EP0561855B1 - Machine a piston rotatif - Google Patents

Machine a piston rotatif Download PDF

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Publication number
EP0561855B1
EP0561855B1 EP92900081A EP92900081A EP0561855B1 EP 0561855 B1 EP0561855 B1 EP 0561855B1 EP 92900081 A EP92900081 A EP 92900081A EP 92900081 A EP92900081 A EP 92900081A EP 0561855 B1 EP0561855 B1 EP 0561855B1
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EP
European Patent Office
Prior art keywords
cam
rotating
piston machine
machine according
revolution
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 - Lifetime
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EP92900081A
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German (de)
English (en)
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EP0561855A1 (fr
Inventor
Jürgen SCHUKEY
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SITA Maschinenbau und Forschungs GmbH
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SITA Maschinenbau und Forschungs GmbH
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    • 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
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/063—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
    • F01C1/067—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them having cam-and-follower type drive

Definitions

  • the invention relates to a rotary piston machine with a housing, with a shaft mounted in the housing, with an annular space in which two rotating bodies are arranged and on the walls, in which inlet and outlet openings are provided for the working medium, the rotating bodies bear tightly, each Rotating body has radially outwardly extending sector-shaped wings, the two rotating bodies are arranged coaxially and their wings interlock so that one wing of the one rotating body is arranged between two wings of the other rotating body, with a cam track control is provided, by the rotation of the shaft execute both rotating bodies with cyclical changes in the rotational speed and the distances between the wings of the two rotating bodies and the cam track control first cam track control means in the form of first cam rings, second cam track control means i n Form of second cam rings and third cam track control means in the form of a cage with rolling elements which are held immovably in the circumferential direction and taper conically towards both end faces and roll on the first and second cam rings, one of the cam track control means with the shaft and another of the cam
  • the cam track control of the rotating bodies is carried out with two sets of elements, each of which has an inner cam ring, rolling bodies and an outer cam ring.
  • Two such sets of controls are required because the rolling elements can only be pressed outwards from the inner cam ring over a certain angular range (for example 45 °) and then these rolling elements in turn turn the outer cam ring by the outward force so that a torque of inner cam ring can be transferred to the outer cam ring. Then the rolling elements must be moved inwards again; no torque can be transferred from the inner cam ring to the outer cam ring during this time.
  • a second set of such a cam track control must therefore be provided, which effects the torque transmission in this angle of rotation range.
  • torques are to be transmitted from the outer cam ring to the inner cam ring.
  • the structure becomes relatively complex due to the large number of elements of the cam track control and increased friction losses can also occur.
  • the cam rings have a relatively complicated shape, so that their production is complex and expensive.
  • the object of the invention is to provide a rotary piston machine of the type mentioned, which is of simpler construction.
  • the solution according to the invention is that the rolling elements are provided with bevel gear teeth, that the surfaces of the cam tracks of the cam rings facing the rolling elements are arranged in a rotationally symmetrical surface corresponding to the surface of the rolling elements and are provided with corresponding internal bevel gear teeth, and that at most one for each rotating body Cam track control with a first and second outer cam ring and rolling elements is provided.
  • the rolling elements no longer transmit the torque from the first to the second cam ring or vice versa by moving outwards or inwards. Rather, they at least essentially maintain their radial position and transmit the torques by rotation with the aid of the toothings.
  • the rolling elements roll on the relatively narrow cam tracks which protrude from the surfaces of the cam rings facing the rolling elements. These surfaces lie in surfaces that have essentially the same double cone shape as the rolling elements and are also provided with toothing. Such essentially conical surfaces can be produced much more easily than the complicated curve shapes of the previously known rotary piston machine.
  • the surfaces of the cam rings facing the rolling elements as a whole can also be rotationally symmetrical or double-conical except for the above cam tracks, which also makes them easier to manufacture.
  • the teeth are involute teeth, the involute geometry of which is perpendicular to the axis of the rolling element.
  • involute toothing The advantages of involute toothing are known to the person skilled in the art. If the involute geometry is perpendicular to the axis of the rolling element and not, as is usually the case with bevel gears, perpendicular to the surface of the cone, you have a profile shift in addition to the center line of the cam track, in which the gears are still free from one another intervention. So you have a zero gear on the center line and V-zero gear on both sides (Decker, "Machine elements, design and calculation", Carl Hanser Verlag Kunststoff 1963, pp. 370-373).
  • the pressure angle is 20 ° according to DIN 867. If it is provided that the pressure angle is approximately 30 to 50 °, in particular approximately 35 to 40 °, not only the torques can be transmitted as desired by the cam rings and the rolling elements, but also radial forces can be absorbed.
  • the cam track controls can therefore serve as additional bearings. Under certain circumstances, it will even be possible to completely do without other bearings, which further simplifies the construction of the rotary piston machine.
  • cam rings are made up of two axially arranged halves, they are easier to manufacture. In addition, the cam track control can be put together more easily. If the cam rings are clamped together axially, which can be done by clamping and / or using appropriate springs, radial forces could act on the bearings of the rolling elements, e.g. if the inner cam rings exert a greater radial force than the outer cam rings. It is therefore expediently provided that the rolling elements, which cannot move in the circumferential direction, are held in bearings which can be displaced in the radial direction at least by a certain amount. In this case, the rolling elements can avoid the uneven forces.
  • the axes of the rolling elements in the bearings are expediently subjected to an elastic force in the direction of the axis of rotation. If no torques act, the axes assume the position adjacent to the axis of rotation without play. If the torque increases, the axes in the bearings can move outwards to a new limit position give in. In this way, the required backlash is achieved with a precisely defined maximum game.
  • the rotating bodies do not perform a net rotational movement against one another.
  • the number of teeth of the inner and outer cam ring is the same and is divisible by the number of wings.
  • Each cam track control advantageously has the same number of rolling elements as the number of vanes per rotating body.
  • the invention is not limited to the cases in which inner and outer cam rings are present, as is the case with the prior art (EP-B1-0 316 346).
  • the cam rings are rotatably connected to the shaft and the second cam rings to a rotating body and the cage is connected to the housing.
  • the first cam rings can be arranged radially on the inside of the rolling elements and the second cam rings enclose the first cam rings and the rolling elements.
  • the second cam rings are arranged radially on the inside of the rolling elements and the first cam rings are second and enclose the rolling elements.
  • the second cam rings have a smaller mass and a smaller moment of inertia, so that the mass to be accelerated and braked again and again is reduced.
  • first and second cam rings are arranged next to one another radially on the inside of the rolling elements. In this case, too, the forces or torques can be transmitted effectively due to the toothing, which would not be possible without toothing in this embodiment.
  • the rolling elements can be enclosed by a massive third cam ring, which can be freely rotated (except for the guidance through the toothing) and which can be decelerated or accelerated exactly against the accelerating and decelerating movements of the rotating elements in order to ensure a more even running .
  • the torque can first be transmitted from the first cam ring to the first part of the rolling element and from there to the massive third cam ring. From the latter, the torque is then transmitted further via the second part of the rolling element to the second cam ring and from there to the rotating element. In this case you get a larger number of translation levels.
  • first and second cam rings enclose the rolling elements; Both cam rings, which are arranged next to each other, work together with the rolling elements from the outside.
  • first cam rings are connected to the housing, the second cam rings are connected to a rotating body and the cage is connected to the shaft.
  • the torque is not transmitted from the shaft to the first cam rings, but to the cage that carries the rolling elements.
  • the gears and cam tracks are designed so that a maximum angular velocity of the one rotating body corresponds to a minimum angular velocity of the other rotating body, that the angular velocity maxima and minima are arranged at intervals of half the cycle duration, in have the same values in the middle between two extreme values, and that the change over time is a flattened function in the area of the maxima.
  • FIG. 1 shows the annular space 1 of a rotary piston machine of the invention, which is enclosed by parts of the housing 2.
  • the two interlocking rotating bodies, which act as impellers 3 and 4 are located in the annular space 1 are trained.
  • the impeller 3 has the vanes 3a, 3b, 3c and 3d, while the impeller 4 has the vanes 4a, 4b, 4c and 4d.
  • Both impellers are driven by a shaft 5 arranged in the center in a manner to be described.
  • 6a-h different inlet openings and outlet openings in the end wall of the annular space 1 are designated.
  • This mode of operation can be used both for a compressor and for an internal combustion engine. Only combustion rooms, fuel lines, etc. would have to be provided.
  • FIG. 3 one half of the machine according to the invention is shown in an axial section. The other half of the The machine continues essentially mirror-symmetrically to the left.
  • the drive shaft 5 is rotatably mounted in the housing 2 via a spacer sleeve 15 and radial and axial bearings 16, 17 and a housing flange 18. Outside the spacer sleeve 15 there is also a coupling flange 19 and a nut 20.
  • the inner of the spacer sleeve 15 is followed by the inner cam ring 7, which consists of two parts. To the left is a spacer sleeve 21, which leads to the corresponding inner cam ring 7 on the other side, which is intended for driving the other of the two rotating bodies.
  • the two halves of the inner cam rings 7 are now pressed together via the spacer sleeves 15 and 21 and by a corresponding counter-pressure element on the left side of the machine, not shown, so that the rolling elements 9 are pressed outwards against the outer cam rings 8.
  • These also consist of two halves and are rotatably arranged in a casing sleeve 22 which is connected to the rotating body 3.
  • Closure flanges 23 not only hold the outer cam rings 8 but also press them against one another in order to create a counterpressure for the pressure of the rolling elements 9 here.
  • the halves of the inner rings 7 or outer rings 8 can also be pressed together via spring elements.
  • the cage 14, in which the rolling elements 9 are mounted, is finally fastened to the housing flange 18 and is connected in a rotationally fixed manner to the cage on the other side of the arrangement via a spline toothing 24.
  • the cage is fixed against the housing 2 in the circumferential direction.
  • the angle setting of the cage 14 with respect to the housing can, however, still be changed in that the angular position of the housing flange 18 with respect to the housing 2 is changed by an adjustment bearing 25.
  • the rolling elements 9 are not mounted directly in the cage 14, but in outside cuboid-shaped bearings 50 which are received in corresponding grooves of the cage 14 so that they have no play in the circumferential direction, but can move a little back and forth in the radial direction. This enables the rolling elements 9 to be pressed outwards during tensioning.
  • the housing 2 is composed of two halves, the seal 31 being provided at the dividing line 33 thereof. If the sealing effect between the vanes of the rotating bodies 3, 4 and the wall of the annular space 1 deteriorates, tightening a bolt guided through the bore 34 can ensure that the two housing halves are moved closer together, as a result of which better contact between the housing walls and Rotational bodies 3, 4 is given in the annular space, whereby the sealing effect is improved.
  • the rolling elements 9 designed in the form of a double cone are provided with bevel gear teeth 51. This involves involute toothing, the involute plane being perpendicular to the axis of the rolling elements 9.
  • the inside of the cam rings 7 and 8 essentially have a similar surface to the outer surface of the rolling elements 9. However, there are gaps 52 between the rings 7, 8 on the one hand and the rolling element 9 on the other hand. Rings 7, 8 on the one hand and rolling elements 9 on the other only touch in the Area of the cam tracks 53, which are provided on the inner surfaces of the cam rings 7, 8 as elongate projections, which have an involute toothing on their surface which corresponds to that of the rolling elements 9.
  • the teeth not only of the rolling elements 9, but also of the cam tracks 53, have one Bevel gear toothing corresponds to a larger module or a larger pitch in the middle than towards the axial ends of the rolling element 9.
  • the cam tracks 53 have different distances from the center plane.
  • the transmission ratio changes both from the inner cam ring 7 to the rolling element 9 and from the rolling element 9 to the outer cam ring 8. If the shaft 5 is now driven, the inner ring 7 rotates uniformly with it.
  • the rolling element 9 will assume a changing rotational speed, depending on how far the cam track 53 is at the point of contact between the rolling element 9 and the inner ring 7 just from the center line.
  • the transmission ratio between the rolling element 9 and the outer ring also varies accordingly, so that the rotating body 3 performs the desired, non-uniform rotary movement.
  • the embodiment of FIG. 3 has four rolling elements 9, two of which are visible in the figure. Two further rolling elements 9 are located at an angular distance of 90 ° in front of the drawing plane and behind the drawing plane.
  • the cam tracks 53 have a profile (distance from the center plane as a function of the angle around the center axis of the rolling element 9) which has a period of 90 °.
  • the cam track 53 has a distance from the central plane that varies with the angle.
  • the involute toothing 54 has a larger module (pitch, tooth spacing) near the center line (at B) than in the outer area (at A).
  • FIG. 5 corresponds essentially to the embodiment of FIG. 3.
  • the housing 2 therefore only needs have a relatively small bore through which the second cam ring 8 and the rotating body 4 are connected on the circumference of the shaft 5.
  • a seal 55 arranged here therefore, only relatively low relative peripheral speeds take place, so that the seal wears less.
  • the first cam ring 7, which is connected directly to the shaft 5, is arranged outside the rolling elements 9. There is a better engagement between these two parts, which enables a better transmission of the torque to the rolling elements 9.
  • the second cam ring 8 is arranged within the rolling elements 9 and is connected again to the rotating element 4. The advantage is that the non-uniformly moving mass is smaller than in the first embodiment.
  • the first cam ring 7 is arranged next to the second cam ring 8; both cam rings are arranged within the rolling element 9.
  • the first cam ring 7 is connected to the shaft 5, the second cam ring 8 with the rotating body 4 in a rotationally fixed manner.
  • the torque transmission takes place without an outer cam ring.
  • apart from the toothing freely rotatable cam ring 64 is provided, which is moved in opposite directions to the rotating body 4 and accelerated or decelerated so that the machine runs more smoothly.
  • the rotating body 9 is constructed from two parts and is mounted on a central axis 57 with a stepped bearing 56.
  • the central axis 57 is supported in cuboid bearings 50, which are not in the circumferential direction, but a little in the radial direction can move outwards against the force of a spring 58. If no torques are transmitted, the bearings 50 are located radially on the inside and are then pressed outwards at higher torques against the force of the spring or springs 58, but there are limits to this outward movement.
  • the bearings 50, the axis 57 of the rotating bodies and the spring 58 are shown even more clearly in FIG. 8.
  • the stop surface 59 which limits the radially outward movement of the bearing part 50, can also be seen there.
  • the rolling element consists of two parts 9a and 9b, between which bearings 60 are arranged.
  • the torque is transmitted from the shaft 5 to the first cam ring 7, from there to the left rolling element part 9a and from there to the outer massive cam ring 64, which again counteracts or compensates for torque fluctuations or rotational accelerations of the rotating body 4.
  • the torque is then transmitted from the massive cam ring 64 to the right part 9b of the rolling element and from there to the inner second cam ring 8, which in turn is connected to the rotating body 4. You have a double translation here.
  • both the first cam ring 7 and the second cam ring 8 act on the outside of the rolling element 9. This results in a more reliable torque transmission from the cam rings to the rolling element and vice versa, since the rolling element 9 nestles into corresponding curvature surfaces of the cam rings 7 and 8, while in the case of an inner cam ring there is more or less point contact.
  • the first cam ring 7 is connected to the shaft 5, the second cam ring 8 with the rotating body 4 in a rotationally fixed manner.
  • the first cam ring 7 is connected to the housing 2.
  • the torque from the shaft 5 is transferred to the associated cage 14, which rotates with the shaft 5.
  • the torque is then transmitted via the freely rotatable rolling element 9 to the second cam ring 8, which in turn is connected to the rotating element 4.
  • the inner ring (only one inner ring half is shown), e.g. the inner ring 7 of the embodiment of FIGS. 1 to 4, as shown in FIG. 13, is provided with bevel gear teeth 54 in the pointed part and with cam track teeth 53 in the part further to the end of the truncated cone. This prevents the teeth from having very large gaps at the end of the truncated cone.
  • the rolling element 9 or the rolling element half 9, which is shown in FIG. 12, is of exactly complementary design.
  • the interrupted cam tracks 53 continue analogously in the other part.
  • the diagram in FIG. 14 shows that in the course of a cycle (0-1 on the t-axis) the angular velocity of the two cam rings 8 moves back from a minimum value to a maximum value and then back to a minimum value. After half a period, the minimum value of one curve ring has changed to the maximum value and vice versa. Exactly in the middle between the maximum values, both reach half the value. In the area of the maxima and minima, the curves are not pointed, but flattened, so that there is a longer period for gas exchange.

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  • Engineering & Computer Science (AREA)
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  • General Engineering & Computer Science (AREA)
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  • Iron Core Of Rotating Electric Machines (AREA)
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Claims (20)

  1. Machine à piston rotatif, comprenant un carter (2), un arbre (5) monté à rotation dans le carter (2), une chambre annulaire (1) dans laquelle sont disposés deux corps de révolution (3, 4) et dont les parois, dans lesquelles sont prévus des orifices (6a-6h) d'admission et d'échappement du fluide moteur, sont en contact étanche avec les corps de révolution (3, 4), chaque corps de révolution (3, 4) présentant des aillettes (3a-3d, 4a-4d) en forme de secteur qui s'étendent radialement vers l'extérieur, les deux corps de révolution (3, 4) étant disposés coaxialement et leurs aillettes étant intercalées de sorte que chaque ailette de l'un des corps de révolution soit disposée entre deux aillettes de l'autre corps de révolution, une commande par cames (7, 8, 9) étant prévue de telle manière que, lorsque l'arbre (5) tourne, les deux corps de révolution (3, 4) effectuent des rotations avec des modifications cycliques de la vitesse de rotation et des distances entre les aillettes des deux corps de révolution, la commande par cames comprenant un premier moyen de commande par cames sous forme de premières cames annulaires (7), un deuxième moyen de commande par cames sous forme de deuxièmes cames annulaires (8) et un troisième moyen de commande par cames sous forme d'une cage (14) munie de corps roulants (9) qui y sont maintenus sans possibilité de déplacement en direction circonférentielle, s'amincissent en cône vers leurs deux surfaces d'extrémité et roulent sur les premières cames annulaires (7) et sur les deuxièmes cames annulaires (8), l'un (7, 8, 14) des moyens de commande par cames étant solidaire en rotation de l'arbre (5), un autre (7, 8, 14) des moyens de commande par cames étant solidaire en rotation de l'un des corps de révolution (3, 4) et le moyen de commande par cames restant (7, 8, 14) étant fixé au carter (2), caractérisée en ce que les corps roulants (9) sont munis de dentures de roue conique (51), en ce que les surfaces des pistes (53) des cames annulaires (7, 8), dirigées vers les corps roulants (9), sont situées sur une surface à symétrie de révolution qui correspond à la surface des corps roulants, et sont munies de dentures de roue conique (54) correspondantes, et en ce qu'il est prévu, pour chaque corps de révolution (3, 4), au maximum une commande par cames comportant une première et deuxième came annulaire (7, 8) et des corps roulants (9).
  2. Machine à piston rotatif selon la revendication 1, caractérisée en ce qu'il est prévu, pour chaque corps de révolution (3, 4), une commande par came (7, 8, 9, 51, 52).
  3. Machine à piston rotatif selon la revendication 1 ou 2, caractérisée en ce que les cames annulaires (7, 8), à l'exception des pistes de came (53), ont essentiellement une forme à symétrie de révolution.
  4. Machine à piston rotatif selon l'une quelconque des revendications 1 à 3, caractérisée en ce que les dentures (51, 54) sont des dentures à développante dont la géométrie de développante est perpendiculaire à l'axe du corps roulant (9).
  5. Machine à piston rotatif selon l'une quelconque des revendications 1 à 4, caractérisée en ce que les cames annulaires (7, 8) sont constituées par deux moitiés disposées l'une après l'autre en direction axiale.
  6. Machine à piston rotatif selon la revendication 5, caractérisée en ce que les corps roulants (9) sont montés dans des paliers (50) qui sont déplaçables en direction radiale.
  7. Machine à piston rotatif selon la revendication 6, caractérisée en ce que les axes des corps roulants (9) dans les paliers (50) sont sollicités par une force élastique en direction de l'axe de rotation.
  8. Machine à piston rotatif selon la revendication 7, caractérisée en ce que la force élastique est la force d'un ressort, la pression d'un gaz ou une pression hydraulique.
  9. Machine à piston rotatif selon l'une quelconque des revendications 1 à 8, caractérisée en ce que le nombre des dents de la came annulaire interne et de la came annulaire externe (7, 8) est le même et est divisible par le nombre des aillettes (3a, 3b, 3c, 3d).
  10. Machine à piston rotatif selon l'une quelconque des revendications 1 à 9, caractérisée en ce que le nombre des corps roulants (9) de chaque commande par cames (7, 8, 9, 51, 52) est divisible par le nombre des ailettes du corps de révolution (3, 4).
  11. Machine à piston rotatif selon l'une quelconque des revendications 1 à 10, caractérisée en ce que les premières cames annulaires (7) sont solidaires en rotation à l'arbre (5), les deuxièmes cames annulaires (8) sont solidaires en rotation d'un corps de révolution (3, 4) et la cage (14) est fixée au carter.
  12. Machine à piston rotatif selon la revendication 11, caractérisée en ce que les premières cames annulaires (7) sont disposées radialement en dedans des corps roulants (9) et les deuxièmes cames annulaires (8) entourent les premières cames annulaires (7) et les corps roulants (9).
  13. Machine à piston rotatif selon la revendication 11, caractérisée en ce que les deuxièmes cames annulaires (8) sont disposées radialement en dedans des corps roulants (9) et les premières cames annulaires (7) entourent les deuxièmes cames annulaires (8) et les corps roulants (9).
  14. Machine à piston rotatif selon la revendication 11, caractérisée en ce que les premières cames annulaires (7) et deuxièmes cames annulaires (8) sont disposées côte à côte, radialement en dedans des corps roulants (9).
  15. Machine à piston rotatif selon la revendication 14, caractérisée en ce que les corps roulants sont entourés par une troisième came annulaire (64) de grande dimension.
  16. Machine à piston rotatif selon la revendication 15, caractérisée en ce que les corps roulants (9) se composent de deux parties (9a, 9b) qui peuvent tourner indépendamment l'une de l'autre.
  17. Machine à piston rotatif selon la revendication 11, caractérisée en ce que les premières cames annulaires (7) et deuxièmes cames annulaires (8) entourent les corps roulants (9).
  18. Machine à piston rotatif selon l'une quelconque des revendications 1 à 10, caractérisée en ce que les premières cames annulaires (7) sont fixées au carter, les deuxièmes cames annulaires (8) sont fixées à un corps de révolution (3, 4) et la cage (14) est fixée à l'arbre (5).
  19. Machine à piston rotatif selon l'une quelconque des revendications 1 à 18, caractérisée en ce que les surfaces coniques des corps roulants (9) et des cames annulaires (7, 8, 64) présentent chacune, par moitié, des dentures de roue conique (54) et des pistes de came surélevées (53).
  20. Machine à piston rotatif selon l'une quelconque des revendications 1 à 19, caractérisée en ce que les dentures (54) et les pistes de came (53) sont réalisées de telle sorte qu'une vitesse angulaire maximale de l'un des corps de révolution (3, 4) corresponde chaque fois à une vitesse angulaire minimale de l'autre corps de révolution (4, 3), en ce que les maximums et les minimums de vitesse angulaire sont situés chaque fois à distance de la demi-durée de cycle et ont des valeurs égales au milieu entre deux valeurs extrêmes, et en ce que, dans la région des maximums, la variation dans le temps est une fonction aplatie.
EP92900081A 1990-12-12 1991-12-04 Machine a piston rotatif Expired - Lifetime EP0561855B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE9016807U 1990-12-12
DE9016807U DE9016807U1 (de) 1990-12-12 1990-12-12 Drehkolbenmaschine
PCT/EP1991/002317 WO1992010648A1 (fr) 1990-12-12 1991-12-04 Machine a piston rotatif

Publications (2)

Publication Number Publication Date
EP0561855A1 EP0561855A1 (fr) 1993-09-29
EP0561855B1 true EP0561855B1 (fr) 1994-08-10

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EP92900081A Expired - Lifetime EP0561855B1 (fr) 1990-12-12 1991-12-04 Machine a piston rotatif

Country Status (11)

Country Link
US (1) US5326238A (fr)
EP (1) EP0561855B1 (fr)
JP (1) JP2915141B2 (fr)
KR (1) KR930703524A (fr)
CN (1) CN1042663C (fr)
AT (1) ATE109868T1 (fr)
AU (1) AU9025391A (fr)
BR (1) BR9107160A (fr)
DE (2) DE9016807U1 (fr)
DK (1) DK0561855T3 (fr)
WO (1) WO1992010648A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0945592A1 (fr) 1998-03-25 1999-09-29 Jürgen SCHUKEY Machine à piston rotatif

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6289867B1 (en) 1999-03-31 2001-09-18 Cummins Engine Company, Inc. Rotary engine
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EP0945592A1 (fr) 1998-03-25 1999-09-29 Jürgen SCHUKEY Machine à piston rotatif

Also Published As

Publication number Publication date
WO1992010648A1 (fr) 1992-06-25
DE9016807U1 (de) 1992-04-09
CN1042663C (zh) 1999-03-24
AU9025391A (en) 1992-07-08
JPH06503392A (ja) 1994-04-14
CN1063141A (zh) 1992-07-29
EP0561855A1 (fr) 1993-09-29
JP2915141B2 (ja) 1999-07-05
KR930703524A (ko) 1993-11-30
ATE109868T1 (de) 1994-08-15
DE59102530D1 (de) 1994-09-15
DK0561855T3 (da) 1994-12-05
US5326238A (en) 1994-07-05
BR9107160A (pt) 1994-03-22

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