EP0561855B1 - Rotating piston machine - Google Patents

Abstract

PCT No. PCT/EP91/02317 Sec. 371 Date Aug. 5, 1993 Sec. 102(e) Date Aug. 5, 1993 PCT Filed Dec. 4, 1991 PCT Pub. No. WO92/10648 PCT Pub. Date Jun. 25, 1992.A shaft (5) is driven in the rotary piston machine. The torque is transmitted via first cam rings (7), connected to it, to rolling bodies (9) supported in cages and from these rolling bodies to second cam rings (8), which drive the rotation bodies (3) of the rotary piston machine. The cam rings (7, 8) and the rolling bodies (9) are, in this case, partially provided with bevel-wheel teeth and partially with cam track teeth (FIG. 3 ). The rotary piston machine can also be used as an engine and is characterised by a particularly high efficiency.

Description

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 track control means with one of the rotational bodies is non-rotatably and the remaining one of the cam track control means is connected to the housing.

In such a rotary piston machine (EP-B1-0 316 346), 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. The same applies, of course, if torques are to be transmitted from the outer cam ring to the inner cam ring. It is understood that the structure becomes relatively complex due to the large number of elements of the cam track control and increased friction losses can also occur. In addition, 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.

Instead of two of the sets of elements mentioned, you only need one set. 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.

Although it is conceivable that only one rotary body is provided with a cam track control, such a cam track control is expediently provided for each of the rotary bodies.

So that the cam track control works without play, it is expediently provided that the teeth are involute teeth, the involute geometry of which is perpendicular to the axis of the rolling element.

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 Munich 1963, pp. 370-373).

In involute gears, 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.

If the 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.

In most cases it will be intended that the rotating bodies do not perform a net rotational movement against one another. For this purpose it is advantageously provided that the number of teeth of the inner and outer cam ring is the same and is divisible by the number of wings. During operation, the rolling element will then interact with its middle region with the outer cam ring and with its end regions with the inner ring.

Each cam track control advantageously has the same number of rolling elements as the number of vanes per rotating body.

It is easily possible to connect the outer cam rings to the corresponding rotating bodies so that the connection is completely present in the part near the axis. The seal surrounding the corresponding connecting part can therefore also be made relatively small and wears little since relatively low relative speeds between rotation and rotating parts occur here.

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). Advantageously, but not necessarily, it can be provided that 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. In this case, as is the case in the prior art, 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. According to the invention, however, it can also be provided that 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. Because of the engagement of the first cam rings with the rolling elements over a larger angular range in this case, the possibly considerable torque can be better transmitted from the shaft to the rolling elements. In addition, 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.

In a further advantageous embodiment it can be provided that the 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.

In this case there is no cam ring outside the rolling elements. However, 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 .

If the rolling elements consist of two parts which can be rotated independently of one another, in the latter case 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.

In a further embodiment it can be provided that the 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.

In another advantageous embodiment, the 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. In this case, the torque is not transmitted from the shaft to the first cam rings, but to the cage that carries the rolling elements.

Since the tooth spacing of the teeth increases with increasing diameter towards the end of the truncated cone, problems can arise here. These large distances can be avoided if the tapered surfaces of the rolling elements and the cam rings each have half bevel gear teeth and half have raised cam tracks. The cam track is interrupted, so to speak, and continues after a certain angular range on one surface on the other surface of the other part.

For smooth running, it is very important that 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

einen Schnitt durch eine Radialebene des Ringraums einer Drehkolbenmaschine der Erfindung mit den beiden Rotationskörpern;

Fig. 2

die beiden Rotationskörper in verschiedenen Stellungen;

Fig. 3

eine Hälfte der Maschine im Querschnitt;

Fig. 4

die Kurvenbahn auf der Oberfläche des inneren Kurvenrings;

Fig. 5

im Schnitt eine etwas abgewandelte Ausführungsform der Drehkolbenmaschine der Fig. 1;

Fig. 6

im Querschnitt eine andere Ausführungsform;

Fig. 7

noch eine andere Ausführungsform im Schnitt;

Fig. 8

einen Querschnitt entlang der Linie VIII-VIII von Fig. 7;

Fig. 9

im Querschnitt noch eine weitere Ausführungsform;

Fig. 10

im Querschnitt noch eine weitere Ausführungsform;

Fig. 11

eine noch andere Ausführungsform im Querschnitt;

Fig. 12

im Axialschnitt eine andere Art der Verzahnung bzw. Kurvenbahnen;

Fig. 13

einen Kurvenring mit der abgewandelten Verzahnung bzw. Kurvenbahn der Fig. 12; und

Fig. 14

eine graphische Darstellung der zeitlichen Änderung der Winkelgeschwindigkeit der Kurvenringe.

The invention is described below with reference to advantageous embodiments with reference to the accompanying drawings. Show it:

Fig. 1

a section through a radial plane of the annular space of a rotary piston machine of the invention with the two rotating bodies;

Fig. 2

the two rotating bodies in different positions;

Fig. 3

half of the machine in cross section;

Fig. 4

the cam track on the surface of the inner cam ring;

Fig. 5

in section a somewhat modified embodiment of the rotary lobe machine of FIG. 1;

Fig. 6

in cross section another embodiment;

Fig. 7

yet another embodiment in section;

Fig. 8

a cross-section along the line VIII-VIII of Fig. 7;

Fig. 9

in cross section yet another embodiment;

Fig. 10

in cross section yet another embodiment;

Fig. 11

yet another embodiment in cross section;

Fig. 12

a different type of toothing or curved tracks in axial section;

Fig. 13

a cam ring with the modified toothing or cam track of Fig. 12; and

Fig. 14

a graphic representation of the temporal change in the angular velocity of the cam rings.

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. With 6a-h different inlet openings and outlet openings in the end wall of the annular space 1 are designated.

The operation of this arrangement is as follows. If the shaft 5 moves counterclockwise, the impellers 3 and 4 are rotated clockwise at different speeds in a manner still to be described. In the position shown, for example, the impeller 4 would rotate clockwise faster than the impeller 3. In this case, the working space between the vanes 3d and 4a would increase, so that gas is sucked in through the inlet duct 6a. At a later point in time, this inlet channel 6a is then closed by the slowly following wing 3d. From about this moment, the wing 3d begins to move faster than the wing 4a, so that the working space between the two wings is reduced and the gas is compressed until both wings have moved so far that the working space has reached the outlet opening 6b , so that the gas can escape here. At this point in time, the wing 3d can be brought up to the wing 4a, so that the gas is pushed out completely here.

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.

2 shows four phases of the work cycle just described. After the 90 ° rotation of the two rotating bodies, a new work cycle begins.

In 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.

By tightening the nut 20, 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. In this way, 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.

At 26 to 30 seals are shown, at 31 another seal between the housing halves. 32 is finally a sliding sleeve between cage 14 and rotor 3.

As said, 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. In the circumferential direction, the cam tracks 53 have different distances from the center plane. As a result, 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 °.

4 shows the curved path of the outer surface of one half of an inner curved ring 7. As clearly visible, 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).

5 to 11 only the surroundings of a rolling element 9 are shown in order to illustrate the operation of other embodiments. Compared to FIG. 1, the relationships to the left of the center plane of the machine are also shown.

The embodiment of FIG. 5 corresponds essentially to the embodiment of FIG. 3. Here, only the outer cam ring 8 is not connected to the rotary body 4 in the vicinity of its circumference, but rather in the vicinity of the shaft 5. 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. In the area of a seal 55 arranged here, therefore, only relatively low relative peripheral speeds take place, so that the seal wears less.

In the embodiment of FIG. 6, 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.

In the embodiment of FIG. 7, 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. Here, however, 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.

In the figure it can also be seen that 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.

In the embodiment of FIG. 9, 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.

In the embodiment of FIG. 10, 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.

In the embodiment of FIG. 11, 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.

In the embodiment of Figures 12 and 13, 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.

Claims (20)

1. Rotating-piston machine with a housing (2), with a shaft (5) mounted in the housing (2), and with an annular space (1), in which two bodies of revolution (3, 4) are arranged and against the walls of which, in which inlet and outlet orifices (6a-6h) for the working medium are provided, the bodies of revolution (3, 4) bear sealingly, each body of revolution (3, 4) having radially outward-extending sector-shaped vanes (3a-3d, 4a-4d), the two bodies of revolution (3, 4) being arranged coaxially, and their vanes engaging into one another in such a way that a vane of one body of revolution is respectively arranged between two vanes of the other body of revolution, there being provided a cam-track control (7, 8, 9), by means of which, during the rotation of the shaft (5), the two bodies of revolution (3, 4) execute rotations with cyclic changes of the rotational speed and of the distances between the vanes of the two bodies of revolution, and the cam-track control having first cam-track control means in the form of first cam rings (7), second cam-track control means in the form of second cam rings (8), and third cam-track control means in the form of a cage (14) with rolling bodies (9) which are held therein so as to be non-displaceable in a circumferential direction and taper conically towards the two end faces and which roll on the first (7) and second (8) cam rings, one (7, 8, 14) of the cam-track control means being connected fixedly in terms of rotation to the shaft (5) and another (7, 8, 14) of the cam-track control means being connected fixedly in terms of rotation to one of the bodies of revolution (3, 4) and the remaining cam-track control means (7, 8, 14) being connected to the housing (2), characterized in that the rolling bodies (9) are provided with bevel-wheel toothings (51), in that the surfaces, directed towards the rolling bodies (9), of the cam-tracks (53) of the cam rings (7, 8) are arranged in a rotationally symmetrical face corresponding to the surface of the rolling bodies (9) and are provided with corresponding bevel-wheel toothings (54), and in that at most one cam-track control with a first and a second cam ring (7, 8) and with rolling bodies (9) is provided for each body of revolution (3, 4).
2. Rotating-piston machine according to Claim 1, characterized in that one cam-track control (7, 8, 9, 51, 52) is provided for each body of revolution (3, 4).
3. Rotating-piston machine according to Claim 1 or 2, characterized in that, with the exception of the cam-tracks (53), the cam rings (7, 8) are essentially rotationally symmetrical.
4. Rotating-piston machine according to one of Claims 1 to 3, characterized in that the toothings (51, 54) are involute toothings, the involute geometry of which is perpendicular to the axis of the rolling body (9).
5. Rotating-piston machine according to one of Claims 1 to 4, characterized in that the cam rings (7, 8) are constructed from two halves arranged axially in succession.
6. Rotating-piston machine according to Claim 5, characterized in that the rolling bodies (9) are held in mountings (50) which are displaceable in the radial direction.
7. Rotating-piston machine according to Claim 6, characterized in that the axles of the rolling bodies (9) in the mountings (50) are loaded with an elastic force in the direction of the axis of rotation.
8. Rotating-piston machine according to Claim 7, characterized in that the elastic force is a spring force, a gas pressure or a hydraulic pressure.
9. Rotating-piston machine according to one of Claims 1 to 8, characterized in that the number of teeth of the inner and outer cam ring (7, 8) is equal and is divisible by the number of vanes (3a, 3b, 3c, 3d).
10. Rotating-piston machine according to one of Claims 1 to 9, characterized in that the number of rolling bodies (9) of each cam-track control (7, 8, 9, 51, 52) is divisible by the number of vanes of the body of revolution (3, 4).
11. Rotating-piston machine according to one of Claims 1 to 10, characterized in that the first cam rings (7) are connected fixedly in terms of rotation to the shaft (5) and the second cam rings (8) are connected fixedly in terms of rotation to a body of revolution (3, 4), and the cage (14) is connected to the housing.
12. Rotating-piston machine according to Claim 11, characterized in that the first cam rings (7) are arranged radially on the inside of the rolling bodies (9) and the second cam rings (8) surround the first cam rings (7) and the rolling bodies (9).
13. Rotating-piston machine according to Claim 11, characterized in that the second cam rings (8) are arranged radially on the inside of the rolling bodies (9) and the first cam rings (7) surround the second cam rings (8) and the rolling bodies (9).
14. Rotating-piston machine according to Claim 11, characterized in that the first (7) and second (8) cam rings are arranged next to one another radially on the inside of the rolling bodies (9).
15. Rotating-piston machine according to Claim 14, characterized in that the rolling bodies are surrounded by a high-mass third cam ring (64).
16. Rotating-piston machine according to Claim 15, characterized in that the rolling bodies (9) consist of two parts (9a, 9b) rotatable independently of one another.
17. Rotating-piston machine according to Claim 11, characterized in that the first (7) and second (8) cam rings surround the rolling bodies (9).
18. Rotating-piston machine according to one of Claims 1 to 10, characterized in that the first cam rings (7) are connected to the housing, the second cam rings (8) are connected to a body of revolution (3, 4) and the cage (14) is connected to the shaft (5).
19. Rotating-piston machine according to one of Claims 1 to 18, characterized in that the conical faces of the rolling bodies (9) and of the cam rings (7, 8, 64) respectively have by half bevel-wheel toothings (54) and raised cam-tracks (53).
20. Rotating-piston machine according to one of Claims 1 to 19, characterized in that the toothings (54) and the cam tracks (53) are designed so that a maximum angular speed of one body of revolution (3, 4) corresponds respectively to a minimum angular speed of the other body of revolution (4, 3), in that the angular-speed maxima and minima are arranged respectively at intervals of half the cycle duration, have equal values in the middle between two extreme values, and in that, in the region of the maxima, the time change is a flat-topped function.

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