DE2533776A1 - ROTATING MOTOR - Google Patents

Description

Patent attorney

. FBÄßZ WERDERSft

2 HAMBURG 36 c.0, Λ 75

New Wall 10 Il

G. 75 081 bt.

Gordon Torquer, Ltd. Concord, Caliph. (V, St.A.)

Rotary motor

For this application, priority is derived from the corresponding U.S. Registration Ser. No. 493 720 dated August 1, 1974.

The invention relates to a rotary motor of low Frictional resistance and predetermined leakage flow properties, either by means of a pressurized Fluid such as gas as a prime mover or as a pressure-generating machine, i.e. as a working machine such as E.g. a pump can be operated.

Several rotary motors which can be operated either as motors or pumps are already known. In displacement type rotary motors Pistons, blades, wings or the like are used, which are in a liquid-tight seal within of a housing against a chamber wall delimiting the working medium. The speed range and the efficiency there are narrow limits to these machines. The machines usually have a complicated structure and are therefore expensive to manufacture and maintain. The starting friction and the wear and tear of the moving parts, especially on the seals, are very high. aside from that

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Many known machines cannot be dynamically balanced, which leads to increased design requirements and of course has a detrimental effect on the service life, maintenance requirements and power consumption. So is for example, the rated power of known air pressure engines is limited by the fact that large engines are not arbitrary can be operated at high speeds.

Turbines can overcome many of the aforementioned difficulties by dynamically balancing turbines can be designed for very high speed ranges and have a relatively long service life and low Need maintenance. On the other hand, there are higher construction and manufacturing costs for turbines, especially for the turbine blades. Since turbines are inherently operated with "leakage flow", they must with run relatively high speeds in order to achieve an acceptable level of efficiency. Simple turbines are also not easily reversible.

The object of the invention is now to create a rotary motor suitable for use as a work or power machine low frictional resistance and predetermined leakage flow properties, which with a simple structure within a can be operated in a wide speed range and in many different sizes for different engine outputs is interpretable.

According to the invention, this object is achieved by a Rotary motor consisting of a housing in which an annular chamber is concentric to a first axis in the longitudinal direction of the machine is formed, as well as serving for supplying and removing working medium to and from the annular chamber Inlet and outlet openings consists and is characterized by one rotatable about the inside of the housing

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piston carrier plate mounted on the first axis and adjoining the annular chamber on one side, several on the circumference of the piston support plate held at mutual distances from this in the longitudinal direction in the Piston protruding into the annular chamber and rotating together with the piston carrier plate, one on the opposite one Side of the annular chamber between the inlet and outlet openings, about one to the first longitudinal axis parallel second axis rotatably mounted check valve with a recess which can be brought into a position in which practically completely surrounds a piston, and one for rotating the shut-off valve around the second axis in temporal allocation to the rotation of the piston carrier plate and to the movement of the piston carrier plate attached piston through the recess of the shut-off valve serving transmission, the shut-off valve making the connection practically completely interrupted between the inlet and outlet openings.

The rotary motor proposed according to the invention is a hybrid form of displacement machine and turbine. There If there are no sliding surfaces between the piston, rotor and housing, there are friction, heat generation and wear is reduced and the lubrication of these parts is therefore not required. However, lubrication can be provided and in some cases allows the efficiency of the given leakage flow to be increased.

Due to the size dimensions and the mutual assignment of the shut-off valve and the inlet opening overlap the pressure strokes of the pistons. The pistons that rotate within the annular chamber and displace the working medium are dynamically balanced as moving parts. The fluid leakage between the piston and the annular chamber is so far given that no to seal the annular chamber

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Liquid seals are required, but at the same time the efficiency over a relatively large Speed range can be maintained.

The gaseous or liquid working medium serves as seals between the piston and the annular chamber, whereby the efficiency these seals increases with increasing speed.

The rotary motor has a relatively simple structure and consists of relatively few parts, for which no tight tolerances and liquid seals are required, so that for this reason alone the manufacturing costs are kept low. The machine has self-cleaning properties and can therefore do not block because small particles carried along by the working medium easily get past the piston and the valve can.

The rotary motor can be used within a wide speed range, with the efficiency even at low Speeds is maintained. The direction of rotation of the rotary motor can be quickly reversed and has a low starting friction resistance and can be brought to a start from any rotational position of the rotor.

The rotary motor can be made in many different sizes, and larger sizes become larger Efficiency achieved. The power-to-weight ratio is relatively high.

For example, three pistons are attached to the piston carrier plate, which together with the circular piston carrier plate are inside rotate around the annular chamber. The check valve rotatably mounted on the opposite side of the annular chamber has a concave recess of such a shape that when the stop valve rotates in a ratio of 3: 1 to

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Rotor, i.e. the piston carrier plate, the recess one after the other practically completely embraces the individual pistons. Inlet and outlet ports are on opposite sides Sides of the shut-off valve and are used to supply or discharge working medium such as compressed gas into and out of the Chamber. The inner and outer surfaces of each piston generally correspond to those radially inward and outward, respectively Walls of the annular chamber, the pistons having a distance from these walls, so that no friction arises and the working medium can flow around the piston in a predetermined leakage flow. The pistons also have generally radially extending flat side walls and can be passed through without contact at a very small distance move the check valve through, the latter practically completely eliminating the connection between the inlet and outlet openings interrupts. The leakage flow of working medium from the chamber through a non-contact and therefore friction-free space between the rotor and the housing in a pressure chamber formed by the sealed housing is also specified.

The rotary motor according to the invention is described below with reference to the exemplary embodiments shown in the drawings explains in more detail which is

1 shows an axial section through a rotary motor designed according to the invention,

Fig. 2 is a cross-sectional view taken along line 2-2 of Fig. 1 showing the various parts are in a first operating position,

3 shows a cross-section corresponding to FIG. 2, with the various parts in another Are in the operating position,

FIG. 4 shows a cross section corresponding to FIG. 2, wherein

the different parts are in a different operating position,

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Figure 5 is a partial end view in one essential part larger scale to illustrate the shape of one of the FIGS. 2-4 piston shown and

6 shows a partial cross-section of a further embodiment of the invention with an enlarged Outlet opening.

The rotary motor 10 according to the invention shown in FIG. 1 is especially designed as a pressurized gas engine. When used as a prime mover, the one serving as the output shaft Motor shaft 11 via a drive connection not shown here coupled with the power receiver. For example, if the rotary motor 10 is equipped with a flow control valve is coupled in a gas pipeline, compressed gas withdrawn from the gas pipeline is used as the working medium used for the rotary motor. The rotary motor is also suitable for other working machines, as well as a working machine, i.e. a pump suitable for increasing the pressure of a medium, the motor shaft 11 being driven.

The rotary motor 10 has a housing consisting of three parts on, which consists of a central cylinder block 12, a bell-shaped Cover 13 on one end of the cylinder block and a mounting cover 14 on the other end of the cylinder block consists. The three housing parts are in the form of a pressure-tight chamber by several on the circumference in mutual Spaced bolts 16 connected, which passed through holes on the circumference of the two covers and are screwed onto the threaded nuts 17.

The outer end surface 18 of the cylinder block 12 forms an annular chamber concentric to the cylinder block longitudinal axis 21 19 with the side walls 22 and 23, which are located at a mutual radial spacing, and a bottom wall 24.

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The motor shaft 11 is rotatable about the longitudinal axis 21 by means Bearings 26, 27 mounted, which are inserted into a corresponding bore of the cylinder block 12. Using As a prime mover, the motor shaft 11 is via a Drive connection connected to the power receiver, while when used as a work machine the Motor shaft is driven by a drive such as an electric motor. The housing is mediated against the motor shaft a conically tapered sealing ring 25 sealed pressure-tight. The inside diameter of the sealing ring 25 has annular grooves into which O-ring seals 15 are inserted. Several inserted into the edge of the sealing ring 25 Springs 25a act on the sealing ring against a stationary bushing 30 which is inserted into an annular recess of the fastening cover 14 is inserted. The outer, flat end of the sealing ring 25 runs in sealing engagement against the Inner shoulder of bushing 30 µm. A rotor 28 in the form of a circular piston support plate is at one end of the Motor shaft 11 attached and also serves as a flywheel to compensate for the force impulses acting on the rotating parts. The inner end face 29 of the rotor protrudes radially outward beyond the outer side wall 23 of the annular chamber 19. The distance between the inside The end face 29 of the rotor and the outer end face 18 of the cylinder block are optimally adjusted, so that the movement is frictionless, but at the same time the leakage flow of fluid from the chamber around the Rotor is given around. The required clearance depends on the respective design features such as the surface texture and / or quality and the properties of the fluid used. If the rotary motor 10 is used as a pressurized gas motor, this gap is preferably dimensioned between 0.050 to 0.127 mm.

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The between the bell-shaped cover 13 and the Rotor 28 located. Space forms a chamber 31. That through the space between the rotor and cylinder block passing fluid escapes into this chamber, so that the internal housing pressure reaches a value which is almost equal to the pressure applied at the inlet port of the motor. This reduces the leakage current that would otherwise occur, with the result that the efficiency of the motor is not increased falls off. At the same time, the space between the cylinder block and the rotor allows a frictionless relative movement, where no seals are required.

Three pistons 32, 33 and 34 are attached to the periphery of the rotor 28 at equal mutual distances, each Piston protrudes into the annular chamber 19. The circular base surfaces 20 of the pistons are sealed in recesses inserted on the rotor, and each piston is held in place on the rotor by means of a bolt 21A, through a recess in the opposite one Is passed through the rotor side.

In Fig. 5 the shape of the piston 34 is shown, which corresponds to that of all three pistons. The piston is in Cross-section generally cylindrical, the diameter being slightly larger than the radial distance between inner and outer side walls 22 and 23, respectively, of the annular chamber 19. The inner and outer end surfaces 36 and 37 of each piston have a curvature which generally corresponds to the curvature of the inner or outer annular chamber wall. The distances between the piston surfaces and the chamber walls are preferably between 0.050 and 0.127 mm. Of the the same distance is provided between the flat end face 38 of each piston and the flat bottom wall 24 of the annular chamber 19. The distance between the piston surfaces and the chamber walls allows a friction-free relative movement

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and also serves to set the fluid leakage flow around the pistons in the sequence described below Way. The inner side flanks of each piston have flat, outwardly diverging surfaces 39, 41.

An inlet port 42 is formed on one side of the housing through which fluid is fed into the annular chamber. An outlet opening 43 on the opposite side of the housing serves to discharge the medium from the annular chamber. The inlet opening 42 is dimensioned in terms of its size and position in relation to the size and circumferential position of the shut-off valve 44 so that pressure medium passes into the recess 50 when a piston as shown in FIG. 4 is guided past the inlet opening. This acts behind the piston e ^v in pressure that builds up before the pressure on the leading piston drops, with the result that the effective pressure stroke for an engine with three pistons is approximately 130 °, ie 10 ° more than the angular distance of 120 ° between the pistons. In other words, the pressure strokes of the pistons overlap by at least 10 °. This avoids throttling of the motor and dead centers during operation, and the machine can start from any rotational position. Inlet and outlet openings are arranged symmetrically to one another on opposite sides of the shut-off valve and have the same flow cross-section, so that the operating parameters of the machine are the same in both directions of rotation.

The embodiment of the rotary motor according to the invention shown in FIG. 6 is designed for only one direction of rotation. The cylinder block 12 'has an elongated outlet opening 45a and a branch opening 45b. the Outlet opening 45a extends over an arc of a circle, which in relation to the diameter of the outlet opening at the embodiment described above much longer

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is. The arc length of the outlet opening preferably corresponds to at least half the outlet stroke of 120 ° between adjacent piston, i.e. 60 °. This allows the gas to be released earlier during the exhaust stroke of each piston so that a lower back pressure is created and the efficiency is increased.

The check valve 44 arranged between the inlet and outlet openings interrupts the direct connection between the two openings, so that the fluid must run around the annular chamber 19 on a circular path. The shut-off valve has a half cylinder 46, the diameter of which is greater than the radial width of the chamber. The cylinder is attached with its base to a shaft 47 which is rotatably mounted in bearings 48 about an axis 49. the Axis 49 runs parallel to the cylinder block longitudinal axis 21, in which the motor shaft is located. That of the wave facing base of the cylinder 46 is circular and rotatably held in an annular seat, which the housing passage opening for the shaft 47 surrounds. The opposite end of the cylinder is turned off and therefore at a small distance can be brought to the inner end face 29 of the rotor. A concave recess 50 is formed in the half cylinder 46, whose boundary wall has a much greater width than the outer diameter of the piston, so that the The recess practically completely surrounds the piston when the latter move past the valve. On the one of the recess opposite cylinder side a sufficiently large recess is formed to allow dynamic balancing for high speed operation.

The check valve 44 rotates in the opposite direction at a speed ratio of 3: 1 driven to the rotor 28. The transmission used for the drive preferably consists of a gear 52 large diameter, for example by means of a wedge

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is connected to the motor shaft 11, and a gear 53 of small diameter with a third of the number of teeth Gear 52, which is connected to shaft 47 by a key, for example. The two gears mesh with each other, so that the check valve executes three revolutions with each revolution of the rotor. The gear ratio is included adjusted so that the rotation of the shut-off valve is precisely timed to the movement of the successive Pistons 32 to 34 takes place, so that the latter move past the valve without contact, without there is a significant pressure drop in the inlet-side pressure at the valve.

The shape of the valve recess corresponds to the progressive operating positions shown in FIGS. 2-4 50 matched with respect to the shape of the piston in such a way that the piston is free of contact with the valve can be encompassed and at the same time only a minimum amount of fluid pass from the inlet to the outlet opening can. Based on the illustration of Fig. 3, it is assumed that the rotor 28 rotates clockwise, the Piston has just entered the rotary cross-sectional area of the check valve and the recess 50 is in a Has rotated the rotational position in which the piston can enter the recess 50. At the same time, the The front edge 56 of the recess 50 is displaced in the immediate vicinity of the front piston surface, but they do so not touched.

As the rotor continues to rotate, the piston 34 moves into the 12 o'clock position of the hour hand shown in FIG. at the same time the valve has rotated further so that its recess 50 points downwards. In this position the circular outer piston surface moves without contact at a short distance from the inner circular surface

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the recess. In addition, the two recess edges 56, 57 are located below the inner one in this position Side wall 22 of the annular chamber 19, so that the passage of fluid from the inlet to the outlet opening is practically blocked is.

As the rotor continues to rotate, the piston 34 moves into the exit position shown in FIG. 4, in which the inner End surface 36 of the piston has emerged from the valve and the rear edge 57 of the valve recess 50 is unobstructed can move upwards with the trailing piston surface at a small distance, but without contact. in the During the further rotation during a full revolution, the next two pistons 33 and 32 become the same Way moved through the check valve 44. The direction of rotation of the rotary motor can easily be reversed Check valve engages around the piston in the same way both clockwise and counterclockwise.

When using the rotary motor 10 according to the invention as of A pressurized gas source driven engine is the inlet port 42 via a pipeline or the like. And a corresponding throughput control device, not shown are connected to the pressurized gas source. When the rotor is first in the position shown in FIG is located, the pressurized gas passes through the inlet opening 42 in the right upper region of the annular chamber 19, in which it acts on the piston 32. The gas pressure acting on this piston gives the rotor a clockwise torque, this rotating the shut-off valve via the gears 52 and 53 drives counterclockwise. The rotor and piston have no sliding surfaces and can move without friction move within the annular chamber 19. Hence the starting friction resistance very low, and these parts do not require lubrication. The heat generation and the wear and tear

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are also low, and at overspeed the Surfaces of the parts not scratched as in known air motors. Because of the small gap The leakage flow around the piston 32 into the one behind the second piston 33 is between the piston and the annular chamber walls located space 58 predetermined and has a limited size. The enclosed gas volume serves as a gas seal, by creating a back pressure against the pressurized volume behind the piston 32. The effectiveness this air or gas seal increases with increasing rotor speeds, as there is a leakage of gas from the Chambers less time is available with each stroke. Due to the small gap between the outer circumference of the rotor and the housing also restricts gas leakage into chamber 31. With this, the pressure reaches within the annular chamber of the housing a value which almost corresponds to the pressure on the inlet side, so that a leakage flow around the rotor is tied around. Another advantage is that the end-side thrust loading of the bearings due to the equally high pressure forces acting on the rotor inside the housing is reduced, which affects the service life the camp benefits.

In the course of the further rotation of the rotor, the parts successively move into those shown in FIGS. 2 and 4 Positions in which the shut-off valve 44 engages around the piston 34 without contact, while the latter passes through the valve is moved through, the connection between the inlet and outlet opening being interrupted. As soon as the trailing Piston 34 passes the inlet opening, an increasingly higher pressure builds up on its rear side, with the pressure continues to act on the next advancing piston 32. This state prevails over an angle of rotation of approximately 10 ° to the trailing piston 34 at the Leading edge of the inlet opening into that shown in FIG

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Location is moved past. The effective pressure stroke is therefore 130 °. The gas pressure in space 58 between pistons 32 and 33 acts as a back pressure through which the fluid leakage flow around the piston 32 is limited. This state continues until the piston 33 is in front of it the outlet opening 43 is located, so that the trapped in space 58 Gas can escape through the outlet opening.

Since all parts of the rotary motor 10, including the rotor and check valve, are dynamically balanced and the pistons are free of contact and therefore frictionless move against the annular chamber walls and the check valve, very high speeds are possible. Because of the low frictional resistance results in a very low starting moment of inertia compared to machines with mutual Frictionally engaged parts where the starting resistance is higher than the rotating torque. the The direction of rotation of the rotary motor can also be quickly reversed at high speeds by inserting the compressed gas into the outlet opening 43 is supplied, the inlet opening now being switched as an outlet opening. This reversibility is of particular advantage when differential response is desired, such as differential control in Closing a valve or gate. The operating characteristics of the motor are the same in both directions of rotation.

The rotary motor can be operated not only in the manner of a turbine at high speeds, but with an acceptable degree of efficiency also within a wide speed range. At low speeds, the good efficiency is based on the Displacement properties of the motor as the leakage flow around the pistons is limited. At higher speeds the efficiency increases due to the reduction in leakage current. With larger machines, you can also get a higher Achieve efficiency, as the distances are essentially un-

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can be kept changed. This is due to the fact that the ratio of piston dimensions to Leakage current gap increases accordingly. Larger machines of the embodiment according to the invention can be operate at high speeds due to the low frictional resistance and dynamic balancing, whereby much higher nominal powers can be achieved. For example, when the motor size is doubled, the nominal power becomes increased by a factor of 8.

The rotary motor 10 is relatively inexpensive to manufacture, since there is no need to adhere to tight tolerances between the piston, chamber and valve. There are no sliding surfaces are available, no special requirements are placed on the surface quality. The machine elements can be made of materials that are compatible with the work or Flow medium are selected. If the working medium consists of harmful gases or vapors, for example, the parts can be made of stainless steel. For high-temperature gases, parts made of ceramic material can be used use. The rotary motor according to the invention can even be produced from materials that would otherwise be used for rotary motors known training are unthinkable. For example, due to the finite distance between the moving parts and the gas seal should also use refractory materials due to the backflow effect. The machine can come in much larger dimensions than machines with frictionally engaged parts or conventional ones Turbines are manufactured.

Since the piston, valve and chamber walls keep a mutual distance from each other, a "seizure" or Jamming excluded, which would otherwise be a danger in machines with tight tolerances, especially when small particles of foreign matter between the moving parts

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or they get due to wear and tear or thermal expansion change their dimensions. Due to the relatively free passages, the machine develops one Self-cleaning effect in that small foreign matter particles carried along by the fluid do not settle between the Can deposit elements. Piston, valve and chamber walls do not require lubrication because there are no tight tolerances and Sliding surfaces are available.

The rotary motor according to the invention can be in many different Sizes with practically unchanged construction for a large performance range of fractions of a kW up to the size of a power plant. Since the machine has relatively few and small parts, can achieve a relatively low power-to-weight ratio (i.e. ratio of engine power to engine weight).

The drive torque acting on the pistons does not have any significant gas expansion as in e.g. machines with variable Chamber volume result. This essentially works full force is applied to the pistons, and pressure surge loads are avoided.

The volumetric fuel consumption of the. The machine is mainly dependent on the speed and the inlet pressure and relatively independent of the performance. In comparison, it occurs in known air motors Pressure loss, as the incoming wings or vanes have to be moved against the pressure medium.

The rotary motor according to the invention is also suitable as a compound machine, the output of a rotary motor being given by Fluids discharged into the inlet port of a second machine of the same leakage flow characteristics Type is initiated in order to increase the overall efficiency.

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Torque fluctuations can be further reduced by that two or more rotary motors are out of phase with each other on a common shaft be coupled.

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Claims (19)

2b33776 claims: 1. Rotary motor, consisting of a housing in which is concentric to a first axis in the longitudinal direction of the machine an annular chamber is formed, as well as for supplying and removing working medium to and from the Annular chamber serving inlet and outlet openings, characterized by an inside of the housing (12, 13, 14) rotatably mounted around the first axis (21) and on one side against the annular chamber (19) adjacent piston support plate (28), several on the Perimeter of the piston carrier plate held at mutual distances from this in the longitudinal direction in the annular chamber in protruding and together with the piston carrier plate rotating piston (32, 33, 34), a on the opposite-side of the annular chamber between inlet and outlet openings (42 and 43) arranged to one the first longitudinal axis parallel to the second axis (49) rotatably mounted shut-off valve (44) with a recess (50), which can be brought into a position in which it practically completely surrounds a piston, and one for the rotary drive of the shut-off valve around the second axis in a temporal assignment to the rotation of the piston carrier plate and to move it through the piston attached to the piston support plate serving through the recess of the check valve Transmission (52, 53), the shut-off valve practically providing the connection between the inlet and outlet openings completely interrupts. 2. Rotary motor according to claim 1, characterized in that a total of three arranged at equal mutual distances Pistons (32, 33, 34) are provided, each piston frictionally spaced from the chamber walls has, which is dimensioned so that in the space (58) between the acted upon by the medium leading 6098 0 9/0346 and trailing piston, a pressure used to limit leakage flow across the trailing piston can be maintained. 3. Rotary motor according to claim 2, in particular for a gaseous working medium, characterized in that the in the space (58) maintainable pressure as the leakage limitation serving gas seal of with increasing Speed of the piston carrier plate increasing efficiency is used. 4. Rotary motor according to claim 2, in particular for a gaseous working medium, characterized in that the Distance between 0.050 and 0.17 mm. 5. Rotary motor according to claim 1, characterized in that the housing comprises a cylinder block (12), the piston carrier plate (28) has a friction-free distance from the cylinder block on its outer circumference, and the housing forms a closed space around the circumferential piston carrier plate, which is used to accommodate the through the intermediate space passing medium and for pressure storage of this medium for the purpose of limitation serves for a further leakage flow through this gap. 6. Rotary motor according to claim 1, characterized in that the check valve (44) consists of one rotatable about the second Axis (49) mounted half cylinder (46), the outer diameter of which is greater than the radial distance between the inner and outer walls of the annular chamber (19), the boundary wall of the recess (50) being a has such a shape that the pistons can be moved through the shut-off valve which surrounds them at small intervals are. 7. Rotary motor according to claim 6, characterized in that the boundary wall of the recess (50) in the half cylinder (46) has a concave shape that is open to the outside on one cylinder side. 8. Rotary motor according to one of claims 1-7, characterized in that that the inlet opening (42) in the successive passage of the pistons (32, 33, 34) in A connection with the recess (50) in the check valve (44) can be brought about and the trailing side of the piston with it the inlet-side pressure can be applied, the next, advancing piston is still pressurized and the pressure strokes of the pistons are partially mutually exclusive overlay. 9. Rotary motor according to claim 8, characterized in that when the piston passes successively the inlet port (42) on the trailing piston, a pressure increase takes place at a rate which comparable is that of the pressure drop on the following advancing piston. 10. Rotary motor according to claim 9, characterized in that the trailing piston during the pressure increase an arc of at least 10 ° in front of the inlet opening (42) runs through and the pressure strokes of the pistons are superimposed in an angular range of at least 10 °. 11. Rotary motor according to claim 1, characterized in that the annular chamber (19) inner and outer, in mutual Radially spaced annular walls (22, 23) and the pistons (32, 33, 34) at a mutual radial spacing located inner and outer surfaces (36,37) from the radii of the inner and outer annular chamber walls each in approximately the same radius RAW 2 b 3 3 7 7 have, with the piston surfaces in question are friction-free at a distance from the inner and outer ring wall, which has a certain leakage flow of Medium allows. 12. Rotary motor according to claim 7, characterized in that each piston (32, 33, 34) opposite one another, radially has extending side walls, the check valve (44) in its orbital motion with the piston carrier plate (28) is coupled and the boundary wall of the recess (50) with little play on the side walls of successive Pistons can be passed, which can be moved through the shut-off valve that encompasses them. 13. Rotary motor according to claim 1, characterized in that the piston carrier plate (28) consists of a flywheel high circular rotor body serving to compensate for force pulses acting on the piston carrier plate Moment of inertia exists. 14. Rotary motor according to claim 1, characterized in that the inlet and outlet openings (42, 43) on opposite sides Sides of the check valve circumference are arranged and the inlet opening is larger than the piston, such, that an adjacent piston can be acted upon tangentially by means of medium entering through the inlet opening under pressure and thus the motor can be started up in any rotational position of the piston carrier plate. 15. Rotary motor according to claim 1, characterized in that Inlet and outlet openings are arranged symmetrically to one another on opposite sides of the shut-off valve (44) and have the same flow cross-section. 609809 / (1346 2b33776 16. Rotary motor according to claim 1, characterized in that the transmission (52, 53) used to drive the shut-off valve (44) has a transmission ratio of Piston support plate (28) to check valve (44) of 1: 3, so that the check valve with one full revolution the piston carrier plate three, which executes three pistons consecutively encompassing revolutions. 17. Rotary motor according to claim 1, in particular with a single direction of rotation, characterized in that the outlet opening (45a) in the direction of piston movement for the purpose of ejecting working medium and reducing dynamic pressure is elongated during the exhaust stroke of each piston. 18. Rotary motor according to claim 17, characterized in that the outlet opening (45a) extends over an arcuate area which corresponds to at least half the outlet stroke. 19. Use of the rotary motor according to one of claims 1 as Pump, characterized in that the inlet port (42) is connected to a source of a gaseous or liquid Medium connected, the piston carrier plate (28) by means of a drive device around the first axis (21) can be put into circulation and the medium can be sucked in through the inlet opening and under pressure through the outlet opening (43) is deliverable. ■ R 0 9 8 Π 9/0 3 U 6 Blank page