EP2585719A2

EP2585719A2 - Continuously variable volume hydrostatic rotary piston machine

Info

Publication number: EP2585719A2
Application number: EP11727168.4A
Authority: EP
Inventors: Siegfried A. Eisenmann
Original assignee: Individual
Current assignee: Individual
Priority date: 2010-06-23
Filing date: 2011-06-21
Publication date: 2013-05-01
Also published as: WO2011161117A2; WO2011161117A3

Abstract

The invention relates to a hydrostatic rotary piston machine according to the orbit principle, having a power element (51) acting as an output and comprising a stationary stator (52), a rotary piston (8), and a rotatably mounted shaft (11), wherein the rotary piston (8) is disposed eccentric to the shaft (11) for carrying out an orbit motion. The rotary motion of the rotary piston (8) and the shaft (11) is generated in that toothed chambers (8) formed between the stator (52) and the rotary piston (8) are supplied with and disposed of working fluid (6) by means of a rotary valve (3). According to the invention, the volume of the toothed chambers (8) and thus the displacement of the rotary piston machine is variable. To this end, the rotary piston (8) is axially displaceable relative to the stator (52) by means of adjusting elements (22). The toothed chambers (6) are axially sealed in the axial direction by an axially fixed rotary piston plate (17) radially coupled to the rotary piston (8), and by a stator plate (14) axially coupled to the rotary piston (8) and radially decoupled from the rotary piston (8), wherein the volume of the toothed chambers (6) is continuously variable by axially displacing the rotary piston (8) and the stator plate (14) by means of the adjusting elements (22). The variable displacement allows both economical operation as a motor, because the displacement adapts to the instantaneous power and torque demand and hydraulic losses can thereby be reduced, and operation as a pump for recuperative utilization of braking energy, because cavitation can be prevented by adapting the displacement as a function of the speed in pump mode. The rotary piston machine is thus suitable as a wheel motor for direct hydraulic drive of a vehicle having braking energy recovery.

Description

CONTINUOUS VOLUME CHANGEABLE HYDROSTATIC

CIRCLE PISTON MACHINE

The invention relates to a hydrostatic

Rotary piston engine according to the orbit principle after

Preamble of claim 1.

A hydrostatic rotary piston engine of this type is known from WO 2006/010471. Such hydrostatic

Rotary engines, as high-torque hydraulic motors

are formed, are excellent, for example, as a wheel motors for the hydrostatic drive of vehicles of all kinds. Because of the very high absorption volume per revolution of the output shaft arise at a given hydraulic

Input pressure very high output torques at the same time extremely small dimensions and weights. In case of

Use as a wheel motor inevitably the weight of the high-torque hydraulic motors unsprung mass of the wheel to be slammed, resulting in too large dimensions and

Weights in vehicle construction leads to significant problems in the suspension and damping of the driven wheel. In this regard, these high-torque hydraulic motors offer great advantages. However, they also have significant drawbacks because their large intake limits the possible

Speed up. In particular, those from the

The state of the art known high-torque hydraulic motors following disadvantages:

First, their flow rates and thus their

Speeds should not exceed certain values because the so-called respiratory organs, i. the control cross-sections on the rotary valve acting as a commutator, system only have very limited flow cross-sections. Because of the

Cavitation hazard should be at these narrowest cross sections in the Flow system, the oil velocity does not exceed the value of 10 m / s to a maximum of 12 m / s. If such a hydraulic motor is operated in the cavitation area, a considerable amount of noise is generated and the imploding cavitation bubbles lead to the destruction of the machine after a short time. These cavitation bubbles contain up to 10% air in the original fluid and also arise at these high levels

Oil velocities oil vapor by the prevailing low static pressure according to the Bernoulli 'see law.

Secondly, the amount of oil required to supply the oil engines would have to be e.g. per minute at high

Vehicle speeds assume very large values, which overstrains overall hydrostatic drive system.

Third, when driving the vehicle in the plane in

Unlike driving at acceleration or at

Gradient ride a relatively small drive torque required. However, for the extreme case of high acceleration or high tightening force at start-up, e.g. designed for towing heavy loads, assuming maximum available hydraulic pressure of the supply pump. All this leads to a conflict of goals between possible maximum

Speed and maximum tractive force of the vehicle.

Fourth: Hydrostatic drive systems in vehicles have the great advantage that a recuperative

Brake energy recovery is possible by the specially designed as a wheel motor high-torque hydraulic motors are switched in the case of braking to pumps and absorb torque. These high-torque hydraulic motors suck fluid from the tank and convey it under pressure into one or more hydraulic accumulators. The energy stored there can then be used again while driving. The problem of narrow flow cross sections at the commutator or rotary valve is much more dramatic here than in the case of the

Motor operation, since the high-torque hydraulic motors now have to suck in the fluid as pumps. Here, however, should be due to the risk of cavitation negative pressures of about 0.2 to 0.4 bar

Atmospheric pressure should not be fallen below.

A high moment hydraulic motors with constant high

Suction volume is thus largely unsuitable for recuperative brake energy recovery at high vehicle speeds.

From the prior art, in particular from the

DE 21 28 711 AI, DE 23 55 117 AI and US 2,484,789 A are certain basic principles for volume variability of hydraulic motors or hydraulic pumps that do not work on the rotary piston principle, but according to gerotor principle known. The gerotor principle is also referred to as a rotary piston principle. In gerotor motors or pumps, an internal rotor or rotary piston with external teeth with a number of teeth N rotates about a fixed internal rotor axis, while an external rotor with internal teeth with a number of teeth N + X, where X is usually 1 to a fixed outer rotor axis in the inner rotor rotates. The fixed outer rotor axis and the fixed one

Inner rotor axis are not on top of each other, but they are spaced parallel to each other. The inner rotor is thus eccentric to the outer rotor, the Ausserverzahnung and the internal teeth partially interlock. In DE 21 28 711 AI the outer rotor is indeed as a stator

However, this stator is also an external rotor rotatable in the housing about an axis. According to the teaching of DE 21 28 711 AI, the volume variability to control the specific amount of intake or delivery achieved by mutual axial displacement of the two rotors. However, this teaching can not be transferred to rotary engines. While a gerotor machine or rotary piston machine consists of an outer rotor and an inner rotor with fixed axes of rotation rotates in a rotary piston centric bearing shaft with a shaft external teeth centrally within a stator fixed in the housing with a stator internal teeth, wherein between the stator - Internal teeth and the shaft external teeth

Rotary piston is arranged, whose rotary piston internal teeth in the shaft outer teeth with

different number of teeth and its Kreiskolben- external teeth in the stator internal teeth with

different number of teeth intervene. The rotary piston performs a rotary motion about its own rotary piston axis, which is spaced parallel but not fixed to the shaft and stator axis. Upon rotation of the shaft of the rotary piston performs an orbit movement about the shaft axis in the region between the stator inner teeth and the shaft outer teeth. The rotary piston axis thus carries out a complex circular movement about the shaft and stator axis. Thus, the orbit movement, ie the

Rotational movement around a circle in a circular path

Axle, basically from the simple rotational movements around fixed axes of a gerotor machine. At a

Rotary piston machine also carry the filled with hydraulic fluid tooth chambers between the stator inner teeth and the circular piston external teeth through a circular motion around the shaft, while the tooth chambers are fixed in a gerotor machine in its basis. Therefore, the known in gerotor machines principles of axial displacement the two rotors in a rotary piston engine not applicable.

The invention therefore has as its object the

to solve system-related problems of high-torque hydraulic motors. The object underlying the invention is to provide a variable volume hydrostatic

To create rotary piston engine and to make the displacement of the known from the prior art high-torque hydraulic motors of a maximum amount to a minimum amount continuously variable, in particular with a

Suction volume ratio of 4: 1 to 6: 1, which results in a certain spread of the swallow volume. As is known, conventional vehicle transmissions,

In particular automatic transmissions, which serve exactly the same purpose, namely that the drive system of the vehicle the required speed ratio and the

required torque ratio while driving, a similar spread of their translations.

This task is accomplished by the realization of

characterizing features of the independent claim. Features that the invention in alternative or

educate in an advantageous manner, are the dependent

To claim.

The invention overcomes the above drawbacks while retaining the aforementioned advantages of such high torque hydraulic motors.

In the present invention is a rotary engine according to the orbit principle, wherein a

internally toothed stator is fixed in the spaces, a rotary piston performs a rotational movement about its own axis and makes this axis a circular motion in the opposite direction of rotation than the rotary piston. That means that in this

Total movement the axial distance between the rotary piston and stator center a rotational movement in the opposite direction of rotation as the rotary piston performs around its own axis. Such a rotary piston engine according to the orbit principle is therefore fundamentally different in structure with respect to the principle of motion than a so-called gerotor pump, as you

for example, from WO 2009/092719 is known. There is already the adjustment of the amount of swallowing such a gerotor pump by changing the effective

A meshing width between a rotatable inner rotor and a rotatable outer rotor as generally known in the art. Because with such a

Hydraulic pump, the center distance line of the two rotors - as well as in a gerotor machine - fixed in space, these approaches are also not suitable for use in high-torque rotary piston engine according to the orbit principle. Thus, the constructive task in the inventive

Machine a new and much more complicated type than a gerotor pump or gerotor machine.

The invention represents a further development of the

WO 2006/010471 known hydrostatic rotary piston engine, which is why in the following first on the already in the

Essentially known from the prior art general basic structure of the inventive hydrostatic

The rotary piston machine is received before the

inventive features will be explained.

The hydrostatic rotary piston engine, also called

In particular, low-speed high-torque rotary piston engine may be referred to, comprises acting as an output Power unit in the housing of the rotary piston engine

is arranged. The power section consists essentially of a fixed, centric stator, a

movable rotary piston and a centric rotatable

stored, serving as output shaft together.

The stator has a stator internal toothing with the

Number of teeth d. The rotary piston has a partially engaged in the stator inner teeth of the stator Kreiskolben- external teeth with a number of teeth c and a rotary piston internal teeth with a number of teeth b. The rotary piston has a rotary piston outer diameter. The shaft meshes with its first external shaft teeth with a number of teeth a partially the rotary piston internal teeth of the rotary piston, wherein the rotary piston arranged to perform an orbital movement so eccentric to the shaft axis and

is dimensioned and the numbers of teeth a, b, c, d are in such a relationship to each other, that with

Working fluid disposable and disposable tooth chambers between the stator inner teeth of the stator and the circular piston external teeth of the rotary piston form.

An inlet and outlet part is used for supply and disposal of the power unit with the working fluid, wherein the working fluid at a working pressure via a pressure connection, as

Input serves, the rotary piston engine can be supplied.

By means of a disc-shaped rotary valve, which is mounted centrically running to the shaft and the stator, the

Control of the supply and disposal of the dental chambers with the

Working fluid. In other words, the rotary valve is rotatably mounted about the central, longitudinally extending shaft of the geometric shaft axis. By means of the rotary valve is arranged over substantially radially in the rotary valve Pressure window the supply and disposal of the tooth chambers with the working fluid by rotation of the rotary valve so

Kommutierend controllbar that the working fluid of the

Pressure connection in a first part of the tooth chambers with the working pressure into and from a second part of the

Tooth chambers is directed out to a low pressure port, so that the working pressure in the first part of

Toothed chambers leads to an orbit movement of the rotary piston and the working fluid from the second part of the tooth chambers

displaced, whereby the shaft is set in rotation, and vice versa. The rotary valve has a specific rotary valve outside diameter, either by the actual

Outer diameter of the rotary valve or by the outer or average diameter of the disc-shaped

Pressure valve radially arranged pressure resistant is determined.

In addition, the rotary engine comprises a gear transmission in the form of an eccentric gear designed in particular as a wobble gear, which between a second

Shaft external teeth of the shaft with a number of teeth w and an internal toothing of a fixed internal gear with a number of teeth z is arranged as a synchronous drive for the rotary valve. Preferably, the eccentric gear, in particular the wobble gear, exclusively in

Leakage oil range of the hydrostatic rotary piston engine, so in non-working pressure leading area of the

Rotary piston engine, which is also connected to the low-pressure port arranged. The shaft is mounted on both sides of the power unit immediately adjacent radial bearings, in particular bearings. Due to the aforementioned structure of the hydrostatic rotary piston engine, a continuous shaft with large shaft diameters and high torsional strength can be used. Thus, it is possible to expose both shaft ends to a high torque flux and, for example, both

To use shaft ends as output, or one shaft end as the output and the other shaft end for connecting a brake or a second drive, whereby the entire

Drive unit can be made compact.

Since the rotary valve itself does not orbit movement, but rotates about the shaft axis, due to the

Accomodation of the eccentric gear in the oil leakage space of the engine and by the use of inexpensive extruded or sintered parts as gear members thus creates a compact and inexpensive construction.

Serving as a synchronous drive for the rotary valve,

in particular designed as a wobble gear eccentric gear has an eccentric, which has an eccentric internal teeth with a number of teeth x and an eccentric external teeth with a number of teeth y. The eccentric internal toothing partially meshes with a second shaft outer toothing of the shaft with a number of teeth w. The eccentric external teeth partially mesh with a fixed internal gear with a number of teeth z. The ratio of the numbers of teeth w, x, y, z is such that the eccentric eccentric to the

Shaft axis between the shaft and the internal ring gear during rotation of the shaft performs an orbit movement. One

pot-shaped connecting part is eccentric with the

rotatable eccentric rotatably coupled and with the centrically rotatable rotary valve, in particular in the ratio of 1: 1, rotatably on a particular tumbling or

eccentric connection is connected such that a Rotary movement of the shaft on the eccentric on the

Rotary valve is transferable.

Are each similar teeth engaged, the number of teeth a is smaller than the number of teeth b, the number of teeth c smaller than the number of teeth d, the number of teeth w smaller than the number of teeth x and the number of teeth y smaller than the number of teeth z, the respective tooth difference preferably one or two teeth.

In particular, the following equation known from the prior art represents the speed ratio shaft to the rotary piston or shaft to the rotary valve: b, x

- • a - c - z - y

w

d - c ^■ y

As can be seen from this equation, the numbers of teeth of the particular designed as a wobble mechanism

Exzentergetriebes be carried out quite differently

In the following, for the sake of simplification, only the term of the wobble mechanism is sometimes used, which generally also means an eccentric gear. A first option is, for example, the design exactly as in the power section, in particular with w = 12, x = 14, y = ll and z = 12. It should only be noted that the eccentricity of the two internal gears are exactly the same. The equation expression is a positive integer, preferably equal to 3. It must also be sought that in this

Range of diameter of the shaft is sufficiently large, so that their torsional strength for the maximum torque still sufficient. Here, however, the eccentricity of

Taumelgetriebes relatively large, so that the

Tumble angle is correspondingly large. However, then the rotational speed of the eccentricity is relatively small.

The relationship between the rotational speed Ne of the eccentricity of the wobble mechanism and the rotational speed Nw of the shaft is given by the equation

Ne_w - y

Nw x - z - w - y

this ratio is preferably between -3 and -9.

A second option is the preferred interpretation of

Number of teeth after a = 12, b = 14, c = ll, d = 12, w = 12, x = 13, y = 23 and z = 24 or after a = 12, b = 14, c = ll, d = 12 , w = 9, x = 10, y = 17 and z = 18, each with a very small eccentricity. As can be seen from the above equation Ne / Nw, the increases

Speed of eccentricity in this case.

In the design of the wobble mechanism with the numbers of teeth a = 12, b = 14, c = ll, d = 12, w = 12, x = 13, y = 23 and z = 24, there are known advantages: As in the assembly of the engine the rotational position of the rotary valve must always exactly match the rotational position of the motor in the power unit in the phase position, it makes sense that the number of teeth w and their rotational position on the shaft is exactly the same as the number of teeth a

External toothing on the shaft on the power unit and its rotational position. Thus, the shaft can always be mounted without having to pay attention to what rotational position it is, whereby the assembly is considerably simplified.

The proposed numbers of teeth a = 12, b = 14, c = ll, d = 12, w = 9, x = 10, y = 17 and z = 18 have the advantage with respect to the toothing for the wobble that the toothing module larger is, the stability of the shaft grows in this area and in particular the negative-running speed of the eccentric axis of the eccentric disc drops sharply, resulting in a smoother running of the transmission. It is thereby accepted that the wobble angle is slightly larger, and dispenses with the above-described advantage during assembly.

In an advantageous embodiment, the stator internal toothing is formed by circular cylindrical rollers, which leads to further increased pressure performance and excellent service life. Measurements have shown that by the transition to roles in the stator of the starting efficiency and also the

mechanical-hydraulic efficiency can be significantly increased.

To seal the disk-shaped rotary valve axially against leakage of the working fluid and with its pressure windows with sufficient pressure against the control plate with their

To push windows, which lead through channels to the tooth chambers, a rotationally fixed axial second balance piston is preferably provided, which acts axially on the rotary valve. The axial second compensating piston is arranged, for example, around the wobble gear. In particular, the fixed internal ring gear is in the axial second

Balancing piston formed. The force on the rotary valve is applied for example by means of a plate spring.

When using such a hydrostatic

High-torque motor as a wheel motor, the output-side radial bearing needs a higher radial load capacity for additional

Recording the wheel load. Preferably, it should be arranged as close to the center of the wheel. It is advantageous if this bearing is as close as possible to the wheel flange and

optionally outside the leakage space of the rotary piston engine is arranged with a permanent rolling bearing grease directly in the housing part of the rotary piston engine. The described

Rotary engine is suitable due to the advantageous

Bearing arrangement and the powerful, optionally continuous shaft, among other things outstanding as a wheel motor for direct driving a wheel. In this case, the shaft is preferably formed integrally with a wheel flange on which a wheel for direct drive is directly mountable.

Instead of the wobble mechanism described above, however, a classic eccentric gear, whose eccentric performs no tumbling movement, but parallel to

Shaft shaft turns, be used. In this case, there is an eccentric connection with a difference in number of teeth between both the eccentric internal teeth and the

Wellenaussenverzahnung, including between the eccentric external teeth and the fixed inner ring gear, as well as between a second eccentric outer teeth and an inner ring gear of the rotary valve.

According to the invention, this feature combination, which is essentially known from the prior art, is followed

further education.

According to the invention, the rotary piston is relative to

fixed stator and axially displaceable relative to the axially fixed shaft parallel to the shaft axis. For this purpose, the first shaft outer teeth of the shaft and the stator inner teeth of the stator extend axially such that the rotary piston inner teeth on the first shaft outer teeth and the outer circular piston teeth on the stator inner teeth can be moved axially. In order to move the rotary piston axially, the rotary piston engine adjusting, which with the

Rotary piston axially to its axial displacement are engaged. Under adjustment means are generally means for axially displacing the rotary piston to understand

in particular hydraulic, mechanical, pneumatic or electric drives which can be arranged inside or outside the housing of the rotary piston engines. In particular, the adjusting members between the rotary piston and the rolling bearings are left and right axially displaceable.

By means of the axial displacement of the rotary piston, the axial longitudinal extent of the tooth chambers and thus the volume of the tooth chambers is adjusted continuously. For this purpose, a radially ersteckende first wall of the tooth chambers is axial

fixed and axially coupled to the housing. By contrast, a radially extending second wall of the tooth chambers is axially displaceable together with the rotary piston and axially coupled to the rotary piston. The second wall is the first wall spaced parallel opposite, wherein the

Toothed chambers between the first and second wall are arranged and extend there axially.

The first wall is formed by a so-called circular piston plate and the second wall by a so-called stator plate. The circular piston plate and the stator plate seal the tooth chambers axially. This means that both between the stator plate and the stator internal teeth and the circular external teeth, as well as between the

Circular piston plate and the stator internal teeth and the circular piston external teeth is a tight contact. Thus, the tooth chambers of the stator, the

Rotary piston plate, the stator internal teeth and the

Limited circular piston external toothing. According to the invention, the rotary piston plate is axial

fixed and radially coupled to the rotary piston so that it also performs the orbital motion of the rotary piston. According to the invention, the rotary piston plate coupled radially to the rotary piston has, in the housing, a free mobility in the radial direction and in the circumferential direction corresponding to the orbital movement of the rotary piston plate. The stator plate, however, is axially movable and axially coupled to the rotary piston, but decoupled radially from the rotary piston, so that they so no orbital motion and no rotational movement performs, but is rotationally fixed. The volume of the tooth chambers according to the invention by the axial displacement of the rotary piston and thus also the

Stator plate by means of adjusting continuously

changeable by the distance between the axial

sliding stator plate and the axially fixed

Circular piston plate can be downsized and enlarged.

Preferably, the axially fixed circular piston plate engages with its circular piston plate internal teeth in the

Spherical external teeth, both of which have the number of teeth c and have similar toothing geometries, so on a sealing manner in the axial direction fit accurately that the rotary piston relative to the axially fixed

Rotary piston plate is axially displaceable. Due to the

The accuracy of fit of the circular piston plate internal teeth with the circular piston external teeth are both in axial sealing, but axially movable contact.

In one embodiment of the invention is the

Circular piston plate in the housing so radially sealed is that the circular piston plate seals the tooth chambers outwards during their orbit movement. this happens

for example, characterized in that the circular piston plate is mounted in a disc-like recess in the housing, in particular between a first housing part and a second housing part of the housing, radially movable and radially sealing. The radial sealing takes place in particular by means of a stator adjacent to the radially outward

extending, pointing in the axial direction wall, on which a likewise radially extending, pointing in the axial direction wall of the rotary piston plate, which performs the orbital movement, slides.

The axially movable stator plate preferably engages with its stator outer teeth in the stator inner toothing in the axial direction sealing manner a precise fit. For this purpose, the stator plate external teeth and the stator internal teeth have the same number of teeth d and essentially the same

Tooth geometry. Thus, the stator plate is axially displaceable relative to the axially fixed stator together with the rotary piston. Due to the fit of the

Stator plate external teeth with the stator internal teeth are both in axially sealing, but axially movable contact.

In a development of the invention, a compensating piston is axially coupled to the stator plate. It is possible to integrally form the stator plate and the balance piston. The balance piston engages in an axial

Adjusting cylinder on. The balance piston is arranged in the fixed housing and acted upon by the working pressure of the working fluid of the tooth chambers, by a direct or indirect connection between the Compensating cylinder and the pressure connection exists. The

Pressurization takes place in such a way that the working pressure in the compensating cylinder over the stator plate at least partially counteracts the working pressure in the tooth chambers and thus a force on the rotary piston in the direction of a

Starting position with a reduced volume of

Dental chambers acts. Thus, on the one side of the axially displaceable stator plate, a first force resulting from the working pressure in the first part of the tooth chambers acts on the opposite other side of the stator plate, a second force resulting from the working pressure in the first

Balancing cylinder results, exercised. These two forces counteract each other and partially compensate, so that the axial holding and adjusting force of the rotary piston is reduced.

In order to support this compensation of forces and / or to force a starting position of the rotary piston in the unpressurized state of the rotary piston engine, provides a development between the balance piston and the balance cylinder acting control springs axially against the rotary piston and thus the rotary piston in the direction of a starting position with a compensation piston Press the reduced volume of the tooth chambers. The control springs thus act in the same direction as the working pressure in the

Compensation cylinder.

The balance piston and the balance cylinder have

for example, a ring shape and in particular extend around the shaft. Preferably, they are between the

Power part and the wobble gear arranged.

According to the invention can balance piston and

Balancing cylinder to be reversed. Under a Balancing piston is thus according to the invention also a

To understand compensation cylinder, and vice versa.

The invention provides in a development of the invention that the adjusting members are designed as a control piston which is axially engaged with the rotary piston. In other words, the control piston is so axially coupled to the rotary piston, that the rotary piston by means of the control piston is axially displaceable. The control piston engages in an axial control cylinder arranged in the fixed housing such that a force can be exerted on the rotary piston for axial displacement of the rotary piston and for changing the volume of the tooth chambers. For this purpose, the control cylinder can be acted upon by a control pressure. Preferably, the

Control cylinder and the control piston arranged such that the rotary piston is displaced by the pressurization in the control cylinder in a direction such that the

Volume of the tooth chambers with increasing control pressure

increased. In other words, an increasing causes

Control pressure an increase in the volume of the dental chambers.

The control piston and the control cylinder may be arranged annularly in the housing around an output section of the shaft in a ring-shaped manner, wherein the output section corresponds to that

Section of the shaft on which the wobble gear is arranged opposite.

In order to transmit the axial force from the control piston to the circular cylinder, for example, a radially extending intermediate disc is arranged between the control piston and the rotary piston. The rotary piston slides in

Execution of his orbital motion with his in axial

Direction facing end face on a facing in the opposite axial direction surface of the washer. The control piston is arranged, for example, such that it presses the rotary piston in particular via this washer against the opposite balance piston and in particular against the control springs. In other words, the working pressure in the compensating piston counteracts the control pressure in the control piston kinematically.

The control pressure in the control cylinder can in a possible variant of the invention by the working pressure of

Working fluids are generated. For this purpose, there is in particular such a direct or indirect connection between the pressure connection and the control cylinder that the control piston can be acted upon by the working pressure of the working fluid. In this case, the control pressure is equal to the working pressure. The effective surfaces of the control cylinder, the control piston, the stator plate, the rotary piston plate and optionally the compensating cylinder and the balance piston are in this case preferably dimensioned such that the control cylinder with increasing torque on the driven shaft and thus with increase in working pressure the rotary piston in the direction of an enlarged Volume of the tooth chambers presses.

Conversely, a decrease in the volume of the tooth chambers is caused by a decrease in torque and drop in working pressure. Thus, the swallowing volume decreases with increasing

Torque off and on decreasing torque. This makes it possible, high speeds at a relatively low output torque, low displacement and

To achieve relatively low working fluid throughput, for example, when driving faster with a vehicle, whereas at low speed, a high torque with a large displacement is available, for example when accelerating or when driving slowly uphill. Also included is a kinematic reversal of the invention. In addition, it is possible to equip the rotary engine with a control pressure connection, which is connected to the control cylinder such that a control pressure from the

Control pressure connection acts on the control piston. Thus, the volume of the rotary engine by changing the

Control pressure can be varied. In one development of the invention, the control piston can be acted upon, in particular by means of a valve, either with the working pressure of the working fluid or with a control pressure from the control pressure port.

The hydrostatic rotary piston machine according to the invention can be used not only as a motor for generating an output, but is also excellently suitable as a pump. In other words, the hydrostatic rotary piston engine has the great advantage that a recuperative

Brake energy recovery is possible by the specially designed as a wheel motor hydraulic motor is switched in the case of braking to a pumping operation and receives torque. This sucks hydrostatic

Rotary piston engine, the working fluid from the tank and promotes this under pressure in one or more

Hydraulic accumulator. The stored energy can be stored in the

Connection while driving again be used. Because of the risk of cavitation negative pressures of about 0.2 to 0.4 bar

Not to fall below atmospheric pressure, it is possible by means of the inventive rotary piston engine, the

Negative pressure by varying the swallow volume of

To set tooth chambers as described above such that a limit negative pressure is not exceeded. The

Suction volume of the rotary piston engine can therefore change, in particular reduced, when there is a change from traction mode to overrun mode, which is also called suction or pumping mode in particular to reduce the risk of cavitation in suction operation.

To reduce the above-mentioned cavitation danger, in particular during pumping operation and to enable an even higher rotational speed of the rotary piston engine, it is advantageous to design the rotary valve as large as possible. Preferably, the rotary valve with its Druckfestern in relation to the rotary piston on an enlarged rotary valve outer diameter. In particular, the rotary valve outer diameter is larger by a factor of 1.3 to 1.5 than the outer diameter of the rotary piston.

The inventive hydrostatic rotary piston engine can thus as an economic direct drive, in particular

Hub drive with recuperative braking energy recovery can be used in a vehicle. The variable

Suction volume allows economic operation of the rotary piston engine, since the displacement of the

adjust current power and torque requirements and thus hydraulic losses can be reduced.

The function and mode of action of the inventive

volume-variable hydrostatic rotary piston engine will be explained below purely by way of example with reference to the figures 1 to 8, which illustrate concrete embodiments, to which the invention is not limited.

In detail show:

1 shows a longitudinal section through a wheel motor

formed inventive hydrostatic

Rotary piston engine in the position of working and adjusting members with maximum absorption per shaft revolution;

Figure 2 is a same longitudinal section in the position of

Working and adjusting with minimum

Amount of swallow per shaft revolution;

3 shows a cross section along the section line A-A of

Figure 1, in which the work spaces as tooth chambers between the orbiting rotary piston and the

Stator are visible;

Figure 4 shows a cross section along the section line B-B of

Figure 1, the axially displaceable, but not rotatable, the axial wall of the tooth chambers

representing stator plate, which is hatched from bottom left to top right, in cross section; Figure 5 shows a cross section along the section line C-C of

Figure 1, which shows the non-axially movable, but together with the rotary piston an orbital movement exporting circular piston plate, which is hatched from bottom right to top left, in cross section; a longitudinal section through the wheel motor in the range of required pressure lines to

Actuation of axially acting compensation surfaces which are to be under the working pressure;

Fig. 7 shows a longitudinal section through the wheel motor in the region of the required pressure lines to

Actuation of trained as a control piston Adjustment organs to be under the control pressure;

Fig. 8 is a longitudinal section through an alternative

Embodiment of a wheel motor according to the invention in the position of the working and adjusting organs with maximum absorption per shaft revolution, wherein a spread of the amount of swallowing in the ratio of about 6: 1 is possible; and

9 is a longitudinal section through an alternative,

more complex embodiment of a hydrostatic rotary piston engine as a wheel motor in the position of the working and adjusting at maximum

Suction rate per shaft revolution.

In the following, possible embodiments with reference to several figures, which partially show a single embodiment in different views with sporadically different levels of detail, shown, the figures are partly explained together. Reference is made to features and reference signs already mentioned in the preceding figures.

The working pressure of the

Working fluid in the form of a working fluid is

For example, during forward travel of the wheel motor shown in Figure 1 a pressure port 1 of an inlet and outlet part 53 in the housing 19, so that one with the pressure port

I connected outer annular space 2 is applied to a disk-shaped rotary valve 3 with pressure, as shown in Figure 1. The disk-shaped rotary valve 3 is a

Shaft axis 50 of a shaft 11 centrally rotatable and to the shaft

II centric continuously stored. By the commutation of the Rotary valve 3 flows the working fluid through window 7 in a power section 51st

As shown in FIG. 3, the power unit 51 has a center fixed stator 52 having one

cylindrical rollers 13 formed stator inner teeth with the number of teeth d = 12, a rotary piston 8 with a

Partially into the stator inner teeth 13 engaging circular piston outer teeth 12 with a number of teeth c = ll, a circular piston internal teeth 9 with a number of teeth b = 14 and a rotary piston outer diameter 68. In addition, the power unit 51 includes the centered about the shaft axis 50 rotatably mounted Wave 11 with a partial in the

Rotary internal teeth 9 engaging first shaft external teeth 10 with a number of teeth a = 12. The rotary piston 8 is thus for performing an orbital movement

arranged eccentrically to the shaft axis 50 and the numbers of teeth a, b, c, d are, as shown above, dimensioned such that with working fluid ver and disposable tooth chambers 6 radially between the stator inner teeth 13 and the

Form a circular piston external toothing 12.

The rotary valve 3 ver and disposed of the tooth chambers 6 via axial channels 4 and radial channels 5 in the stator 52 with the working fluid such that the working fluid of the as

Input-acting pressure port 1 in a first part 6a of the tooth chambers 6 with the working pressure into and out to a low-pressure connection acting as an output from a second part 6b of the tooth chambers 6 out.

To the largest possible amount of working fluid in the

To be able to guide tooth chambers 6 into and out of the tooth chambers, the rotary valve 3 has as large a size as possible

Rotary valve outer diameter 69, as shown in Figures 1, 2 and 7 can be seen. Preferably, the Drehventil- outside diameter 69 is larger by a factor of 1.3 to 1.5 than the outer diameter of the rotary piston 68. Since the rotary valve 3 together with windows 7 ensures that, for example, in Figure 3, only the first part 6a of the tooth chambers 6 is applied to the left of the axial distance DD with working pressure, the rotary piston 8 rotates in Figure 3 in

Clockwise while outputting its torque over the

Circular piston internal teeth 9 of the rotary piston 8 and a first shaft outer teeth 10 of a shaft 10, wherein the working fluid under lower pressure in the second part 6b of the tooth chambers 6 right of the center distance D-D

displaced and discharged via the low pressure port 70. The torque can be tapped via a driven out of the housing 19 output-side portion 65 of the shaft 10. The rotary piston 8 and the shaft 10 rotate in the same direction, as shown

Embodiment in the clockwise direction, as illustrated in Figure 3 by the two arrows.

The rotary valve 3 is in a known manner by means of a

Taumelgetriebes 56, as a synchronous drive for the

Rotary valve 3 is used, driven. An eccentric 57 of the

The wobble mechanism 56 has an eccentric internal toothing 58 with a number of teeth x and an eccentric external toothing 59 with a number of teeth y. The eccentric internal toothing 58 meshes with a second shaft outer toothing 60 of the shaft 11 with a number of teeth w. The eccentric external teeth 59 meshes with a fixed internal gear ring 61 with a number of teeth z. The numbers of teeth w, x, y, z are dimensioned such that the eccentric 57 performs eccentric to the shaft axis 50 between the shaft 11 and the inner ring gear 61 during rotation of the shaft 11 an orbital movement. Possible number of teeth combinations can be found in the above statements. A pot-shaped connecting part 62 is rotatably coupled to the eccentrically rotatable eccentric 57 at one end. Otherwise it is

cup-shaped connecting part 62 with the centrally rotatable rotary valve 3 1: 1 rotatably connected via a tumbling connection. A rotational movement of the shaft 11 is thus transmitted via the eccentric 57 to the rotary valve 3.

The shaft 11 is radially mounted on both sides of the power section 51 adjacent radial bearings 63, which are designed as rolling bearings in O arrangement.

In order to fix the rotary valve 3 axially and to seal axially against leakage of the working fluid, a rotationally fixed axial second compensating piston 55, which acts axially on the rotary valve 3, arranged around the wobble gear 56. Of the

fixed internal ring gear 61 is formed within this axial second balance piston 55. This mode of operation of a hydrostatic rotary piston engine is essentially known from WO 2006/010471.

The amount of swallowing and thus the torque that the

Rotary piston 8 and the shaft 11 passes, hang

decisively on how large the effective width of the tooth engagement in the tooth chambers 6 between a

Circular external gear teeth 12 and the stator internal teeth 13 is. In the figure 3, the stator internal teeth is shown in the form of rollers 13, which is a particularly advantageous embodiment of this tooth shape

represents serious advantages.

According to the invention, the rotary piston 8 with his

Rotary piston inner toothing 9 on the first shaft External teeth 10 relative to the shaft 11 and with his

Spherical external teeth 12 on the stator inner teeth 13 relative to the stator 52 parallel to

Shaft axis 50 axially displaceable. The displaceability is made possible by adjusting members 22, which are in engagement with the rotary piston 8 and by means of which same axially

is displaceable. The tooth chambers 6 are arranged in the axial direction between an axially fixed circular piston plate 17 and an axially movable stator plate 14. They are by the circular piston plate 17 and the

Stator plate 14 axially limited and sealed. The

Circular piston plate 17 is axially fixed and radially coupled to the rotary piston 8. Thus, it performs the orbital motion of the rotary piston 8 together with the rotary piston 8. The stator plate 14 is axially movable, axially with the

Rotary piston 8 coupled and radially from the rotary piston. 8

decoupled. The volume of the tooth chambers 6 is thus continuously variable by the axial displacement of the rotary piston 8 and the stator plate 14 by means of the adjusting members 22. in the

Below we explain this general arrangement in more detail.

The axially movable stator plate 14, which in Figure 4 in

Cross-section is shown, engages with their Statorplatten- external teeth 64 in the stator inner teeth 13 with the number of teeth d = 12 in a sealing manner in the axial direction fitting that the stator plate 14 relative to the axially fixed stator 52 together with the rotary piston 8 axially displaceable is. With the stator 14 is a - in particular annular - compensating piston 15a axially coupled. The compensating piston 15 a is formed by a piston extension of the stator plate 14. In other words, the balance piston 15a and the

Stator plate 14 integrally formed. This Balancing piston 15a is arranged in the stationary housing 19 and can be acted upon by the working pressure of the working fluid of the toothed chambers 6. The compensating piston 15a engages in an axial - in particular annular - compensating cylinder 15b in such a way that the working pressure in the compensating cylinder 15b via the stator plate 14 to the

Working pressure in the tooth chambers 6 counteracts and thus a force on the rotary piston 8 in the direction of

Starting position with a reduced volume of

Dental chambers 6 acts. Between the compensating piston 15a and the compensating cylinder 15b act control springs 16 which press the compensating piston 15a axially against the rotary piston 8 and thus the rotary piston 8 in the direction of a starting position with a reduced volume of the tooth chambers 6.

As can be seen from FIG. 1, the width of the

Tooth engagement between the circular piston external teeth 12 and the stator inner teeth 13 is particularly bulky, so that accordingly a large displacement per

Rotary piston rotation and thus per shaft revolution is generated. In this case, the stator plate 14 with its piston neck, which forms the balance piston 15 a, together with the

Rotary piston 8 moved to the right. The control springs 16 are completely compressed and thereby generate the highest possible axial force on the stator plate 14. Here is the highest possible regulated working pressure in the

Toothed chambers 6 reached, if this is not yet to be increased over the block size of the control springs 16, which would be quite possible.

In FIG. 2, the stator plate 14 is in its left limit position. The control springs 16 are largely relaxed, corresponding to a low pressure in the tooth chambers 6. The effective width of the tooth engagement between the rotary piston External teeth 12 and the stator inner teeth 13 is greatly reduced. This results in the desired strong reduction of the specific amount of swallowing in the ratio of the reduced effective tooth width to the maximum effective tooth width in FIG. 1. The transition from the maximum

effective tooth width to the minimum effective tooth width can be done continuously, which is why a stepless

Control of the swallowing amount is possible. The closing of the tooth chambers 6 to the left in the

Figures 1 and 2 is performed by the circular piston plate 17. This has a circular piston plate internal teeth 18, which corresponds exactly to the circular piston external teeth 12 of the rotary piston 8, wherein a movement of a few hundredths of a millimeter is provided, so that a high degree of tightness between the tooth chambers. 6 and the non-pressurized interior of the machine. This running clearance need not be greater than that it is ensured that the rotary piston is axially displaceable therein. This circular piston plate 17 must thus join the orbit movement of the rotary piston 8 with as little friction loss. It is not axial

movable and is guided radially movable with a minimal axial play between the housing parts 19a and 19b. The

Circular piston plate 17 is thus in a disc-like

Recess in the housing 19 between a first housing part 19a and a second housing part 19b mounted radially movable and radially sealing. In the housing 19 thus one of the orbital movement of the rotary piston plate 17 corresponding free mobility in the radial direction and in the circumferential direction is provided.

Figure 5 shows a cross section through the axial center of this circular piston plate 17, into which a groove 20 is radially inserted from the outside, so that by the orbital movement of the Circular piston plate 17 between a housing ring 21 displaced viscous working fluid does not generate excessive crushing losses. The adjusting members 22 are, as shown in Figures 1 and 2, as an annular centric to the

Output section 65 of the shaft 11 arranged control piston 22 a formed, which is axially in engagement with the rotary piston 8 via a radially extending washer 66, as shown in Figures 1 and 2. The control piston 22a is arranged such that it presses the rotary piston 8 against the compensating piston 15a and against the control springs 16 via the intermediate disc 66. In the housing 19, an axial control cylinder 22 b is arranged, which is acted upon by a control pressure and in which the control piston 22 a engages such that by means of the control pressure in the control cylinder 22 b, a force on the rotary piston 8 for axial displacement of the rotary piston 8 can be exercised. Because of this

Moving the volume of the tooth chambers 6 can be actively changed in particular. Both the control piston 22a and the control cylinder 22b annularly surround the output section 65 of the shaft 11 in an annular manner.

That it is even possible to design a rotary piston engine according to the orbit principle so that a stepless

Change in the swallow volume is due to the fact that according to the execution of such

Machine according to WO 2006/010471 the torque-generating rotary piston 8 transmits its torque via its rotary piston internal teeth 9 to the first shaft external teeth 10 of the shaft 11, on which the rotary piston. 8

is axially movable and there against tilting a good

Leadership relationship gets. The axial force vectors in this rotary engine are equal in any way without offset, but run past each other at a considerable distance. While the force of the balance piston 15a on the stator plate 14 and the control piston 22a exactly offset in the center of the machine and compensate in part, the resulting hydraulic axial force of the tooth chambers 6 is significantly offset from the piston forces. This results in a considerable tilting moment on the one hand on the stator plate 14 and the

Circular piston plate 17 and thus also on the rotary piston 8. To avoid tilting and resulting large frictional forces, it is necessary for both the rotary piston 8 and in particular for the stator plate 14 with her

Balance piston 15 a good leadership relationship. Therefore, it is preferable that the balance piston 15a is fixedly connected to the stator plate 14 to improve the guide ratio. Furthermore, it is desirable to constructively, as well as the tooth engagement between the rotary piston internal teeth 9 and the first shaft external teeth 10 as long as possible out.

Extensive tests have shown that even under high working pressure the required axial displacement in both directions is possible with almost no hysteresis. It must be ensured that the corresponding sliding surfaces under load are worked as smoothly as possible.

In FIG. 6 channels 71 are shown in which the

Working pressure from the pressure port 1 to the balance piston 15a, to the compensating cylinder 15b and to a compensating pressure field 23 for the rotary piston plate 17 is passed. Valves 24, in particular check valves, ensure that the

Working pressure at different directions of rotation is always directed to the right place. As shown in FIGS. 1 and 2, in a first embodiment of the invention, such direct or indirect connection between the pressure port 1 and the control cylinder 22b is that the control piston 22a communicates with the control piston 22a

Working pressure of the working fluid is applied, so that the control piston 22a with increasing working pressure the rotary piston 8 and the stator plate to the right in the in Figure 1

shown position with an increased volume of the tooth chambers 6 suppressed, so that the torque increases with increasing working pressure. The working pressure in the control piston 22a thus counteracts the control springs 16 as well as the

Working pressure in the tooth chambers 6.

In another embodiment, shown in Figure 7, the rotary piston engine has a control pressure port 67 which is connected to the control cylinder 22b via lines such that the control piston 22a can be acted upon with a control pressure from the control pressure port 67. In FIG. 7, therefore, a separate pressure line with a control pressure connection 67 is provided for the supply of the regulating piston 22a. Thus, it is possible to reduce the amount of

Rotary piston engines, in particular depending on the design of the control springs 16 even substantially independent of

Working pressure and torque of the active by varying the control pressure to adjust.

There are two adjustment conceivable:

When the control pressure port 67 is connected to the pressure port 1, the engine automatically operates as

Torque converter. As in the application of the wheel motor as a vehicle drive with increasing driving resistance of

Working pressure at the pressure port 1 and the control pressure port 67 increases, increases the force of the control piston 22 a and displaces the rotary piston 8 against the control springs 16 in the direction of a larger meshing width and thus in the direction of a larger amount of intake. Since the torque generated on the shaft 11 from the product pressure times

The amount of swallowing calculated increases the torque of the

Rademotors disproportionately to increase the pressure, so that the traction of the drive increases accordingly dramatically.

This automatism can be modified by the design of the core lines of the control springs 16. At a constant flow rate of the supply pump, which supplies the working fluid to the pressure port 1, which is driven for example by an internal combustion engine, automatically reduces the output speed of the rotary piston engine and thus the input speed of the wheels. The

Vehicle speed therefore drops. This results in a similar behavior as in a hydrodynamic

Föttinger converter, as it is used in almost all automatic transmissions. The efficiency of the hydrostatic

However, converter is better than the hydrodynamic converter, since the oil flow losses are smaller.

In the current effort to use as much braking energy recuperatively, however, is another kind of

Regulation makes sense. As explained above, such orbit motors can only be used to a limited extent as hydraulic pumps. When braking from high vehicle speed, the hydraulic motor can be operated as a pump only with a small amount of swirl due to the risk of cavitation. Does that fall?

Vehicle speed in the course of the braking process, however, from, the amount of swirl of the variable wheel motor in

increased inversely proportional to speed decrease. In this regulation, care must be taken that the total amount of oil produced by the hydraulic motor has a certain

Limit does not exceed. As already mentioned, the promotes Hydraulic motor when braking as a pump, the fluid against a largely constant accumulator pressure. The braking torque can thus only with decreasing vehicle speed

Increasing the absorption volume can be increased in compliance with the mentioned limit of the oil flow rate. In this case, a pressure independent and thus

Demand-dependent regulation required. This is done via a control pressure at the control pressure port 67. A big advantage in the inventive

volume-variable hydrostatic rotary piston engine, as well as in the hydraulic motor according to WO 2006/010471, the continuous wave. FIG. 8 shows an alternative embodiment of a volume-variable hydrostatic head according to the invention

Rotary piston engine with a along the shaft axis 50 elongated rotary piston 8, an elongated shaft 11, a longer control piston 22a and a longer

Control cylinder 22b and a greater distance from

Stator plate 14 and circular piston plate 17 and thus also a larger adjustment of the adjusting 22 shown. As a result, a spread of the swallow volume with the value 6: 1 is achieved. This corresponds to

Gearbox transmissions a 6-speed gearbox with the

corresponding design effort. Opposite the

Embodiment of the wheel motor according to Figure 1 and Figure 2, this is only about 16% longer. The remaining features correspond to the features of the previous one

Embodiment to which reference is hereby made.

Figure 9 shows a longitudinal section through a complex

Embodiment of a wheel motor according to the invention in the position of the working and adjusting at maximum Suction amount per shaft revolution, wherein to reduce the axial bearing distance of the radial bearing 63 both the

Balancing cylinder 15b and the control springs 16 are moved radially outward and the eccentric 56 is designed as a classic Exzentergetiebe with an alternative 1: 1- connection to the rotary valve. The

Eccentric 56 has an eccentric 57 with a

Eccentric internal teeth 58 and an eccentric external teeth 59 on. The eccentric internal teeth 58 meshes with a second shaft outer teeth 60 of the shaft 11. The eccentric external teeth 59 meshes with a

fixed internal ring gear 61. The numbers of teeth are dimensioned such that the eccentric 57 eccentric to

Shaft axis 50 between the shaft 11 and the inner ring gear 61 during rotation of the shaft 11 performs an orbit movement.

Possible number of teeth combinations can be found in the above explanations. A cup-shaped connecting part 62 is rotatably connected to the eccentrically rotatable eccentric 57 at one end

coupled. At the other end, the cup-shaped connecting part 62 is connected in a rotationally fixed manner via an eccentric connection to the centrically rotatable rotary valve 3. A rotational movement of the shaft 11 is thus transmitted via the eccentric 57 to the rotary valve 3. Of course, the invention is not limited to the exemplary embodiments shown schematically and illustrated here in the drawings. For example, a kinematic reversal is possible according to the invention, in which the shaft 11 is stationary and the housing 19 rotates, which at

Wheel motors and other applications can bring certain benefits.

Claims

Hydrostatic rotary piston engine according to the orbit principle

• an output acting in a housing (19)

arranged power section (51), the

- A centric fixed stator (52) with a stator inner toothing (13) with the

Number of teeth d,

- A rotary piston (8) with a partially in the

Stator internal toothing (13) engaging rotary piston outer toothing (12) with a number of teeth c, a circular piston internal toothing (9) with a number of teeth b and a rotary piston outer diameter (68), and

- A centrally about a shaft axis (50) rotatable

mounted shaft (11) with a partially in the

Circular piston internal teeth (9) engaging first shaft external teeth (10) having a number of teeth a, wherein the rotary piston (8) for performing an orbital movement is so eccentric to the shaft axis (50) and the numbers of teeth a, b, c, d such are dimensioned such that dental chambers (6) which can be supplied and disposed of with working fluid form radially between the stator internal toothing (13) and the external circular toothing (12),

• An inlet and outlet part (53) for supply and disposal of the power section (51) with the working fluid, with a pressure port (1) as input for the under

Working pressure standing working fluid,

• a disc-shaped rotary valve (3), which around the

Shaft axis (50) centrically rotatable and to the shaft (11) and the stator (52) is centrally running, for such Kommutierenden control of supply and disposal of the tooth chambers (6) with the working fluid that the Working fluid in a first part (6a) of the tooth chambers (6) with the working pressure into and out of a second part (6b) of the tooth chambers (6) out to generate the drive or driven output, wherein the

Rotary valve has a rotary valve outer diameter (69),

• an eccentric gear, in particular a

Wobble gear (56), as a synchronous drive for the

Rotary valve (3), with

- An eccentric (57) having an eccentric internal teeth (58) with a number of teeth x and a

Eccentric external toothing (59) having a number of teeth y, wherein the eccentric internal toothing (58) with a second shaft outer toothing (60) of the shaft (11) with a number of teeth w and the eccentric external toothing (59) with a fixed

Internal toothed ring (61) meshes with a number of teeth z, wherein the number of teeth w, x, y, z are dimensioned such that the eccentric (57) eccentric to

Shaft axis (50) between the shaft (11) and the inner ring gear (61) upon rotation of the shaft (11) a

Orbit movement performs, and

- A pot-shaped connecting part (62) which rotatably with the eccentrically rotatable eccentric (57)

is coupled and in particular 1: 1 rotatably connected to the centrally rotatable rotary valve (3) via a particular tumbling or eccentric connection such that a rotational movement of the shaft (11) via the eccentric (57) on the rotary valve (3) transferable is

and

Two radial bearings (63) arranged on both sides of the power section (51) and arranged on the shaft (11) for radially supporting the shaft (11),

characterized in that the rotary piston (8) with its circular piston internal toothing (9) on the first shaft outer toothing (10) relative to the shaft (11) and with its circular piston outer toothing (12) on the

Stator internal toothing (13) relative to the stator (52) parallel to the shaft axis (50) is axially displaceable, adjusting members (22) with the rotary piston (8) are engaged, by means of which the rotary piston (8) is axially displaceable,

the tooth chambers (6) in the axial direction between

- An axially fixed and radially with the

Rotary piston (8) coupled, the orbital movement of the rotary piston (8) exporting circular piston plate (17) and

- An axially movable, axially with the rotary piston (8) coupled and radially from the rotary piston (8) decoupled stator plate (14)

are arranged and by the circular piston plate (17) and the stator plate (14) are axially sealed, wherein the volume of the tooth chambers (6) by the axial

Moving the rotary piston (8) and the stator plate (14) by means of the adjusting members (22) continuously

is changeable,

the radially coupled to the rotary piston (8)

Circular piston plate (17) in the housing (19) one of

Orbitbewegung the circular piston plate (17) corresponding free mobility in the radial direction and in

Having circumferential direction and

the circular piston plate (17) in the housing (19) is guided so radially sealing that the circular piston plate (17) during its orbit movement, the tooth chambers (6) seals to the outside.

2. Hydrostatic rotary piston engine according to claim 1, characterized in that

the axially fixed circular piston plate (17) with a

Piston plate internal teeth (18) in the

Circular piston external toothing (12) with the number of teeth c in such a tight fit in the axial direction sealing manner that the rotary piston (8) relative to the axially fixed circular piston plate (17) is axially displaceable.

Hydrostatic rotary piston engine according to claim 1 or 2, characterized in that

the circular piston plate (17) in a disc-like recess in the housing (19), in particular between a first housing part (19a) and a second housing part (19b) of the housing (19) is mounted radially movable and radially sealing.

Hydrostatic rotary piston engine according to one of

Claims 1 to 3,

characterized in that

the axially movable stator plate (14) with a

Stator plate external teeth (64) in the stator inner toothing (13) with the number of teeth d engages in such a tight fit in the axial direction sealing manner that the stator plate (14) relative to the axial

stationary stator (52) is axially displaceable together with the rotary piston (8).

5. Hydrostatic rotary piston engine according to one of

Claims 1 to 4,

characterized in that a particularly annular compensating piston (15a) is axially coupled to the stator plate (14) arranged in a stationary housing (19), with the

Working pressure of the working fluid of the tooth chambers (6) acted upon, axial and in particular annular compensating cylinder (15b) engages such that the

Working pressure in the compensating cylinder (15b) on the stator plate (14) at least partially counteracts the working pressure in the tooth chambers (6) and thus a force on the rotary piston (8) in the direction of

Starting position with a reduced volume of

Tooth chambers (6) acts.

Hydrostatic rotary piston engine according to claim 5,

characterized in that

the stator plate (14) and the balance piston (15a) are integrally formed.

Hydrostatic rotary piston machine according to claim 5 or 6, characterized by

between the balance piston (15a) and the

Balancing cylinder (15b) acting control springs (16), the balance piston (15a) axially against the rotary piston (8) and thus the rotary piston (8) in the direction of

Starting position with a reduced volume of

Press tooth chambers (6).

Hydrostatic rotary piston engine according to one of

Claims 1 to 7,

characterized in that

The adjusting members as a control piston (22a)

are trained

• the control piston (22a) is in axial engagement with the rotary piston (8) and • The control piston (22a) arranged in a fixed housing (19), with a control pressure

acted upon, axial control cylinder (22b) engages such that by means of the control pressure in the

Control cylinder (22b) a force on the rotary piston (8) for axial displacement of the rotary piston (8) and for changing the volume of the tooth chambers (6) is exercisable.

Hydrostatic rotary piston engine according to claim 8, characterized in that

The control piston (22a) and the control cylinder (22b)

annularly centered about a driven portion (65) of the shaft (11) in the housing (19) are arranged.

Hydrostatic rotary piston machine according to claim 8 or 9, referring back to one of claims 5 to 7,

characterized in that

the control piston (22 a) is arranged such that it in particular via an intermediate disc (66) the

Rotary piston (8) presses against the balance piston (15a) and in particular against the control springs (16).

Hydrostatic Kreiskolbenmaschme after one of

Claims 8 to 10,

characterized in that

Such a direct or indirect connection between the pressure port (1) and the control cylinder (22b) is that the control piston (22a) can be acted upon by the working pressure of the working fluid.

Hydrostatic rotary piston engine according to one of

Claims 8 to 11,

marked by

a control pressure port (67) connected to the Regulating cylinder (22b) is connected such that the

Regulating piston (22a) with a control pressure from the

Control pressure port (67) - in particular optionally instead of the working pressure of the working fluid from the pressure port (1) - can be acted upon.

13. Hydrostatic rotary piston engine according to one of

Claims 1 to 12,

characterized in that

the stator internal teeth by circular cylindrical rollers

(13) is formed.

14. Hydrostatic rotary piston engine according to one of

Claims 1 to 13,

marked by

a rotationally fixed axial second compensating piston (55) which acts axially on the rotary valve (3), the rotary valve (3) seals axially against leakage of the working fluid and in particular around the wobble gear (56) and in particular the fixed internal ring gear

(61).

15. Hydrostatic rotary piston engine according to one of

Claims 1 to 14,

characterized in that

the rotary valve outer diameter (69) is larger by a factor of 1.3 to 1.5 than the outer diameter of the rotary piston (68).