EP2655801B1 - Rotary piston machine operating as a pump, a compressor or a motor - Google Patents

Description

State of the art

The present invention relates to a rotary piston machine which works as a pump, compressor or motor, with a rotor and a counter rotor.

From the DE 42 41 320 A1 a rotary piston machine is known that works as a pump, compressor or motor. In this case, combs of teeth of a rotating drive part to delimit working spaces run on a cycloid surface of a likewise toothed output part and in the process drive this output part. The working spaces mentioned are formed between the teeth of the drive part and the driven part and are enlarged or reduced for their work during the rotation of the parts in order to generate the conveying effect on a gaseous or liquid medium.

From the US 758 214 A another rotary piston machine is known. In this, too, combs of teeth of a rotating drive part to delimit working spaces run on a surface of a likewise toothed output part and in the process drive this output part. The working spaces mentioned are formed between the teeth of the drive part and the driven part and are enlarged or reduced in size for their work during the rotation of the parts in order to generate the conveying effect on a medium. The drive part and the driven part have a spherical cap and a complementarily shaped support surface for mutual support.

Such drive and output parts run in a common housing, the interior of which is spherical. To assemble these parts, the housing is divided in such a way that the parting plane contains the center point of the spherical interior, so that a first housing part with a hemispherical interior with a first center and a second housing part with a hemispherical interior and a second center result. As a result, special attention must be paid to the design of the separating surfaces of the two housing parts in such a way that, in the assembled state, the first and second center points of the spherical interior spaces of the housing parts coincide. Since the two center points coincide by chance for manufacturing reasons, the gap resulting between the drive part or output part and the housing is adapted to the manufacturing technology and correspondingly generously dimensioned.

Summary of the invention

There may be a need to specify a rotary piston machine in which the gap between the housing and the drive part or output part is minimized.

This need can be solved by the respective subject matter of the independent claims. Advantageous refinements are given in the dependent claims.

A rotary piston machine that works as a pump, compressor or motor has a rotor and a counter-rotor, the counter-rotor being arranged opposite the rotor. The rotor has a first end face with a first toothing and the counter rotor has a second end face with a second toothing, the first and the second toothing each being formed from at least one tooth and one tooth gap. The toothings are in engagement with one another in such a way that by meshing the teeth of the first toothing and the teeth of the second toothing, working spaces are formed, with volumes formed by the working spaces being changed by the meshing of the teeth. The rotor has a first axis of rotation and the counter rotor has a second axis of rotation. The first axis of rotation and the second axis of rotation enclose an angle that is not equal to 0 degrees. In an embodiment that does not fall within the scope of protection of the claim, the rotor has a first spherical inner wall and the counter rotor has a first spherical outer contour which is complementary to the first spherical inner wall of the rotor.

According to the invention, the counter-rotor has a second spherical-ring-shaped inner wall and the rotor has a second spherical-ring-shaped outer contour which is designed to be complementary to the second spherical-ring-shaped inner wall of the counter-rotor.

In the following, the advantages of the invention are explained using the rotary piston machine, which does not fall within the scope of protection of the claim, ie using the rotor with the first spherical inner wall and the counter-rotor with the first spherical outer contour. These advantages also result in an embodiment in which the counter rotor has a second spherical ring-shaped inner wall and the rotor has a second spherical ring-shaped outer contour. It can be seen as an advantage of the invention that the originally intended delimitation of the working space by an inner wall of the housing is now effected by the rotor. In this way, the number originally necessary to limit the working space of three components, namely rotor, counter-rotor and housing, can be reduced to just two components, namely rotor and counter-rotor. The spherical ring-shaped housing inner wall which was originally implemented in the housing and required for the functioning of the rotary piston machine is now implemented in the rotor. Since a rotor-counter-rotor arrangement is designed to be relatively compact and smaller than the housing, dimensional accuracy can be implemented more easily. Due to the topography requirement, the rotor and counter rotor are already made of high quality material, preferably high quality plastics, with an accurate shape. Thus, the gap now resulting between the spherical ring-shaped inner wall and the spherical ring-shaped outer contour can be made as small as possible. This largely eliminates gap losses. Due to the high-precision manufacture of the rotors, an adjustment process by means of grinding in or adjustment with respect to the rotor and counter-rotor can therefore be dispensed with. Since the first spherical inner wall now rotates and does not stand still, as is the case with the housing inner wall of the stationary housing, a gaseous or liquid medium to be compressed is exposed to less wall friction than on this housing inner wall. As a result of the rotation of the first spherical ring-shaped inner wall, the laminar flow that forms on this inner wall is subjected to less dynamics. This can lead to a distance between the first spherical inner wall of the rotor and an interface that separates the laminar flow from a turbulent flow being greater than in the case of a housing inner wall from a stationary housing. Since the laminar flow is less energetic than the turbulent flow, due to these fluid mechanical relationships alone, lower gap losses could result in the proposed solution compared to the previously known solution with the same gap size, with the gap size being the shortest distance between the outer wall of the counter-rotor and the inner wall of the rotor or the shortest distance between the outer wall of the known rotor-counter-rotor arrangement and the inner wall of the housing.

In an exemplary embodiment that does not fall within the scope of the claim, the rotor of the rotary piston machine has a first wall area delimited by the first spherical inner wall and by a first outer wall. The first outer wall is designed as a first straight circular cylinder. A first housing, in which the rotor is rotatably mounted, has a first housing inner wall which, at least in a partial area of the rotor, has the shape of a second straight circular cylinder. The first straight circular cylinder is at least partially enclosed by the second straight circular cylinder.

To accommodate the rotor, the housing no longer has to have a spherical interior, but can instead be made in the form of a straight circular cylinder. This is a geometric shape that is easy to produce and can be manufactured with almost any diameter and within any tolerance. In the simplest case, this shape could even be made by drilling.

In the invention, the end of the housing can be locked in a rotationally fixed manner with a cover in which the counter rotor is rotatably mounted. The storage can be done, for example, by roller or plain bearings. As a rule, the bearings are designed in such a way that they can absorb the forces generated radially and axially by the counter rotor during operation. In addition, in this configuration, with a rotor already mounted in the housing, either the counter-rotor can be pre-assembled with the rotor in order to finally close the housing with the cover, or the counter-rotor can be pre-assembled with the cover in order to attach this pre-assembled combination to the front of the housing attach.

In an exemplary embodiment not falling within the scope of the claim, a medium to be compressed can be fed radially to the housing and / or removed radially from the housing.

In the invention, the counter rotor has a second wall area delimited by the second spherical ring-shaped inner wall and a second outer wall. The second outer wall is designed as a third straight circular cylinder, with a second housing, in which the counter rotor is rotatably mounted, having a second housing inner wall which, at least in a partial area of the counter rotor, has the shape of a fourth straight circular cylinder, the third straight circular cylinder from the fourth straight circular cylinder is at least partially enclosed.

It has already been explained above that such circular cylindrical shapes can be produced with little effort.

In a further exemplary embodiment of the invention, at least one first control opening is formed in the wall area transversely to the axis of rotation of the rotary piston machine.

This first control opening can be formed either in the first wall area of the rotor or in the second wall area of the counter-rotor. This first control opening can be designed as a bore or as an elongated hole in the wall area, wherein the elongated hole can extend either along the axis of rotation or transversely to the axis of rotation. Usually at least two first control openings are formed in the wall area in order to supply the medium to be compressed to the at least one working space and to remove the compressed medium from the at least one working space. In order to avoid losses between the control openings supplying the medium and discharging the medium, the gap resulting between the outer wall and the inner wall of the housing can be made as small as possible. Due to the already mentioned advantageous design of the outer wall and the inner wall of the housing as a straight circular cylinder, the housing and associated rotor or counter-rotor can be manufactured in such a way that the gap required between the rotor or counter-rotor and housing is as small as possible.

In the invention, the second wall area of the counter-rotor is arranged in a radial bearing, the radial bearing being supported on the second inner wall of the housing.

This radial bearing can be designed both as a roller bearing and as a plain bearing. When using plain bearings as well as roller bearings, tight manufacturing tolerances must be maintained for the bores receiving the bearings in order to achieve precise concentricity of the rotor and counter-rotor. A design in which all components used, such as bearings, the inner wall of the housing accommodating these bearings, and the outer wall of the rotor and the counter-rotor can be manufactured as a straight circular cylinder with the tightest manufacturing tolerances, ensures a precise position of the rotor and counter-rotor relative to the housing. In particular when using a plain bearing to support the counter rotor in the housing, corresponding first control openings can be provided in the plain bearing in order to supply the medium to be compressed to the working spaces or to remove the compressed working medium from the working spaces.

In the invention, an end face is formed on the second wall region of the counter rotor of the rotary piston machine on a side facing away from the second toothing. The end of the second housing can be locked in a rotationally fixed manner with a cover. An axial bearing is arranged between the cover and the end face.

The axial bearing can be designed both as a roller bearing and as a plain bearing. The axial bearing absorbs the axial forces occurring on the counter rotor during operation and introduces them into the cover, the cover being connected to the housing in such a way that these forces can be absorbed by the housing. The axial bearing can be connected to the cover in a rotationally fixed manner for easier assembly with the cover, particularly in the case of the plain bearing design.

In the invention, the cover has at least one inlet opening arranged parallel to the second axis of rotation of the counter-rotor, the axial bearing at least one second inlet control opening and the end face at least a third one Entry control opening on. A medium to be transported can be fed through the inlet opening and the second inlet control opening to the third inlet control opening.

The medium to be transported can also be removed through the third entry control opening, the second entry control opening and the entry opening. Furthermore, it is possible to form an outlet opening in the cover parallel to the inlet opening, a second outlet control opening in the axial bearing parallel to the second inlet control opening and a third outlet control opening parallel to the third inlet control opening in the end face of the counter rotor. Here, the inlet opening, the second inlet control opening and the at least one third inlet control opening as well as the outlet opening, the second outlet opening and the at least one third outlet control opening are connected to one another in a fluid-communicating manner. However, the inlet opening, the second inlet control opening and the third inlet control opening are separated from the outlet control opening, the second outlet control opening and the third outlet control opening in a fluid-tight manner. By means of such an arrangement, a medium to be compressed can be fed to the at least one working space in the axial direction, i.e. parallel to the second axis of rotation of the counter-rotor, and the compressed medium can be removed from the at least one working space in a likewise axial direction.

In one embodiment of the invention, the counter-rotor has at least one inlet control channel which is connected in a fluid-communicating manner to the third inlet control opening and at least one of the tooth gaps such that the medium can be fed to the at least one working space.

This ensures that the fluid to be compressed reaches the opening working spaces and then leaves the closing working spaces in a compressed state. The opening does not necessarily have to be made in a tooth gap, but can also be formed in the area of the tooth flank.

In one embodiment of the invention, the spherical ring-shaped outer contour is clasped by the spherical ring-shaped inner wall.

Clasp is to be understood as meaning that the spherical ring-shaped inner wall extends at least partially into a spherical ring-shaped outer contour that tapers in the direction of a shaft of the rotor or counter-rotor, the shaft being arranged on a side facing away from the respective toothing. By clasping or grasping the rotor is fitted into the counter rotor and vice versa. In other words, a first diameter at the entry of the spherical ring-shaped inner wall is smaller than a second largest diameter of the spherical ring-shaped outer contour. Thus, a mounted rotor-counter-rotor arrangement can either no longer be separated from one another or can only be separated from one another under the action of force along the axes of rotation. Particularly when the rotor and / or counter-rotor are formed from plastic, it may be possible to move the two rotors into the rotor-counter-rotor arrangement due to the high modulus of elasticity of plastics and the associated elastic deformability as well as a force acting along the axes of rotation of the rotor and counter-rotor bring. Due to this modulus of elasticity, it may also be possible to separate the rotor and counter-rotor from one another by applying force. The rotor and / or counter-rotor can also be made in several parts in order to achieve this clasping effect in rotors made in particular of metal, since metal generally has a considerably lower modulus of elasticity than the aforementioned modulus of elasticity of the plastics used here.

As a rule, a fraction of the compressed medium is used to exert a force on the face of the counter-rotor in the axial direction, which counteracts the force that is exerted on the counter-rotor by the medium to be compressed. This ensures that when the teeth of the rotors are meshed, there are no gaps that go beyond a predetermined amount. However, in the start-up phase, that is to say at the start of the rotation of the rotors, there is no or at least insufficient pressure of the medium on the face of the counter-rotor. Thus, the counter rotor would be pushed out by the rotor through the medium to be compressed beyond the predetermined gap size of the teeth without being clasped. Thus it would take a certain time until the medium to be compressed is subjected to the predetermined pressure so that this medium can press on the end face in such a way that the counter rotor is pressed towards the rotor to the predetermined gap. Through the Clamping, this effect is largely avoided, since the medium to be compressed can only push the counter-rotor away from the rotor until the rotor or counter-rotor rests against this clasping. Thus, the extent to which the medium to be compressed can push the counter rotor away from the rotor is not determined by the axial bearing, but rather by the clasping. Due to this grip, the medium to be compressed reaches its final pressure after just a few rotations of the rotor-counter-rotor combination.

In a further exemplary embodiment of the invention, at least one component from the group of rotor, counter-rotor and housing is formed in one piece.

In a further exemplary embodiment of the invention, at least one component from the group of rotor, counter rotor and housing is made of plastic.

In a further exemplary embodiment of the invention, at least one component from the group of rotor, counter-rotor and housing is designed as an injection-molded part.

Embodiments of the invention are described below with reference to the accompanying figures. The figures are only schematic and not true to scale.

Fig. 1

zeigt eine Drehkolbenmaschine im Längsschnitt, die nicht in den Umfang des Anspruchs fällt, aber zweckdienlich für die Beschreibung und das Verständnis der Erfindung ist,

Fig. 2

zeigt eine 3D-Ansicht von Rotor und Gegenrotor aus Fig. 1 in Betriebsstellung,

Fig. 3

zeigt eine Drehkolbenmaschine gemäß der beanspruchten Erfindung im Längsschnitt,

Fig. 4

zeigt eine Explosionszeichnung der Komponenten aus Fig. 3 und

Fig. 5

zeigt einen Querschnitt der in Fig. 4 dargestellten Komponenten.

Brief description of the drawings

Fig. 1

shows a rotary piston machine in longitudinal section, which does not fall within the scope of the claim, but is useful for the description and understanding of the invention,

Fig. 2

shows a 3D view of the rotor and counter rotor Fig. 1 in operating position,

Fig. 3

shows a rotary piston machine according to the claimed invention in longitudinal section,

Fig. 4

shows an exploded view of the components Fig. 3 and

Fig. 5

shows a cross section of the in Fig. 4 illustrated components.

Detailed description of exemplary embodiments

At this point it should be pointed out that the same parts in the individual figures have the same reference symbols.

Fig. 1 shows a rotary piston machine which does not fall within the scope of the claim but is useful for the description and understanding of the invention and which operates as a pump, compressor or motor with a rotor 2 and a counter rotor 4, the rotor 2 being arranged opposite the counter rotor 4. The rotor 2 has on its first end face 6 a first toothing 8, which in the present case is designed as a cycloid toothing, but can also be, for example, a trochoidal toothing. The first toothing 8 is formed by at least one first tooth 10 and at least one first tooth gap 12. The counter rotor 4 has a second toothing 16 on its second end face 14. The second toothing 16 is formed by at least one second tooth 18 and at least one second tooth gap 20 formed. The two toothings 8, 16 are in engagement with one another in such a way that working spaces 24 are formed by meshing the teeth 10, 18. Furthermore, the rotor 2 has a first axis of rotation I and the counter-rotor 4 has a second axis of rotation II. The first axis of rotation I and the second axis of rotation II enclose an angle ϕ that is not equal to 0 °. By combing the teeth 10, 18, volumes formed by the first working spaces 24 are changed. The rotor 2 has a first spherical ring-shaped inner wall 26. The counter rotor 4 has a first spherical ring-shaped outer contour 28. The first spherical ring-shaped outer contour 28 is complementary to the first spherical ring-shaped inner wall 26 of the rotor 2. In the present exemplary embodiment, the rotor 2 is driven by a motor, of which only its drive shaft 30 is shown. The drive shaft 30 engages in a bore 31 formed on the rotor 2. The rotor 2 and the counter rotor 4 are jointly surrounded by a first housing 32. The first housing 32 is closed in a fluid-tight manner at the end by a first cover 36. The rotor 2 has a first wall area 40 delimited by the first spherical inner wall 26 and by a first outer wall 38. The first outer wall 38 is designed as a first straight circular cylinder 44. The first housing 32 has a first housing inner wall 42, which is shaped as a second straight circular cylinder 46 in the area of the rotor 2. Here, the first straight circular cylinder 44 is enclosed by the second straight circular cylinder 46. A rotor shaft 54 extending in a direction facing away from the first toothing 8 is integrally formed on the rotor 2, the rotor shaft 54 being received by a roller bearing 34 which is supported on the first housing 32. The rotor 2 is thus rotatably supported with respect to the first housing 32. The counter-rotor 4 can be rotated in that the cover 36 is provided with a bearing receptacle 48 which has the shape of a fifth straight circular cylinder 50. A counter-rotor shaft 52 extending in a direction facing away from the second toothing 16 is integrally formed on the counter-rotor 4 and is received by at least one further roller bearing 34, in the present case by two roller bearings 34. The two roller bearings 34 are supported in the bearing receptacle 48 of the cover 36, the cover 36 being non-rotatably connected to the housing 32. A first gap 55 which forms between the first outer wall 38 of the rotor 2 and the first inner wall 42 of the housing 32 is so small that liquid or gaseous medium can be fed to the at least one working space 24 via a feed channel 56 integrated in the housing 32 without the supplied medium mixes with the compressed medium to be discharged, which is removed from the working space 24 by means of a discharge channel 58 formed in the housing 32. The working space 24 is delimited on the one hand by the first 10 and second tooth 18 and the first 12 and second tooth gap 20 a support surface 61 arranged on the rotor 2 symmetrically to its axis of rotation I and shaped complementary to the spherical cap 59, as well as through the first spherical inner wall 26 of the rotor 2. According to the claimed invention, however, the support surface 61 is in the counter rotor 4 and the spherical cap 59 in the rotor 2, as shown in Figure 3 is shown.

A fluid to be compressed is supplied to the opening working spaces 24 via the supply channel 56 and is compressed by means of closing working spaces 24. The compressed fluid is removed from the working spaces 24 by means of the discharge channel 58 and fed to a consumer, not shown here.

Fig. 2 shows the off Fig. 1 known rotor 2 and counter rotor 4 in a 3D view. The first outer wall 38, shaped as a second straight circular cylinder 44, is clearly visible. At least one first control opening 60 is formed in the first wall region 40 transversely to the first axis of rotation I. In the present exemplary embodiment, this first control opening 60 is designed as a bore perpendicular to the first axis of rotation I. This at least one first control opening 60 can also be designed as an elongated hole which runs either along or transversely to the first axis of rotation I. The fluid supplied via the supply channel 56 passes through this at least one first control opening 60 into the at least one first working chamber 24 in order to be removed from this at least one working chamber 24 via the at least one first control opening 60 by means of the discharge channel 58 after the compression process.

Fig. 3 shows an embodiment of the rotary piston machine in longitudinal section. The main difference from the in Fig. 1 described example consists in that the counter rotor 4 has a second spherical ring-shaped inner wall 62 and the rotor 2 has a second spherical ring-shaped outer contour 64. Here, the second spherical ring-shaped outer contour 64 is designed to be complementary to the second spherical ring-shaped inner wall 62. Furthermore, the second spherical ring-shaped inner wall 62 of the counter-rotor 4 is extended by a clasping area 65. This clasping area 65 surrounds the second, second spherical outer contour 64 of the rotor 2, which tapers toward the rotor shaft 54. This clasping area 65 is also designed to be complementary to the second spherical inner wall 62 of the counter-rotor 4. By clasping or embracing, the rotor 2 is fitted into the counter-rotor 4 and vice versa. In other words, a first diameter d forming at an inlet 67 to the second spherical ring-shaped inner wall 62 is smaller than a second largest diameter D of the spherical ring-shaped outer wall 62 Rotor 2 and the counter rotor 4 are mounted, the two rotors 2, 4 cannot be separated or only with an increased force that would have to be applied along the first I and second axis of rotation II due to the clasping by the clasping area 65. In this case, the increased force is not achieved by the fluid compressed to a final pressure, so that the compressed fluid cannot push the rotor 2 and / or the counter rotor 4 apart to such an extent that the rotor 2 and / or the counter rotor 4 leaves the clasping area 65. The rotor 2 and the counter-rotor 4 are surrounded by a second housing 66, which is closed on the end face by a second cover 74 in a rotationally fixed and fluid-tight manner. The rotor 2 is mounted on its rotor shaft 54 in a first slide bearing 68, the slide bearing 68 being supported on the second housing 66. The slide bearing 68 absorbs radial and axial forces acting on the rotor 2. The counter rotor 4 has a second wall region 78 delimited by the second spherical ring-shaped inner wall 62 and a second outer wall 76. The second outer wall 76 is designed as a third straight circular cylinder 82. The second housing 66 has a second housing inner wall 80 which, at least in a partial area of the counter-rotor 4, has the shape of a fourth straight circular cylinder 84. Here, the third straight circular cylinder 82 is enclosed by the fourth straight circular cylinder 84. The second wall area 78 is arranged in a radial bearing designed as a second slide bearing 70, the second slide bearing 70 being supported on the second inner wall 80 of the housing. Furthermore, an end face 88 is formed on the second wall region 78 on a side facing away from the second toothing 16. A bearing receptacle 86 is formed on an inner side of the second cover 74 and receives an axial bearing designed as a third slide bearing 72. As a rule, the axial forces acting on the counter rotor 4 are absorbed by the clasping of the clasping area 65. If, for example, the axial forces should rise above a predetermined amount due to a malfunction, these axial forces can be introduced into the slide bearing 72 via the end face 88 of the counter-rotor 4.

In operation, the rotor 2 and the counter rotor 4 are spaced apart from one another by a predetermined second gap dimension 69. This is achieved in that a portion of the compressed fluid is directed onto the end face 88 of the counter-rotor 4. Thus, the force that the fluid exerts on the The rotor 2 and the counter rotor 4 are compensated by the fact that the end face 88 of the counter rotor 4 is also acted upon by a force. During the start-up phase, there is still no compressed fluid available, the pressure of which could be directed onto the end face 88. The fluid to be compressed can thus push the counter rotor 4 away from the rotor 2 beyond the predetermined second gap dimension 69 during the compression process. In order to achieve a constant operating state, it takes several revolutions of the rotor 2 until a predetermined final pressure of the fluid can be reached. The clasping in the clasping area 65 prevents the fluid from pushing the counter-rotor 4 away from the rotor 2 beyond the predetermined second gap dimension during the start-up of the rotary piston machine during the compression process. Thus, after just a few revolutions of the rotor 2, a stable operating state is achieved in which the compressed fluid has received its predetermined final pressure. Thus, the clasp has the effect that the fluid reaches its final pressure in a shorter time than would be the case without the clasp.

The supply and discharge of the fluid can take place here as it is in FIG Fig. 2 has been described. However, in the embodiment claimed, the fluid is supplied and discharged in the axial direction along the second axis of rotation II Figures 4 and 5 are explained in more detail.

Fig. 4 shows the components of the Fig. 3 shown as a 3D exploded view. Fig. 5 shows these components in longitudinal section. A fluid to be compressed is fed to the working spaces 24 via an inlet opening 90 arranged in the second cover 74 parallel to the second axis of rotation II. Here, the fluid flows through a second inlet control opening 92 integrated in the third slide bearing 72 and subsequently formed in the end face 88 third inlet control openings 94 which are connected in a fluid-communicating manner to at least one inlet control channel (not shown here), the inlet control channel with at least one in a second tooth flank 22 of the second toothing 16 formed opening 104 is connected in fluid communication. This opening 104 can also be formed in the second tooth gap 20 of the second toothing 16. The medium to be compressed enters the opening working spaces 24 through these openings 104. After the fluid has been compressed, this is via at least one further opening 104, which is connected to at least one third outlet control opening 96 by means of an outlet control channel (not visible here), is discharged from the rotary piston engine via a second outlet control opening 98 formed in the third slide bearing 72 and an outlet opening 102 formed parallel to the inlet opening 90 in the second cover 74. So that the fluid can be compressed in the rotary piston machine, the supplied fluid has essentially no connection to the discharged fluid within the rotary piston machine. The second inlet control opening 92 is therefore separated from the second outlet control opening 98 by means of webs 100 which are integrated in the third slide bearing 72.

Claims (1)

1. Rotary piston machine operating as a pump, compressor or motor,

   - having a rotor (2) and a counter rotor (4), wherein the counter rotor (4) is arranged facing the rotor (2),

   - wherein the rotor (2) has a first face surface (6) with a first toothing (8), wherein the counter rotor (4) has a second face surface (14) with a second toothing (16), and wherein the first toothing (8) and the second toothing (16) are each formed from at least one tooth (10, 18) and one tooth space (12, 20),

   - wherein the toothings (8, 16) engage with one another such that meshing of the teeth (10) of the first toothing (8) and of the teeth (18) of the second toothing (16) causes working chambers (24) to be formed, wherein volumes formed by the working chambers (24) are varied by the meshing of the teeth (10, 18),

   - wherein the rotor (2) has a first axis of rotation (I), wherein the counter rotor (4) has a second axis of rotation (II), wherein the first axis of rotation (I) and the second axis of rotation (II) enclose an angle (ϕ) that differs from 0°,

   - wherein the counter rotor (4) has a first spherical ring-shaped internal wall (62), and the rotor (2) has a first spherical ring-shaped external contour (64), which is formed in a complementary manner with respect to the first spherical ring-shaped internal wall (62) of the counter rotor (4),

   - wherein the counter rotor (4) has a wall region (78) which is delimited by the first spherical ring-shaped internal wall (62) and an external wall (76), wherein the external wall (76) is in the form of a rectilinear circular cylinder (82), wherein a housing (66) in which the counter rotor (4) is rotatably mounted has a housing internal wall (80) which, at least in a partial region of the counter rotor (4), is in the form of a rectilinear circular cylinder (84), wherein the rectilinear circular cylinder (82) is at least partially enclosed by the rectilinear circular cylinder (84),
   characterized in that

   - the wall region (78) is arranged in a radial bearing (70), wherein the radial bearing (70) is supported on the housing internal wall (80),

   - wherein a face side (88) is formed on the wall region (78) on a side facing away from the second toothing (16), wherein the second housing (66) is closable on the face side by a cover (74) for rotation therewith, wherein an axial bearing (72) is arranged between the cover (74) and the face side (88),

   - wherein the cover (74) has at least one inlet opening (90) arranged parallel to the second axis of rotation (II) of the counter rotor (4), the axial bearing (72) has at least one inlet control opening (92) and the face surface (88) has at least one inlet control opening (94), wherein a medium which is to be transported can be supplied through the inlet opening (90), the inlet control opening (92) and the inlet control opening (94),

   - wherein the cover (74) has an outlet opening (102) parallel to the inlet opening (90), the axial bearing (72) has an outlet control opening (98) parallel to the inlet control opening (92), and the face surface (88) of the counter rotor (4) has at least one outlet control opening (96) parallel to the inlet control opening (94), wherein a medium which is to be transported can be conducted away through the at least one outlet control opening (96), the outlet control opening (98) and the outlet opening (102),

   - wherein the inlet control opening (92) is separated from the outlet control opening (98) by means of webs (100) which are integrated in the axial bearing (72).

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