel through the work wheel.
  • the invention has a number of advantages. So the one sucked through the work wheel cools gaseous medium, which will usually be air, which it but it can also be a fuel-air mixture, the working wheel from the inside.
  • gaseous medium which will usually be air, which it but it can also be a fuel-air mixture, the working wheel from the inside.
  • the working piston or pistons act twice in each case: when they approach the counter wheel move, compress the air that is already pre-compressed, if necessary already formed fuel-air mixture, after passing through the corresponding working piston recess in the counter wheel they act as "movable Wall "of the combustion chamber caused by the gas pressure generated during combustion is pushed away.
  • the work wheel with the air blades and one or more working pistons even performs three functions: pre-compacting, compacting, working.
  • the output takes place in the center of the Work wheel arranged output shaft, the axis of rotation of which is then identical to that Rotation axis of the work wheel is.
  • the first air blades can then be advantageous attack directly or indirectly (via a gearbox) on the output shaft and so that of mechanical energy absorbed by the piston or pistons on the output shaft transmitted from where it is then forwarded in a manner known per se and e.g. to the Drive of a vehicle can be used.
  • a gearbox so that of mechanical energy absorbed by the piston or pistons on the output shaft transmitted from where it is then forwarded in a manner known per se and e.g. to the Drive of a vehicle can be used.
  • an output shaft the axis of rotation of which is not coincides with the axis of rotation of the working piston.
  • the drive of the Output shaft then e.g. over a sprocket provided on the work wheel take place, which drives the output shaft directly or indirectly.
  • a number of second air blades that can be driven in rotation can be provided for further pre-compression of air or a fuel-air mixture his.
  • These second air blades can be part of a ring gear like a spoke and also attack the output shaft.
  • These spoke-like blades have then a profile that rotates as in the usual compressor stages of a turbine causes a compression of the conveyed medium about the axis of rotation.
  • the ring gear with the second air blades firmly connected to the work wheel. If such a ring gear is provided, it can this ring gear with the second air blades with one at least partially complementary ring gear on the counter gear in meshing engagement. To this This results in a reliable positive control of the counter wheel.
  • the work wheel can move over the ring gear be set. Because the engine is actively filled in the combustion chamber area and none Has suction function, can via a rotation caused by the starter Working wheel the first filling to start the engine.
  • a reservoir can be used to hold the working piston in operation compressed gaseous medium (air or fuel-air mixture) when Passage of the working piston through the counter wheel
  • the Reservoir e.g. semi-cylindrical or toroidal and part of the housing or can be a separate component attached to the housing.
  • the counter gear can Openings and corresponding valves have, in particular, spring elements or can be hydraulically controlled. That from a working piston at the Movement of the gaseous medium compressed on the counter wheel is converted into one in the counter wheel formed, serving as a reservoir and pressed after passage of the piston left out again.
  • the rotary piston internal combustion engine at least two arranged on a common work wheel Has working pistons
  • the inlet and the outlet are open at the same time, which enables purge air to lead through the inlet into the space between the two neighboring ones Working piston, the housing and the working wheel is formed. This may still be Exhaust gases present in the room are reliably pushed out.
  • purge air it can be advantageous for the first and possibly the second air scoop sucked in gaseous medium, the medium being this In this case, of course, it is not about a fuel-air mixture, but about air should act.
  • the fuel or a fuel-air mixture then becomes later added, in particular by means of one arranged after the counter wheel Injector.
  • the compressor stage which is formed by the first and second air blades, is in a preferred embodiment, an exhaust gas turbocharger connected downstream of the ambient air drawn in can also compress.
  • This exhaust gas turbocharger can be designed as a so-called soft turbocharger that continuously with the Speed increasing boost pressure generated.
  • the working pistons can be designed as a solid component, they are preferred provided with cooling. In one configuration, this cooling can be performed by a Charge air cooling takes place, which is the ambient air drawn in by the compressor stage cools.
  • Another preferred embodiment has active piston cooling, at which the first air blades are arranged centrally below the working piston, wherein the working pistons have a U-shaped cooling channel.
  • This cooling channel is In terms of flow technology, one end is arranged in front of the compressor stage Intake side and with the opposite end with that behind the compressor stage arranged pressure side connected. Due to the pressure drop along the In this embodiment, the compressor axis will have an air flow through it Form cooling channel. This is a simple and efficient cooling of the Working piston guaranteed.
  • the work wheel can also drive the counter wheel via other drive means.
  • This can be, for example, a drive chain which, in the manner of a timing chain conventional reciprocating engines in the ring gear of the work wheel with the complementary ring gear of the counter wheel instead of an immediate toothing combines.
  • the only important thing here is the correct interpretation of the Translation ratio, since it must be guaranteed at all times that the Engage the working piston in the working piston recess, which is due to this required speed ratio is realized.
  • FIG. 1 to 3 show a rotary piston internal combustion engine in which in a working wheel 2 with a housing 1 provided with a plurality of cooling fins is rotatably mounted.
  • the working wheel carries four working pistons 3, which are in operation continuously on a counter wheel 4 run to and away from this, with a 4 in the counter gear Working piston recess 5 is provided so that the working piston 3 with the Combing counter gear 4 in the manner of gears.
  • the working pistons 3 engage in the working piston recess 5, which is designed so that there is a rolling of the front and outer edge of the piston on the inner contour of the working piston recess results.
  • Counter wheel 4 which is arranged such that the outer running surface of the counter wheel 4 and the working wheel 2 each roll on each other, so here the counter wheel 4 rotates clockwise while the work wheel 2 rotates counterclockwise.
  • This combustion chamber is limited by the inner facing the counter wheel 4 Side of the working piston 3, part of the tread of the counter wheel 4 and the inner wall of the working wheel 2 and the wall of the housing 1.
  • This housing 1 is designed on its side facing the work wheel 2 so that there is a fine tread like a cylinder liner for the Piston 3 results.
  • the housing 1 either in the be processed according to the quality or have a standard, which in the Housing 1 is used and the required type of cylinder liner Offers surface quality and tread.
  • the housing 1 or the standard of the Housing 1 offer a receptacle for the counter wheel 4, which also has a tread for the largely gas-tight system of the counter wheel 4 on the side wall of the Housing 1 offers. Under the counter wheel 4, a reservoir 12 is arranged, the Operation will be described below.
  • an advance outlet and an inlet 13 for the Purge air and an outlet 14 for a mixture of exhaust gas and purge air When viewed in the direction of rotation, an advance outlet and an inlet 13 for the Purge air and an outlet 14 for a mixture of exhaust gas and purge air. Further in Seen in the direction of rotation is an air inlet or an inlet for a fuel-air mixture provided on the for the renewed combustion process compressing gas can be sucked.
  • the work wheel 2 consists essentially of a pulley-like Construction shown in section in the figures.
  • the working piston 3 are arranged equidistantly, which here from flat webs are formed, the annular channel of the working wheel 2 in here divide four segments.
  • the inner wall of the housing 1 or a standard of the housing 1 results in a closed space in each case Shape of a toroidal segment with a rectangular cross section, which is caused by the rotation of the Working wheel 2 is moved around the axis of rotation.
  • the Specification does not preclude that through inlet or outlet openings a gas exchange with the outside can take place.
  • the work wheel 2 has first air blades 6, so that it inner area is designed in the manner of a turbine wheel. These air blades 6 are with their outer ends with the groove-shaped outer area and with inner Ends connected to an inner hub.
  • the first air blades 6 are preferred arranged concentrically and symmetrically to the axis of rotation R. About in the case of used first air blades 6 and their position relative to medium flowing through the compression ratio, that is behind the Working wheel in the housing prevailing pressure can be set.
  • the operation of the first air blades is best shown in FIG. 2 and 3 too detect.
  • the air from the left side of the housing 1 passes through the rotation of the drive wheel 2 sucked air through an inner Flow channel flows through.
  • the air drawn in and compressed in this way collects in an air collection container (not shown here), which is fluidically connected an air inlet of the housing 1 into the channel of the working wheel 2 near the combustion chamber connected is.
  • compressed air can be provided without the need for additional components for compression.
  • the motor has a second compressor stage which is operated by a Gear ring 10 is formed, which is placed on the shaft holding the drive wheel 2 is.
  • This ring gear 10 actually has the function of driving the counter wheel 4 and similar to the drive wheel 2, has an inner area which is connected to the second Air blades 9 is provided and can be flowed through by gaseous medium.
  • FIG. 1 to 3 shown embodiment is only a principle Representation of a single cylinder, but is already fully functional.
  • Prefers However, several work wheels are used, both on a common Output shaft 8 as well as be arranged side by side on several shafts can. In this way, multi-row or multi-stage motors with one Multiple combustion chambers possible.
  • a motor can also be formed, which has two combustion chambers per working wheel 2.
  • the only important thing here is The fact that behind the counter gear 4, the functional areas described here for Expulsion and flushing of the combustion residues and in front of the counter wheel 4 Precautions for filling with ambient air and compressing the Combustion air are provided.
  • Behind the counter wheel 4 is one Injection nozzle arranged, for example, diesel fuel or kerosene can be injected into the combustion chamber.
  • FIG. 4 shows that Working wheel 2 in a position in the pre-compressed ambient air in the later Combustion chamber, i.e. has entered the groove of the work wheel 2.
  • This gas volume which is under increased pressure relative to the ambient pressure, becomes now by further rotation of the work wheel 2 in the direction of the counter wheel 4 transported and by further collision of the working piston 3 on the counter wheel 4 increasingly reduced in size.
  • the compression of the Gas volume on so that in a preferred embodiment, for example builds up a pressure of approx. 40 bar due to a compression ratio of 1:20.
  • the side Pressure reservoir opened so that the compressed medium is in this reservoir can flow in easier relaxation.
  • this torus segment fills with the while relaxing compressed medium, which now have a pressure of 30 bar, for example can.
  • a further rotation of the work wheel 2 by a few angular degrees causes Moving the lateral inlet opening away from the outlet of the pressure reservoir 12, that the torus segment completely to form a closed combustion chamber is closed.
  • Ignition device can already be ignited provided the enclosed medium is a fuel-air mixture.
  • a diesel engine is preferred
  • Direct injection used there is an injection nozzle behind the counter wheel 4 provided, for example in FIG. 1 is shown. In the case of direct injection in the case shown, the gasoline becomes tangential along the surface of the counter wheel 4 injected.
  • the shape of the side walls and the Bottom of the groove-shaped channel according to the flow requirements be modified. So it is possible, for example, that instead of here shown planes on surfaces of counter wheel 4 and groove base of drive wheel 2 a slightly spherical configuration of the counter wheel 4 and a corresponding one negative shape of the groove base of the drive wheel 2 is selected. Also the Injection angle relative to the two directions perpendicular to the axis of rotation R des Drive wheel 2 can be modified depending on the requirement to a possible to guarantee 100 percent and therefore low-pollution combustion.
  • the drive wheel 2 is rotated further, so that initially a side pollutant outlet comes into flow contact with the combustion chamber. hereby
  • the first exhaust gases already escape, which are the usual exhaust gas cleaning and exhaust systems can be supplied.
  • a further rotation of the work wheel 2 causes the chamber volume possibly still filled with residual gases is congruent with a Inlet 13 is brought to which a pressurized ambient air volume is created. When the chamber comes into contact with flow, this inlet 13 flows Ambient air then enters the chamber and can pass through an outlet 14 below Exit the gas residues to flush them out completely.
  • the working pistons 3 are designed with their outer contour so that in the upper Area is a large expansion, which is an automatic seal with the inner running surface of the housing 1 results. Additional sealants such as Piston rings in the case of a reciprocating piston engine are not required.
  • the work wheel 2 is mounted in the housing 1 via slide bearing 11.
  • the pre-compressed gaseous media can be compressed by the work wheel itself.
  • the work wheel has one within the toroidal work area Design according to the shape of a turbine wheel.
  • This turbine wheel is made by first air blades 6 are formed, which suck ambient air from the environment and provide compressed in a chamber volume.
  • a second compressor stage can be provided which additionally compresses the air, the chamber volume is both with the purge air inlet 13 and with the inlet connected for the gaseous medium to be compressed.
  • the gaseous medium is under a pressure of, for example 2.5 bar relative to the environment. This causes a quick and safe inflow of the Ambient air into the respective volumes of the annular body without being long Opening times of the valves would be required.
  • FIG. 10 shows a schematic diagram of a single-engine with only one drive wheel 2 and a counter wheel 4.
  • FIG. 11 shows an expansion of the engine with two Drive wheels 2, which use a common counter wheel 4 for building the function.
  • FIG. 12 shows a star-shaped structure of a three-barrel motor, which also uses a common counter gear. This structure is particularly advantageous because the Compensate for the axial load on the bearing of the counter wheel 4. In in this case, the bending stress on the bearing of the counter wheel 4 is minimized, which has positive effects on both wear and bearing losses Has.
  • a common Rotation shaft also several drive wheels can be arranged one behind the other, so that there is a multi-stage motor with several drive wheels 2, which by one common axis of rotation R are rotatably mounted.
  • each of the Drive wheels 2 interact with a counter wheel 4, but it is also possible that instead of several counter wheels 4 a roller-like configuration of the Counter wheel 4 is used, this one counter wheel 4 then used with all Driving wheels works together.
  • the latter configuration is of course only possible when the angular position of the working piston 3 for all drive wheels 2 each is identical.
  • a rotation of the drive wheels 2 relative to one another leads to a rounder running of the engine and so the higher effort for storage justify the different counter wheels 4.
  • FIG. 13, 14 and 15 show a multi-row engine like the one above has been described. All drive wheels are flowed through and point one turbine wheel each.
  • the one available behind the turbine wheel Overpressure can either be directly to the respective openings of the drive wheels be guided or behind the turbine wheel stack in a common reservoir be directed from where it can be fed from the corresponding openings.
  • FIG. 18 shows the housing without the drive wheel 2, so that the reservoir 12 and the opposite exhaust gas discharge can be seen. At the center of the The second compressor stage with the second air blades 9 can be seen in the housing.
  • FIG. 19 shows, on the other hand, that shown in FIG. 18 not shown part of the engine with the Counter gear 4 and drive gear 2.
  • the counter gear 4 rotates twice as fast here like the drive wheel 2, so that engagement of the working piston 3 in the Piston recesses 5 is securely guaranteed.
  • FIG. 20 shows a side view of the device shown in FIGS. 18 and 19 shown motor, at the reservoir 12 is particularly well recognizable.

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

Claims (10)

  1. Moteur à combustion interne à piston rotatif comprenant
    un carter (1),
    au moins une roue de travail (2) tournant autour d'un axe de rotation (R) dans le carter (1),
    au moins un piston moteur (3) prévu sur ladite roue de travail (2) et destiné à aspirer et à comprimer de l'air ou un mélange air-carburant et à transformer en énergie mécanique la pression de gaz produite lors de la combustion d'un mélange air-carburant,
    au moins une roue conjuguée (4) ayant au moins un creux (5) pour les pistons moteurs,
    un nombre de premières pales d'air (6) entraínables en rotation et destinées à la précompression d'air ou d'un mélange air-carburant, et
    au moins une chambre de combustion (7) pour la combustion d'un mélange air-carburant,
    ladite au moins une chambre de combustion (7) étant formée, durant la marche, continuellement à nouveau entre le piston moteur (3), la roue de travail (2), la roue conjuguée (4) et le carter (1), et
    lesdites premières pales d'air (6) constituant, à l'instar de rayons, une partie de la roue de travail et aspirant, durant la marche, le mélange air-carburant ou l'air à travers la roue de travail (2),
    caractérisé par le fait
    que la roue de travail (2) est réalisée à la manière d'une poulie et dispose d'au moins un canal interrompu par le ou les pistons moteurs (3) et s'étendant, à part cela, tout autour en anneau, et
    que chaque piston moteur est disposé solidement dans un tel canal d'une roue de travail.
  2. Moteur à combustion interne à piston rotatif selon la revendication 1, caractérisé par le fait que chaque piston moteur (3) est réalisé comme entretoise plate.
  3. Moteur à combustion interne à p iston rotatif selon la revendication 1 ou 2, au moins deux pistons moteurs étant disposés sur une roue de travail, caractérisé par le fait que les pistons moteurs (3) sont disposés à équidistance dans le canal de la roue de travail (2), qui s'étend tout autour en anneau, et partagent le canal en segments à dimension égale.
  4. Moteur à combustion interne à piston rotatif selon la revendication 3, caractérisé par le fait que la roue conjuguée est réalisée de telle façon que, durant la marche du moteur, sa vitesse angulaire est supérieure à la vitesse angulaire de la roue de travail associée.
  5. Moteur à combustion interne à piston rotatif selon l'une des revendications 1 à 4, caractérisé par le fait que l'on prévoit un arbre de sortie (8) dont l'axe de rotation (R) est identique à l'axe de rotation (R) de la roue de travail (2).
  6. Moteur à combustion interne à piston rotatif selon l'une des revendications 1 à 5, caractérisé par le fait que l'on prévoit un nombre de deuxièmes pales d'air (9) entraínables en rotation et destinées à une autre précompression de l'air ou du mélange air-carburant.
  7. Moteur à combustion interne à piston rotatif selon l'une des revendications 1 à 6, caractérisé par le fait que l'on prévoit un réservoir (12) destiné à recevoir l'air comprimé durant la marche par l'un des pistons moteurs (3) ou bien le mélange air-carburant comprimé, lorsque le piston moteur (3) passe à travers la roue conjuguée (4).
  8. Moteur à combustion interne à piston rotatif selon la revendication 7, caractérisé par le fait que le réservoir (12) est disposé dans la roue conjuguée.
  9. Moteur à combustion interne à piston rotatif selon l'une des revendications 1 à 8 comprenant au moins deux pistons moteurs (3) disposés sur une roue commune de travail ( 2), caractérisé par le fait que dans le carter (1) sont réalisées au moins une entrée (13) et une sortie (14) de telle manière qu'elles sont simultanément ouvertes dans des positions déterminées de rotation de deux pistons moteurs (3) voisins, de sorte que de l'air de balayage peut être introduit par l'entrée (13) dans l'espace formé entre les deux pistons moteurs (3) voisins, le carter (1) et la roue de travail (2) et peut expulser par la sortie (14) des gaz d'échappement éventuellement présents dans ledit espace.
  10. Moteur à combustion interne à piston rotatif selon l'une des revendications 1 à 9, caractérisé par le fait qu'il est réalisé en tant que moteur à plusieurs rangées avec au moins deux roues de travail (2) qui sont logées l'une derrière l'autre et de manière à pouvoir tourner autour d'un axe commun de rotation (R) et auxquelles est associée respectivement une roue conjuguée (4).
EP01993746A 2000-11-10 2001-11-08 Moteur a combustion interne a piston rotatif Expired - Lifetime EP1339952B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10055906 2000-11-10
DE10055906 2000-11-10
DE10119146 2001-04-19
DE10119146 2001-04-19
PCT/DE2001/004173 WO2002038917A1 (fr) 2000-11-10 2001-11-08 Moteur a combustion interne a piston rotatif

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EP1339952A1 EP1339952A1 (fr) 2003-09-03
EP1339952B1 true EP1339952B1 (fr) 2004-10-06

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Country Link
US (1) US6672274B2 (fr)
EP (1) EP1339952B1 (fr)
AT (1) ATE278868T1 (fr)
AU (2) AU1690502A (fr)
CA (1) CA2428565C (fr)
DE (2) DE10194849D2 (fr)
WO (1) WO2002038917A1 (fr)

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WO2005107552A2 (fr) * 2004-05-03 2005-11-17 Castronovo Charles A Aspirateurs particulierement silencieux, pompes et moteurs associes
US7059294B2 (en) * 2004-05-27 2006-06-13 Wright Innovations, Llc Orbital engine
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Publication number Publication date
CA2428565C (fr) 2007-08-28
EP1339952A1 (fr) 2003-09-03
CA2428565A1 (fr) 2002-05-16
AU2002216905B2 (en) 2005-08-04
DE10194849D2 (de) 2003-12-04
AU1690502A (en) 2002-05-21
US20030159674A1 (en) 2003-08-28
WO2002038917A1 (fr) 2002-05-16
US6672274B2 (en) 2004-01-06
DE50104043D1 (de) 2004-11-11
ATE278868T1 (de) 2004-10-15

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