EP2655802B1 - Gear machine with a small diameter-to-length ratio - Google Patents

Description

State of the art

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

From the DE 42 41 320 A1 is known a rotary piston machine, which works as a pump, compressor or motor. In this run combs of teeth of a rotating drive member for limiting work spaces on a cycloid surface of a likewise toothed output member and thereby drive this output member. Between the teeth of the driving part and the driven part, the said work spaces are formed, which are increased or reduced during the rotation of the parts for their work or to produce the conveying effect on a gaseous or liquid medium.

Such drive and driven parts run in a common housing, whose interior is spherical. For mounting these parts, the housing is divided such that the separation plane contains the center 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 is formed. As a result, special attention is to be paid to the design of the parting surfaces of the two housing parts in such a way that in the assembled state the first and the second center of the spherical interior spaces of the housing parts coincide.

Summary of the invention

There may be a need to provide a rotary engine in which the housing is made compact and easy to manufacture.

This need can be solved by the subject matter of the independent claim. Advantageous embodiments are specified in the dependent claims.

A rotary piston engine operating as a pump, compressor or motor has a rotor and a counter rotor, the counter rotor being located opposite the rotor. The rotor has a first end face with a first toothing. The counter rotor has a second end face with a second toothing. The first toothing is formed from at least a first tooth and a first tooth gap. The second toothing is formed from at least one second tooth and a second tooth gap with a second tooth root. The teeth are engaged with each other such that first working spaces are formed by meshing the first teeth of the first teeth and the second teeth of the second teeth, wherein volumes formed by the first working spaces are 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 include a first angle other than 0 °. A second extension of a second generatrix of the second tooth root, the first axis of rotation and the second axis of rotation intersect at a common center point. Here, a second angle enclosed between the second extension and the second axis of rotation is less than 45 °.

Assuming equal volumes in the prior art and the invention, these volumes being each formed by the at least one working space, causes a reduction of the second angle of about 80 °, as known in the art, to less than 45 °, that an outer diameter of the toothing is reduced. As a result, a reduction of the outer diameter of the prior art of 50% and more can be achieved. As a result of the changed outer diameter, the teeth of the new rotor counter rotor arrangement generally become longer. hereby As a rule, a housing accommodating the novel rotor-counter-rotor arrangement will also be made longer than the prior art, but a diameter of the new housing will be smaller compared to a housing according to the prior art. Also, in the inventive rotor-counter-rotor arrangement, a distance measured at the outer diameter which forms in the at least one maximally opened working space between a first tooth root of the first tooth space of the first toothing and a second tooth bottom of the second tooth space of the second toothing is less than in the prior art. Thus, a sealing the at least one working space relative to the housing surface can be made smaller than in the prior art. In addition, it is no longer necessary to manufacture the housing from two half-shells, as is necessary in the prior art, but the housing can be made in one piece. In this case, the necessary sealing surface can be integrated. With the same number of revolutions of the rotor counter-rotor arrangement, measured in an arrangement according to the prior art and an arrangement according to the invention, results in comparison with the novel arrangement, a lower peripheral speed of the teeth and thus a lower peripheral speed of the fluid to be transported. As a further advantage, it may be found that when the gears are made very long, large volumes of the working spaces can be formed with a small diameter of the housing. In addition, increased tightness between the rotor mating rotor assembly and the housing can be achieved by better reducing a gap between the housing and the rotors on the sealing surface by moving the rotors.

In a further embodiment of the invention, the included second angle is less than 30 degrees.

In another embodiment of the invention, the included angle is 22.5 degrees.

In a further embodiment of the invention, a third toothing adjoins the first toothing and a fourth toothing adjoins the second toothing, wherein the third toothing comprises at least one third tooth and a third tooth gap is formed, and wherein the fourth toothing of at least a fourth tooth and a fourth tooth gap is formed with a fourth tooth root. The third and fourth teeth are engaged with each other such that second working spaces are formed by meshing the third and fourth teeth, and volumes formed by the second working spaces are changed by the meshing of the teeth. Here, the first toothing of the third toothing and the second toothing of the fourth toothing is spatially separated by a separating web.

Thus, therefore, two independent work spaces are formed in a rotor counter rotor arrangement. Thus, therefore, a gaseous or liquid medium to be transported can be supplied to both the first and the second work spaces. Also, the number of teeth of the first gear and the third gear must not be equal. Thus, there may be more teeth in the first toothing than in the third toothing and vice versa. The first toothing has a tooth difference with respect to the second toothing and the third toothing with respect to the fourth toothing. In the present example, in each case the second or the fourth toothing has one tooth more than the first or third toothing. The spatial separation of the first toothing of the third toothing and the second toothing of the fourth toothing can cause a medium to be transported is first supplied to the first work spaces for precompression and then the second work spaces for recompression. Thus, a medium to be transported by means of two compressor stages, ie multi-stage, compacted from an initial pressure to a final pressure. Also, a medium to be compressed can be divided into a first and a second volume flow, wherein the first volume flow is supplied to the at least one first working space and the second volume flow to the at least one second working space for compression. This is a multi-flow operation. By arranging valves before or after the first and / or second working spaces, the volumetric flow leaving the rotary piston engine can be reduced step by step or continuously with respect to the volumetric flow supplied to the rotary piston engine at constant rotational speed of the rotor counter-rotor arrangement. In a further embodiment of the invention, the separating web is fluid-tightly connected to the rotor.

The spatial separation of the first toothing of the third toothing and the second toothing of the fourth toothing causes a fluid communication between the pressurized first working spaces and the acted upon with a second pressure second working spaces does not occur, wherein the first pressure of the second Pressure can be different. A connection of the first and second work spaces takes place, if at all, only when the medium compressed by means of the first work spaces is supplied to the second work spaces for further compaction.

In a further embodiment of the invention, a fourth extension of a fourth generatrix of the fourth tooth base coincides with the second extension. In this embodiment, it is a continuous toothing, which is spatially separated by the separating web or the groove into a first and third or a second and fourth toothing.

In a further embodiment of the invention, a fourth extension of a fourth generatrix of the fourth tooth base does not coincide with the second extension. Thus, the number of teeth of the first gear may be different from the number of teeth of the third gear and the number of teeth of the second gear on the number of teeth of the fourth gear. The first toothing and the third toothing or the second toothing and the fourth toothing can also have the same number of teeth, but the first and the third toothing or the second and the fourth toothing can be at different angles to one another. It can also be the same angle just be, but then the fourth extension and the second extension will be aligned parallel to each other.

In a further exemplary embodiment of the invention, the separating web is formed on a third end face of the rotor and engages in a groove and / or recess designed to be complementary to the separating web in the counter-rotor. A the first toothing facing end face of the divider is formed spherical shell around the common center.

Due to the mutually angled arrangement of the first axis of rotation of the rotor and the second axis of rotation of the counter rotor changes over the circumference viewed a distance of the first toothing of the second toothing. Due to the different number of teeth, the rotor and the counter rotor move at different speeds. If the separating web is formed concentrically to the first axis of rotation and rotates with the rotor, the separating web immersed in a closed working space deeper into the groove of the counter-rotor than in an open working space. This is to be considered in the design of the groove in the counter rotor. Of course, the divider can also be formed in the counter rotor and, accordingly, the groove in the rotor. In particular, if the separating web of the at least one rotor delimits the working space on the front side on an outer wall of the associated counter-rotor, this region of the outer wall which is in communication with the separating web can be formed as a depression.

In a further exemplary embodiment of the invention, at least two rotors are connected to each other in an axially and radially non-rotatable manner such that axes of rotation of the rotors coincide with the first axis of rotation. The associated counter-rotors are axially and radially backlash-free rotatably connected to each other, such that axes of rotation of the counter-rotors coincide with the second axis of rotation.

This makes it possible to create a series connection of work spaces. For the individual stages, the rotors and the counter-rotors can be designed the same, in which case the separating web is arranged in each case on the third end face of the rotors, wherein the individual working spaces are separated from each other in a fluid-tight manner by the dividing webs. Thus, for example, the same rotors can be used for a series connection, for example, concentric with the axis of rotation at the third end face of the rotor may be an opening in which a formed on one of the third end face fourth end face of the rotor formed pin can engage. The axial and radial backlash of both the rotors and the counter rotors ensures that when mounting the individual rotors with the individual counter rotors the Fluid tightness between the individual workrooms can already be done during assembly. To compensate for possible manufacturing tolerances and to produce the fluid tightness, a grinding process may be required.

In a further embodiment of the invention, a rotor counter-rotor arrangement of the rotary piston engine is integrated in an electric motor.

This can be done, for example, such that the electric motor is located in a housing designed as a straight circular cylinder, wherein the rotor counter-rotor arrangement is arranged centrally in the housing.

In a further embodiment of the invention, the third end face of the rotor of the rotor counter rotor arrangement is mounted in a fifth end face of a housing surrounding the electric motor. One of the third end face of the rotor opposite fourth end face of the rotor of the rotor counter-rotor assembly is rotatably connected to an external rotor of the electric motor. By means of the external rotor of the electric motor, the rotor and thus also the counter rotor are driven. The fifth end face of the housing may be spherical in shape in order to seal the work spaces of the rotor counter-rotor arrangement facing the fifth end face. Advantageously, therefore, the large diameter of the toothing in the direction of the fifth end face and the small diameter of the toothing is assigned to the external rotor. During operation, the rotor is pressed in the direction of the fifth end side due to the forces acting on the rotor-counter-rotor arrangement by the medium to be compressed. Thus, no axial forces act on the external rotor of the electric motor. The then acting on the counter rotor through the medium to be compressed axial forces are opposite to the axial force acting on the rotor. As a rule, this axial force acting on the counter rotor is absorbed by a thrust bearing.

In a further embodiment of the invention bearing journals are in the form of straight circular cylinders formed on the third and fourth end face of the rotor, which are arranged concentrically to the first axis of rotation.

These trunnions can be accommodated in a simple manner by sliding and / or roller bearings, these bearings can be supported on a Gehäuseinnenwandung of the housing and accordingly initiate the acting on the rotor counter-rotor arrangement forces in the housing.

In a further embodiment of the invention, the counter rotor on its outer wall on at least one bearing seat, which is surrounded by a bearing, which is supported on a housing inner wall of the housing.

By attaching bearing seats on the outer wall of the counter-rotor, it is possible to support the counter-rotor on its length several times. A multiple support along the outer wall of the counter-rotor, for example, serve to reduce buckling of a particularly thin-walled counter-rotor in conjunction with high pressures. Here, the outer wall enclosing bearing serves as a stiffener at the same time. In general, the outer wall will have two bearing seats, one of which is a bearing seat for receiving a fixed bearing and the other bearing seat for receiving a floating bearing. In particular, the fixed bearing can also be designed to absorb axial forces, so that here also a combined axial-radial bearing can be used.

In a further embodiment, the fifth end face is formed as a spherical surface around the common center and arranged to seal the at least one first working space with respect to a housing.

In this way, no fluid to be compressed from the rotor-counter rotor arrangement in the electric drive.

In a further embodiment of the invention, the electric motor is designed as a brushless DC motor. In particular, brushless DC motors have a long life, as has been dispensed with wearing brushes. Also, no abrasion takes place within the electric motor, possibly on the one hand in the rotor counter-rotor assembly receiving bearing and the other in the sealing surface designed fifth end face could arrive. Of course, the electric motor can also be designed as an asynchronous motor with external rotor.

In a further embodiment of the invention, the rotary piston machine is designed instead of a rotor counter-rotor arrangement with a rotor-stator arrangement.

In a further embodiment of the invention, the rotor and the counter rotor are made in one piece.

It is noted that thoughts on the invention herein are described in the context of a rotary engine having a rotor and a counter rotor. It will be clear to a person skilled in the art that the individual features described can be combined with one another in various ways so as to arrive at other embodiments of the invention.

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

Figur 1

zeigt eine Rotor-Gegenrotor-Anordnung nach dem Stand der Technik,

Figur 2

zeigt einen Längsschnitt der Rotor-Gegenrotor-Anordnung nach dem Stand der Technik aus Figur 1,

Figur 3

zeigt eine erfindungsgemäße Rotor-Gegenrotor-Anordnung,

Figur 4

zeigt einen Längsschnitt der erfindungsgemäßen Rotor-Gegenrotor-Anordnung aus Figur 3,

Figur 5

zeigt eine Explosionszeichnung der erfindungsgemäßen Rotor-Gegenrotor-Anordnung,

Figur 6

zeigt einen Längsschnitt durch eine Rotor-Gegenrotor-Anordnung mit Trennsteg,

Figur 7

zeigt einen Längsschnitt durch eine Rotor-Gegenrotor-Anordnung mit zwei in Reihe geschalteten Rotoren mit Gegenrotoren,

Figur 8

zeigt die Anordnung aus Figur 7 im Röntgenblick,

Figur 9

zeigt einen Längsschnitt eines Elektromotors mit einer integrierten Rotor-Gegenrotor-Anordnung,

Figur 10

zeigt eine stirnseitige Ansicht des Elektromotors, und

Figur 11

zeigt den Elektromotor in der Ansicht von Figur 10 im Röntgenblick.

Brief description of the drawings

FIG. 1

shows a rotor counter-rotor arrangement according to the prior art,

FIG. 2

shows a longitudinal section of the rotor counter-rotor assembly according to the prior art FIG. 1 .

FIG. 3

shows a rotor counter-rotor arrangement according to the invention,

FIG. 4

shows a longitudinal section of the rotor counter-rotor assembly according to the invention FIG. 3 .

FIG. 5

shows an exploded view of the rotor counter-rotor assembly according to the invention,

FIG. 6

shows a longitudinal section through a rotor counter rotor arrangement with separating web,

FIG. 7

shows a longitudinal section through a rotor counter-rotor arrangement with two rotors in series with counter-rotors,

FIG. 8

shows the arrangement FIG. 7 in X-ray vision,

FIG. 9

shows a longitudinal section of an electric motor with an integrated rotor-counter-rotor arrangement,

FIG. 10

shows an end view of the electric motor, and

FIG. 11

shows the electric motor in the view of FIG. 10 in x-ray view.

Detailed description of exemplary embodiments

It should be said at this point that the same parts in the individual figures have the same reference numerals.

FIG. 1 shows a rotor 2 counter rotor 4 arrangement according to the prior art. Here, the rotor 2 has a first end face 6 with a first toothing 8, wherein the first toothing 8 is formed from a first tooth 10 and a first tooth gap 12. The counter rotor 4 has a second end face 16 with a second toothing 18, wherein the second toothing 18 consists of a second tooth 20 and a second tooth gap 22 with one in particular FIG. 2 visible second tooth bottom 24. In this case, first working chambers 28 are formed by combing the first teeth 10 of the first toothing 8 and the second teeth 20 of the second toothing 18, wherein volumes formed by the first working chambers 28 are changed by the meshing of the teeth 10, 20. The rotor 2 rotates about a first rotation axis I and the counter rotor 4 rotates about a second rotation axis II. The first rotation axis I and the second rotation axis II include a first angle φ which is not equal to 0 °. Furthermore, a resulting largest opening of the working space is shown as a bold line extending along a first outer contour 34 of the rotor 2 counter-rotor 4 arrangement.

FIG. 2 shows a longitudinal sectional view of the rotor 2 counter rotor 4 arrangement FIG. 1 According to the state of the art. In addition to the illustration in FIG. 1 It can be seen that the first axis of rotation I and the second axis of rotation II intersect at a common center M. At the end face 16 of the counter-rotor 4, a ball cap 30 is formed. A second outer contour 36 of the ball cap 30 has a first diameter d, which passes through the common center M. On the rotor 2 is concentric to the first axis of rotation I to the second outer contour 36 complementary formed support surface 32 is formed. The rotor 2 counter rotor 4 arrangement forms the first outer contour 34 in the form of a hemisphere stub. This first outer contour 34 has a second diameter D, which also extends through the common center M. A tooth length L1 of the first 8 and second toothing 18 is limited by the first 34 and the second outer contour 36. A second extension 26 of a second generatrix, which runs in the second tooth base 24 and also through the common center M, closes with the second axis of rotation II of the counter-rotor 4 a second angle β, wherein the angle β is about 80 ° in the prior art.

FIG. 3 shows the components of the FIG. 1 , wherein the second angle β, as in particular in FIG. 4 can be seen, is reduced to 22.5 °. It is clearly visible that the rotor 2 and the counter-rotor 4 is formed elongated with the same volume of the first working space 28 with respect to the rotor 2 counter-rotor 4-arrangement according to the prior art. In addition, a shaping of an outer wall 44 of the counter-rotor 4 as a truncated cone is possible. The rotor 2 can thus be enclosed by the counter rotor 4 at least in wide areas. By changing the second angle β to 22.5 results, as in particular in FIG. 4 can be seen, an opposite the first tooth length L1 extended second tooth length L2. In addition, the spherical cap 30 of the counter-rotor 4 and the support surface 32 corresponding to the spherical cap 30 are made considerably flatter, as can be seen on the second outer contour 36. This is also due to the fact that the common center M is now outside the rotor 2 counter rotor 4 arrangement. Furthermore, it can be seen that a largest opening 14 of the first working space 28 resulting in the area of the first outer contour 34, into which FIGS. 1 and 3 shown in bold, facing the in FIG. 1 State of the art has greatly reduced.

FIG. 5 shows an exploded view of the rotor 2 counter rotor rotor assembly 4 according to the invention. Here, a bearing pin 40 is integrally formed on a third end face 38 concentric with the first axis of rotation I. At a third end face 38 opposite fourth end face 42 is also concentric with the first axis of rotation I, a further bearing pin 40 is formed. On the outer wall 44 of the counter rotor 4 are two bearing seats 46 for Recording of camps, not shown here forms. Due to the change of the second angle β to 22.5 °, the rotor 2 and the counter rotor 4 have changed their geometric shape, assuming that both the rotor 2 and the counter rotor 4 have assumed the shape of a truncated cone. In this case, the first 6 and the second end face 16 with their respective toothings 8, 18 are changed from an originally end-side arrangement to a now circumferential arrangement. The first end face 6 now forms an outer circumferential surface of the frustoconical shaped rotor 2 and the second end face 16 forms an inner circumferential surface of the hollow truncated cone shaped counter-rotor 4. For the further description, the outer and inner lateral surface are still referred to as end face 6, 16.

FIG. 6 shows a longitudinal section through a rotor 2 counter-rotor 4-arrangement according to the invention with a divider 48. This divider 48 spatially separates a subsequent to the first toothing 8 third toothing 52, which is formed by a third tooth 54 and a third tooth gap 56. The divider 48 is formed spherical shell-shaped and connected to the rotor 2 inextricably. At the separating web 48, a spherical end face 49 facing the third toothing 52 is formed, wherein the spherical end face 49 has a diameter running through the common center M. The divider 48 dips into a complementary groove 50 formed in the counter rotor 4. This groove 50 spatially separates the second toothing 18 from the fourth toothing 58 adjoining this second toothing 18, wherein the fourth toothing 58 is formed from at least one fourth tooth 60 and at least one fourth tooth gap 62. Furthermore, the separating web 48, in cooperation with the groove 50, separates the space formed by at least one first working space 28 from a second working space 66, which is formed by meshing the second teeth 54 and the fourth teeth 60, spatially and fluidtightly. In the present example, the rotor 2 and the counter rotor 4 are made in one piece and rotationally symmetrical. Also, the number of the first teeth 10 and the number of the third teeth 54 and the number of the second teeth 20 and the number of the fourth teeth 60 are the same. The number of first teeth 10 and third teeth 54 is smaller by one tooth than the number of second teeth 20 and fourth teeth 60, respectively. In this arrangement, a fluid to be compressed first becomes the at least one first working space 28 supplied to pre-compact it. Subsequently, the precompressed fluid is supplied to the at least one second working space 66 in order to compress it to its final pressure. Thus, a multi-stage compression takes place. Also, a fluid to be compressed can be split into a first and a second volume flow, wherein the first volume flow is supplied to the at least one first working space 28 and the second volume flow to the at least one second working space 66 for compression. This is a multi-flow application.

FIG. 7 shows a longitudinal section through a rotor 2 counter rotor 4 arrangement with two rotors 2 connected in series with associated counter rotors 4. The in FIG. 7 shown rotors 2 differ from the in FIG. 5 shown rotor 2 characterized in that the formed on the third end face 38 bearing pin 40 has been replaced in the present figure by a bearing bore 72. As a result, a plurality of rotors 2 can now be connected to one another in a rotationally fixed manner axially and radially free of play along the first axis of rotation I, in that the bearing journal 40 integrally formed on the fourth end face 42 engages in the bore 72 provided for this purpose. In order to limit the forming first working spaces 28 frontally, is the off FIG. 6 already known separating web 48 integrally and concentrically with respect to the first axis of rotation I formed on the third end face 38, such that the spherical end face 49 of the separating web 48 of the first toothing 8 faces. Furthermore, the outer wall 44 of the counter-rotor 4 is provided on an end face 69 facing the separating web 48 with a recess 68 designed complementarily to the spherical end face 49, which is designed to be fluid-tight in connection with the end face 49 of the separating web 48. It can also be dispensed with the recess 68, so that the end face 69 of the counter-rotor 4 is complementary to the spherical end face 49 of the separating web 48 and in connection with the separating web 48, the at least one first working space 28 fluid-tight. The associated counter-rotors 4 are axially and radially backlash-free connected to each other. In the FIG. 7 Of course, shown two-stage series circuit can be extended by means of another rotor 2 counter rotor 4-arrays. Such rotor 2 counter-rotor 4 arrangements can then be operated in multiple stages and / or multi-flow.

FIG. 8 shows the arrangement FIG. 7 in x-ray view. It can be seen in particular that the series connection of identical rotors 2 is constructed with the associated counter-rotors 4.

FIG. 9 shows the in FIG. 5 illustrated rotor 2 counter rotor 4 assembly integrated in an electric motor 70. Of course, a rotor 2 counter rotor 4 arrangement, for example according to FIG. 7 be used. The formed on the third end face 38 bearing pin 40 is received in a radial bearing 88, which is located in a dome 86, wherein the dome 86 is integrally formed with the housing 73. The integrally formed on the fourth end face 42 bearing pin 40 is received in a combined axial-radial bearing 76. Here, the bearing pin 40 is radially received and the counter rotor 4 is supported with its integrally formed on the outer wall 44 sixth support surface 45 axially on this bearing 76 from. The two bearing seats 46 are each received by a radial bearing 74, wherein the two radial bearings 74 are supported on a Gehäuseinnenwandung 78 of the housing 73. Thus, all the axial and radial forces emanating from the fluid to be compressed onto the rotor 2 counter rotor 4 arrangement are introduced into the housing 73 and received by the latter. Furthermore, it can be seen that the third end face 38 opposite fourth end face 42 of the rotor 2 is formed as the support surface 32 which abuts the ball cap 30 of the counter-rotor 4 or is spaced predetermined. Furthermore, the electric motor has an external rotor 84, which is non-rotatably connected to the journal 40 formed on the fourth end face 42. Since the essentially formed as a closed at one end side hollow cylinder housing 73 is easily accessible on its cover 79 a facing end face, all components can be mounted from this page. Subsequently, the housing 73 is closed at the end by means of the lid 79. In particular, the housing 73 may be integrally formed.

As in FIG. 10 As can be seen, located in the vicinity of the dome 86, an inflow opening 90 and an outflow opening 92. These openings 90, 92 are in the FIG. 9 not apparent due to the longitudinal section selected there. Through the inflow opening 90, a fluid to be compressed flows into opening working spaces 28 of the rotor 2 counter-rotor 4 arrangement of the FIG. 9 a to by a rotation process of the rotor 2 about the first axis of rotation I and the Counter rotor 4 to be compressed about the second axis of rotation II by closing working spaces 28 and the electric motor, respectively the rotary piston engine, to leave via the outflow opening 92. During the compression process, the fluid exerts a force on both the rotor 2 and the counter rotor 4. The force acting on the rotor 2 axial force component pushes the rotor 2 in the direction of a spherical and complementary to the first spherical outer contour 34 of the rotor 2 counter-rotor assembly 4 formed fifth end face 80 of the housing 73. A diameter of the spherical fifth face 80 extends through the common center M. One of the fifth end face 80 facing seventh end face 82 of the counter rotor 4 and the third end face 38 of the rotor 2 together seal the working space 28 relative to a housing interior 98. The force acting on the counter rotor 4 axial force component of the fluid to be compressed pushes the counter rotor 4 in the direction of the axial-radial bearing 76 which receives this Axialkraftanteil. A force acting on the counter rotor 4 radial force component is introduced into the two radial bearings 74 and from there into the housing 73. The two radial bearings 74 may be configured as a fixed-lot storage.

FIG. 11 shows the electric motor 70 from the FIG. 9 with the integrated rotor 2 counter rotor 4 arrangement as a 3D representation in the X-ray view. Here, it can be seen that the inflow opening 90 in an inlet control opening 94 and the outflow opening 92 in an outlet control opening 96 open, wherein the inflow opening 90, the outflow opening 92, the inlet control opening 94 and the outlet control opening 96 is shown as dash-dotted line.

Claims (10)

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

   - with a rotor (2) and a counter-rotor (4), the counter-rotor (4) being arranged opposite the rotor (2),

   - the rotor (2) having a first end face (6) with a first toothing (8), and the counter-rotor (4) having a second end face (16) with a second toothing (18),

   - the first toothing (8) being formed from at least one first tooth (10) and one first tooth space (12), and the second toothing (18) being formed from at least one second tooth (20) and one second tooth space (22) with a second tooth bottom (24),

   - the toothings (8, 18) being in engagement with one another in such a way that, as a result of the meshing of the first teeth (10) of the first toothing (8) and of the second teeth (20) of the second toothing (18), first working spaces (28) are formed, volumes formed by the first working spaces (28) being varied as a result of the meshing of the teeth (10, 20),

   - the rotor (2) having a first axis of rotation (I), the counter-rotor (4) having a second axis of rotation (II), the first axis of rotation (I) and the second axis of rotation (II) forming a first angle (ϕ) which is unequal to 0°,

   - a second prolongation (26) of a second generatrix of the second tooth bottom (24), the first axis of rotation (I) and the second axis of rotation (II) intersecting at a common centre point (M),

   characterized in that

   - a second angle (β) formed between the second prolongation (26) and the second axis of rotation (II) is smaller than 45°.
2. Rotary piston machine according to Claim 1, characterized in that a third toothing (52) adjoins the first toothing (8) and a fourth toothing (58) adjoins the second toothing (18), the third toothing (52) being formed from at least one third tooth (54) and one third tooth space (56), and the fourth toothing (58) being formed from at least one fourth tooth (60) and one fourth tooth space (62) with a fourth tooth bottom, the third (52) and the fourth (58) toothing being in engagement with one another in such a way that, as a result of the meshing of the third (54) and of the fourth (60) teeth, second working spaces (66) are formed, volumes formed by the second working spaces (66) being varied as a result of the meshing of the teeth (54, 60), the first toothing (8) being spatially separated from the third toothing (52) and the second toothing (18) from the fourth toothing (58) by means of a separating web (48).
3. Rotary piston machine according to Claim 1 or 2, characterized in that the separating web (48) is formed on a third end face (38) of the rotor (2) and engages into a groove (50) and/or depression (68) formed in the counter-rotor (4) complementarily to the separating web (48), an end face (49), facing the first toothing (8), on the separating web (48) being designed in the form of a spherical shell about the common centre point (M).
4. Rotary piston machine according to Claim 3, characterized in that at least two rotors (2) are connected fixedly in terms of rotation to one another in an axially and radially play-free manner, in such a way that axes of rotation of the rotors (2) coincide with the first axis of rotation (I), and in that the associated counter-rotors (4) are connected fixedly in terms of rotation to one another in an axially and radially play-free manner, in such a way that axes of rotation of the counter-rotors coincide with the second axis of rotation (II).
5. Rotary piston machine according to one of the preceding claims, characterized in that a rotor (2)-counter-rotor (4) arrangement is integrated in an electric motor (70).
6. Rotary piston machine according to Claim 5, characterized in that the third end face (38) of the rotor (2) of the rotor (2)-counter-rotor (4) arrangement is mounted in a fifth end face (80) of a housing (73) surrounding the electric motor (70), and in that a fourth end face (42) of the rotor (2), opposite the third end face (38) of the rotor (2), of the rotor (2)-counter-rotor (4) arrangement is connected fixedly in terms of rotation to an external rotor (84) of the electric motor (70).
7. Rotary piston machine according to Claim 6, characterized in that bearing journals (40) in the form of straight circular cylinders, which are arranged concentrically to the first axis of rotation (I), are formed on the third (38) and the fourth (42) end face of the rotor (2).
8. Rotary piston machine according to Claim 6 or 7, characterized in that the counter-rotor (4) has on its outer wall (44) at least one bearing seat (46) which is surrounded by a bearing (74) which is supported on a housing inner wall (78) of a housing (73).
9. Rotary piston machine according to Claims 6 to 8, characterized in that the fifth end face (80) is designed as a spherical surface about the common centre point (M) and is set up to seal off the at least one first working space (28) with respect to the housing (73).
10. Rotary piston machine according to Claims 6 to 9, characterized in that the electric motor (70) is a brushless-direct-current motor.

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