EP2213878B1 - Rotating piston engine - Google Patents

Description

The invention relates to a rotary piston machine according to the preamble of claim 1.

State of the art

The publication DE 2262776 A1 discloses a radial piston machine which is suitable for use as a pump, compressor or motor. A disadvantage of this machine is the fact that the torques and forces generated thereby are relatively limited, and that the construction of the pump is relatively complex and therefore expensive. The publication WO 92/08892 discloses a rotary piston machine according to the preamble of claim 1. A disadvantage of this machine is, inter alia, that this has an unstable running behavior.

Presentation of the invention

The object of the invention is therefore to form an economically advantageous rotary piston engine.

This object is achieved with a rotary piston machine having the features of claim 1. The dependent claims 2 to 14 disclose further advantageous embodiments.

The object is achieved in particular with a rotary piston machine comprising a main bearing forming a first rotation center, comprising a drum which is rotatably mounted on the main bearing about the center of rotation, comprising a sub-camp, which forms a second center of rotation, wherein the main bearing and the sub-camp disposed in that the first and second rotation centers are mutually parallel and mutually eccentric, comprising a manifold rotatably supported by the sub-bearing about the second rotation center, and comprising a plurality of piston-cylinder assemblies, each piston-cylinder assembly pivotally connected at one end to the drum and at the other end thereof to the manifold, the piston-cylinder assemblies being circumferentially spaced apart from each other in the circumferential direction of the drum, and the piston-cylinder assemblies being transversely spaced one by the first or z wide rotational center defined radial direction.

The rotary piston engine according to the invention further comprises a synchronization device, which is configured such that the drum and the distributor rotate mutually synchronously, wherein the synchronization device is designed as a mechanical coupling comprising a distributor driver, which is concentrically connected to the distributor, wherein the distributor driver a plurality in The journal having a plurality of circumferentially spaced, parallel to the first center of rotation extending bearing journal, wherein the bearing pins of the drum and the bearing pins of the distributor driver are each arranged along a circular line with the same diameter, and wherein the bearing journals are arranged mutually extending, that in each case two bearing pins are connected via a rolling connection, wherein the rolling connection rotatable with respect to the bearing journal is stored.

The rotary piston engine according to the invention comprises a plurality of piston-cylinder arrangements, that is to say two or more piston-cylinder arrangements, for example 2, 3, 4, 5, 6, 7, 8, 9, 10, 11 or 12 piston-cylinder arrangements. Arrangements which are arranged distributed in the circumferential direction and operated simultaneously. The piston-cylinder arrangements are advantageously arranged uniformly spaced in the circumferential direction. This plurality of piston-cylinder arrangements gives the rotary engine according to the invention excellent Tracking characteristics, which also manifests itself in that the rotary piston machine during operation has a low-vibration behavior. The rotary piston machine according to the invention has the advantage that it is suitable for a large number of different applications. The rotary piston machine according to the invention can be used, for example, as a pump for a liquid or as a compressor for a fluid, in particular for a gaseous fluid. The rotary piston engine according to the invention is also particularly suitable for pumping viscous conveyed material such as concrete. Characterized in that at the same time move a plurality of piston-cylinder assemblies, the medium to be conveyed, the medium to be conveyed very evenly promoted, especially when the rotary piston machine has a relatively large number of, for example, 6 or more piston-cylinder assemblies. The discharged medium emerging from the rotary piston machine thus preferably has no or only slightly pulsating flow behavior.

The speed of the rotary piston engine and thus also the funded volume of the piston-cylinder arrangement can be varied by a corresponding control of the speed in a very wide range. The rotary piston machine may, depending on the structural embodiment, be operable up to a maximum speed of 20,000 to 30,000 revolutions per minute. In an advantageous embodiment, the rotational speed of the rotary piston machine can be varied, thereby varying the delivery rate. The rotary piston engine according to the invention also has the particular advantage that it also with a very low speed of, for example, 1 revolution per minute or even slower to operate. This is advantageous, for example, if a viscous conveyed material such as concrete is conveyed. Known pumps for concrete have the disadvantage that the concrete is not continuously but due to the pump used periodically promoted, causing beating noises. The rotary piston machine according to the invention makes it possible, for example, to continuously convey concrete, without beating noises, and in addition the amount of concrete conveyed per unit of time can be set very precisely and also varied very precisely by a corresponding activation of the rotational speed of the rotary piston engine.

However, the rotary piston engine according to the invention can also be used as an engine by supplying the piston-cylinder assemblies with a pressurized fluid, such as a liquid, a gas or, for example, water vapor, which drives the engine. The inventive rotary piston engine can also be used as an expander to expand a gas and convert the energy released thereby via the rotary piston engine into mechanical energy. In a particularly preferred embodiment, the inventive rotary piston machine is operated both as a compressor and as a motor, for example by compressed air in a first step and then stored, and in a second step, the compressed air is relaxed again, and the rotary piston engine as an engine is operated. In an advantageous embodiment, the rotary piston engine according to the invention could be used, for example, in an automobile by at least partially effecting deceleration is that is compressed by the rotary piston engine, which is stored in a pressure vessel, and by the startup or acceleration of the automobile is at least partially effected by the compressed air is supplied to the rotary piston engine, so as to drive or accelerate the car. In a further advantageous embodiment, the rotary piston engine could also be used in connection with the use of solar energy by the resulting in a solar system hot steam is supplied to the piston-cylinder assemblies of the rotary piston engine, so that it is driven. For example, the rotary engine may be connected to an electric generator to generate electrical power.

The rotary piston machine according to the invention has the advantage that it is compact and inexpensive to produce, that the rotary piston engine can record or dispense a relatively large power, and that it is reliable and low maintenance operable. The inventive rotary piston engine can therefore be used in a variety of applications. The rotary piston machine according to the invention has the further advantage that it can be dimensioned in various sizes, so that, for example, a motor can be formed as required with a shaft power of a few watts up to a motor with several megawatts. The drum can be configured, for example, depending on the requirements of the medium to be conveyed with a diameter of a few centimeters, for example 2 cm or 3 cm, up to a diameter of several meters, for example 1 m or 2m. The inventive rotary piston engine is for example, suitable for stationary operation in a power plant, or a non-stationary operation in a motor vehicle.

In an advantageous embodiment, the rotary piston machine according to the invention is operated with a gaseous fluid. In a particularly advantageous embodiment, the supply and removal of the gaseous fluid is effected with a mechanical rotary valve, so that the rotary piston engine according to the invention can be operated purely mechanically and without additional electronic components in an advantageous embodiment. Such a rotary piston engine is particularly inexpensive and also very reliable operable.

The invention is explained below with reference to drawings in detail.

Brief description of the drawings

Fig. 1

schematisch eine Drehkolbenmaschine;

Fig. 2

eine perspektivische Seitenansicht eines Teils einer Drehkolbenmaschine;

Fig. 3

und 4 zwei perspektivische Ansichten einer Drehkolbenmaschine;

Fig. 5

eine Ansicht der Rückseite einer Drehkolbenmaschine;

Fig. 6

ein Hauptlager, ein Nebenlager, einen Verteiler sowie einen Zylinder;

Fig. 7

eine perspektivische Ansicht eines Nebenlagers mit Verteiler;

Fig. 8

eine Seitenansicht eines Verteilers;

Fig. 9

eine perspektivische Ansicht eines Nebenlagers, das Teil eines Drehschiebers bildet;

Fig. 10a, 10b, 10c

eine zweite Trommelscheibe, einen Verteilertreiber sowie deren gegenseitige Verbindung;

Fig. 11

eine perspektivische Ansicht einer zweiten Trommelscheibe;

Fig. 12

eine perspektivische Ansicht eines Verteilertreibers;

Fig. 13

eine Rollverbindung;

Fig. 14

schematisch die gegenseitige Verbindung von zweiter Trommelscheibe und Verteilertreiber über eine Mehrzahl von Rollverbindungen;

Fig. 15

eine erste Trommelscheibe;

Fig. 16

ein Schnitt durch ein Gelenkteil;

Fig. 17

einen Längsschnitt eines Zylinders;

Fig. 18

einen am Verteiler befestigten Zylinder.

The drawings used to explain the embodiments show:

Fig. 1

schematically a rotary piston machine;

Fig. 2

a side perspective view of a part of a rotary piston machine;

Fig. 3

and Fig. 4 two perspective views of a rotary engine;

Fig. 5

a view of the back of a rotary engine;

Fig. 6

a main bearing, a sub-camp, a distributor and a cylinder;

Fig. 7

a perspective view of a sub-camp with distributor;

Fig. 8

a side view of a distributor;

Fig. 9

a perspective view of a sub-camp, which forms part of a rotary valve;

Fig. 10a, 10b, 10c

a second drum disc, a distributor driver and their interconnection;

Fig. 11

a perspective view of a second drum disc;

Fig. 12

a perspective view of a distributor driver;

Fig. 13

a roll connection;

Fig. 14

schematically the mutual connection of second drum pulley and distributor driver via a plurality of rolling joints;

Fig. 15

a first drum disc;

Fig. 16

a section through a hinge part;

Fig. 17

a longitudinal section of a cylinder;

Fig. 18

a cylinder attached to the manifold.

Basically, the same parts are given the same reference numerals in the drawings.

Ways to carry out the invention

Fig. 1 schematically shows a rotary piston machine 1 comprising a first drum pulley 4a, which is rotatably mounted on a main bearing 5 about a first rotation center 5a. In the main bearing 5, a sub-bearing 7 is arranged, which forms a second center of rotation 7a, wherein a distributor 6 is rotatably mounted on the sub-bearing 7. The first and second rotation centers 5a, 7a are mutually parallel and mutually eccentric. The rotary piston engine 1 comprises a plurality of piston-cylinder assemblies 10, 10a-10h, wherein each piston-cylinder arrangement 10, 10a-10h comprises a piston 8 and a cylinder 9, the piston 8 being displaceable in the direction of its travel in the cylinder 9 is stored. In the illustrated embodiment, all the pistons 8 are pivotally connected at the end 10i with a connecting means 4c with the first drum pulley 4a. All cylinders 9 are pivotally connected to the distributor 6 at their end 10k. In the illustrated embodiment, eight piston-cylinder assemblies 10, 10a-10h arranged mutually spaced in the circumferential direction of the drum 4 and in the circumferential direction of the manifold 6, wherein the piston-cylinder assemblies 10, 10a-10h transversely or obliquely to a through the first or second rotation center 5a, 7a defined radial direction. Not shown in FIG. 1 the claimed synchronization device 16, which is designed such that the drum 4 and the distributor 6 rotate mutually synchronously.

During operation of the rotary piston engine 1, both the first drum pulley 4a and the distributor 6 rotate synchronously in the direction of rotation A, with the first drum pulley 4a rotating about the drum The first rotation center 5a rotates, and the distributor 6 rotates around the second rotation center 7a. This rotation causes the piston-cylinder assemblies 10, 10a-10h are moved in the direction of rotation A, wherein the respective piston-cylinder assemblies 10, 10a-10h due to the eccentrically arranged centers of rotation 5a, 7a, depending on the rotational position of Rotary piston machine 1 have a different length, since the piston 8 is inserted at different depths in the cylinder 9. In the in FIG. 1 illustrated embodiment, for example, in the piston-cylinder assembly 10f shown below, the piston 8 is fully retracted into the cylinder 9, while the in FIG. 1 Piston 8 shown above is maximally extended from the cylinder 9. Rotation of the first drum pulley 4a and the sub-bearing 7 through 360 degrees causes each piston-cylinder assembly 10, 10a-10h to perform a complete stroke movement. Thus, for example, the small internal volume of the piston-cylinder arrangement 10 shown at 10f increases by one turn by 180 degrees to the piston-cylinder arrangement 10b shown in FIG. 10b, whereby the internal volume decreases again during further rotation until after a rotation of 360 Degree the piston-cylinder assembly 10 again has the position shown with 10f small internal volume. During rotation, the internal volume of the individual piston-cylinder assemblies is thus periodically increased and decreased. The rotary piston engine 1 according to the invention therefore also has excellent synchronous running properties. The rotary piston engine 1 can be used, for example, as an engine by supplying a pressurized gas to the piston-cylinder assemblies 10, so that the rotary piston engine 1 rotates in the direction of rotation A. The rotary piston machine 1 can, for example, as a compressor can be used by a gas is supplied to the piston-cylinder assemblies 10 and compressed therein, wherein the rotary piston machine 1 for compression in the direction of rotation B rotates. Instead of a reversal of the direction of rotation could also, as in FIG. 4 3, the fluid inlet 7b and the fluid outlet 7c for the supplied and discharged fluid are interchanged to thereby operate the rotary engine 1 either as a motor or as a pump / compressor.

FIG. 2 shows in a perspective side view of an embodiment of a rotary piston machine 1, wherein the claimed synchronization device 16 is not shown. The main bearing 5 is fixedly connected to a bracket 3. The holder 3 is fixedly connected to a base plate 2. The first drum pulley 4a is rotatably supported by the main bearing 5. The distributor 6 is rotatably supported by the auxiliary bearing 7. The piston-cylinder assemblies 10 are, as in FIG FIG. 1 described in detail, with the first drum pulley 4a and the distributor 6 connected. In an advantageous embodiment, a ball bearing is arranged in each case between the main bearing 5 and the first drum pulley 4a and between the sub-bearing 7 and the distributor 6, in order to effect the most smooth and low-wear bearing possible.

The FIGS. 3 and 4 show in perspective views from different directions another embodiment of a rotary piston engine 1. In contrast to the in FIG. 2 In the disclosed embodiment, the first drum disk 4a is provided with a plurality of circumferentially spaced connecting means 4c with a second drum disk 4b connected, so that the two drum discs 4a, 4b form a drum 4 together with the connecting means 4c. The pistons 8 of the piston-cylinder assemblies 10 are pivotally connected to the connecting means 4c. The sub-camp 7 is rotatably mounted in the main bearing 5. In the auxiliary bearing 7 shown, this has a fluid inlet 7b and a fluid outlet 7c. FIG. 5 shows the in FIG. 4 perspective view shown in a front view, wherein in FIG. 5 In addition, a locking device comprising an adjustment 7d and a fixing member 7e is arranged, wherein the adjusting member 7d is fixedly connected to the sub-bearing 7 to axially rotate the sub-bearing 7 with respect to the main bearing 5, and to fix the fixing member 7e at the desired angle. Instead of the adjusting part 7b, for example, a motor drive device acting directly on the auxiliary bearing 7 could be provided in order to turn the auxiliary bearing 7 by motor. Preferably, this motor drive device is connected to a control device, not shown.

FIG. 6 shows components of the FIGS. 3 to 5 The main bearing 5 comprises a bearing portion 5 b which is insertable into the holder 3. The main bearing 5 also comprises a bearing section 5c for the first drum disk 4a, so that the drum disk 4a is rotatably mounted on this bearing section 5c. The auxiliary bearing 7 extends through a bore in the main bearing 5, wherein the auxiliary bearing 7 is rotatably mounted in the main bearing 5. The distributor 6 is rotatably mounted on the sub-camp 7. The distributor 6 shown in this embodiment has left and right on a first and second side wall 6c, 6d, between which a radial bore 6e is arranged, which opens at the surface in an outer opening 6f.

The cylinder 9, whose front side is shown, is rotatably connected to the distributor 6 between the side walls 6c, 6d via a fastening axis 6a which is not visible from the illustrated viewing direction, wherein the cylinder 9 in the illustrated arrangement is connected to the distributor 6 so as to be rotatable in the vertical direction is. The cylinder 9 may be connected to the manifold 6 in a variety of ways, so that the illustrated embodiment is only one example of a variety of possibilities.

FIG. 7 shows the sub-camp 7 and the distributor 6 in detail. FIG. 8 shows a plan view of the distributor 6 from the in FIG. 7 direction C. In FIG. 7 a fastening axis 6a is shown. The distributor 6 has a plurality of radially extending to the center of rotation 7a radial bores 6e, which have an inner opening 6g and an outer opening 6f. The distributor 6 also has a plurality of fastening bores 6h. This in FIG. 7 shown auxiliary bearing 7 is configured in an advantageous embodiment such that it forms a rotary valve or a rotary valve together with the distributor 6. and the auxiliary bearing 7 has two longitudinally extending within the sub-bearing 7 fluid lines, which have a fluid inlet 7b and a fluid outlet 7c, and which open into a fluid feed 7g. The manifold 6 is arranged on the bearing portion 7i so as to provide a fluid-conducting connection between the fluid feed 7g and the inner opening 6g, resulting in a fluid-conducting connection between the fluid inlet 7b and the fluid outlet 7c and the outer opening 6f of the distributor 6 are ensured. The sub-camp 7 is in FIG. 9 again shown in a perspective view, wherein in particular the fluid inlet 7b and the fluid supply 7g are visible, the fluid are conductively connected, and wherein the fluid outlet 7k and the fluid outlet 7c are visible, the fluid are conductively connected. The auxiliary bearing 7 is rotatably supported with respect to the main bearing 5 and, in combination with the openings 7g, 7k and the openings 6g of the distributor 6, forms a rotary valve. In the simplest embodiment, the secondary bearing 7 has only the fluid feed 7g and the fluid inlet 7b, so that only the flow of the supplied fluid is determined by the rotary valve. For example, the piston-cylinder assembly could include an exhaust valve such that the fluid supplied to the piston-cylinder assembly is discharged to the environment via the exhaust valve. Will the in FIG. 1 operated rotary engine 1, for example, the sub-bearing 7 is preferably rotated in such a position that preferably the piston-cylinder assemblies 10f, 10g and 10h, a fluid is supplied, whereas preferably from the piston-cylinder assemblies 10i, 10d, 10e a fluid is discharged. By rotating the sub-camp 7 about its longitudinal axis, the time or the angle of rotation can be adjusted, in which the fluid is the respective piston-cylinder assemblies 10 zubeziehungsweise removed.

An embodiment of an embodiment of the fluid conductive connection between the manifold 6 and the piston-cylinder assembly 10 is in the FIGS. 16 to 18 shown. FIG. 16 shows a section through a hinge part 13, which has a bore 13a for a Having pivot bearing through which the mounting axis 6a extends in the assembled state. The joint part 13 has two meeting, fluid-conducting bores 13b, 13c. The joint part also has a blind hole 13d and a circular surface 13e. FIG. 17 shows a longitudinal section through a cylinder 9 with cylinder wall 9b, end face 9a, fixing pin 9c and connection opening 9d. The interior of the cylinder 9 is bounded by a self-sealing piston, not shown, which is mounted displaceably in the cylinder 9 in the longitudinal direction. FIG. 18 shows a manifold 6 to which by means of the attachment axis 6a, a hinge part 13 is rotatably connected. The cylinder 9 is fixedly connected to the joint part 13, so that via the inner opening 6 g, the radial bore 6 e, and the bores 13 b, 13 c, a fluid-conducting connection in the interior of the cylinder 9 is formed. From the FIG. 18 In addition, the effect of the rotary valve is recognizable again. As long as the fluid feed 7g, 7k is arranged below the inner opening 6g, there is a fluid-conducting connection between the fluid inlet 7b and the fluid outlet 7c and the interior of the respective cylinder 9. Constructively, there are a variety of possibilities for a fluid from the distributor 6 into the cylinder 9 to lead. Thus, for example, a flexible hose could be provided, which fluidly connects the radial bore 6e of the distributor 6 with the connection opening 9d of the cylinder 9.

FIG. 15 shows a perspective view of a first drum disk 4a with a plurality of circumferentially spaced holes 4f for connecting means 4c. The drum disk 4a has a bearing surface 4e, which in the assembled state on the bearing surface 5c of the main bearing 5 is rotatably mounted. For example, an at least partially encircling belt, via which the rotating drum 4 could be deprived of energy, could abut against the outer surface of the drum disk 4a denoted by 4a.

The FIGS. 10 to 14 show the claimed synchronization device 16, which serves to drive the distributor 6 via the drum 4, such that the drum 4 and the distributor 6 rotate mutually synchronously. The synchronization device 16 also serves, in particular, to ensure synchronization between the drum 4 and the distributor 6, that is to say that the drum 4 and the distributor 6 rotate synchronously with one another. In this case, a torque is transmitted to the distributor 6 during rotation of the drum 4. FIG. 10a shows a second drum disc 4b in a plan view and FIG. 11 in a perspective view. The second drum pulley 4b has circumferentially distributed bearing journals 4d and connecting means 4c. FIG. 10c shows a distributor driver 11 in a plan view and FIG. 12 in a perspective view. The distributor driver 11 has circumferentially distributed bearing pins 11b. The bearing pins 4d and 11b are each arranged along a circular path with an identical radius. Each trunnion 4d is connected via a rolling connection 12 to a respective trunnion 11b in that the rolling connection 12 has two openings 12a, 12b for receiving the corresponding trunnion 4d, 11b. The FIG. 10b shows a second drum pulley 4b and a distributor driver 11, which are connected to each other via five circumferentially spaced roller joints 12 to transmit power. FIG. 14 shows this force-transmitting connection schematically in a plan view, the bearing journals 4d of the second drum disk 4b and the bearing journals 11b of the distributor drivers 11, as shown in FIG FIG. 14 are arranged along a circle with the same diameter, so that the bearing pins 4d and 11b run during rotation along a well-defined path, so that the rigid, pivotally mounted on the bearing pins 4d, 11b rolling connection 12 a torque between the second drum disc 4b and the Distribution Driver 11 can transmit. In the FIG. 14 The arrangement shown thus makes it possible to transmit a torque between the two mutually eccentrically arranged elements, namely the second drum pulley 4b and the distributor driver 11. In the FIG. 11 shown second drum pulley 4b has four holes 4g in the center. At these four holes 4 g, a central shaft, not shown, could be fastened, via which the drum 4 is driven, or through which the drum 4 energy is removed.

The synchronization device 16 can be further configured to synchronize the mutual movement of the drum 4 and distributor 6. The synchronization device 16 could, for example, additionally comprise a sensor for measuring the angle of rotation of the drum 4, and the synchronization device 16 could additionally comprise a drive device, for example an electric motor, which drives the distributor 6 in such a way that it rotates synchronously with the drum 4.

The in FIG. 12 illustrated distributor driver 11 has a plurality of pins 11c, of which only one is shown visible. These pins 11c are insertable into the mounting holes 6h of the distributor 6 to firmly connect the distributor driver 11 to the distributor 6.

The fluid supply lines 7g can also be arranged such that at least two piston-cylinder assemblies 10, 10a-10h are fed by a separate fluid supply line 7g. In an advantageous embodiment, each piston-cylinder arrangement 10, 10a-10h could be fed with its own fluid supply line 7g. For this purpose, for example, the sub-camp 7 can be configured with the required number of separate fluid supply lines 7g, which is easily possible, especially in a rotary piston engine 1 with a large diameter. Thus, the auxiliary bearing 7 could for example have a diameter of 20 cm, so that within the secondary bearing 7, a plurality in the longitudinal direction of the sub-camp 7 side by side extending fluid supply lines 7g can be introduced.

The piston-cylinder arrangement could also be designed as an internal combustion engine by being supplied to a gas mixture which is ignited within the piston-cylinder arrangement.

In the FIG. 4 illustrated drum 4 comprising the piston-cylinder assemblies 10, 10a - 10h may also be referred to as a multi-piston-cylinder unit 14. In an advantageous Embodiment, the rotary piston machine 1 and the drum 4, two or more multiple piston-cylinder units 14 have. For example, at the in FIG. 4 arrangement shown also on the right side of the holder 3, a main bearing 5 to be arranged above, on which a second multi-piston-cylinder unit 14 is rotatably mounted. In an advantageous embodiment, the multiple-piston-cylinder units 14 identical piston-cylinder assemblies 10, 10a-10h. In a further advantageous arrangement, at least two multi-piston-cylinder units 14 have different piston-cylinder assemblies 10, 10a-10h, wherein the piston-cylinder assemblies 10, 10a-10h differ in particular with respect to cross-section and / or stroke , In a further advantageous embodiment, the fluid supply lines 7g are arranged and configured such that the piston-cylinder assemblies 10, 10a-10h are connected in series by at least two multi-piston-cylinder units 14. This is particularly advantageous when the rotary piston engine 1 is designed as a compressor, so that thereby a two-stage or multi-stage compressor can be formed with compressor stages connected in series. Thus, in the drum 4 twice eight piston-cylinder assemblies 10, 10a-10h in the running direction of the main bearing 5 and the secondary bearing 7 can be arranged side by side, with all the pistons 8 outside the connecting means 4c are fixed, and wherein all cylinders 9 on the manifold 6 are attached. This arrangement would advantageously have two distributors 6, one distributor 6 each for the eight piston-cylinder assemblies 10, 10a-10h. The distributor 6 and the auxiliary bearing 7 could be designed such that two piston-cylinder units are connected in series by the output of the one Piston-cylinder assembly 10 of the adjacent in the direction of the main bearing piston-cylinder assembly 10 is supplied.

In an advantageous embodiment, an engine comprising a rotary piston engine further comprises a speed control device which supplies the fluid with respect to quantity and / or pressure of the rotary piston engine such that the rotary piston engine has a predetermined speed.

Claims (14)

1. A rotary piston machine (1) which is suitable for use as a pump, a compressor or a motor, comprising a main bearing (5) forming a first centre of rotation (5a), comprising a drum (4) which is rotatably supported about the first centre of rotation (5a) by the main bearing (5), comprising a secondary bearing (7) forming a second centre of rotation (7a), wherein the main bearing (5) and the secondary bearing (7) are arranged such that the first and second centres of rotation (5a, 7a) extend mutually in parallel and are arranged mutually eccentrically, comprising a distributor (6) which is rotatably supported about the second centre of rotation (7a) by the second bearing (7), as well as comprising a plurality of piston-in-cylinder arrangements (10, 10a-10h), wherein every piston-in-cylinder arrangement (10, 10a-10h) is pivotably connected to the drum (4) at its one end (10i) and to the distributor (6) at its other end (10k), wherein the piston-in-cylinder arrangements (10, 10a-h) are arranged mutually spaced apart in the peripheral direction of the drum (4) or in the peripheral direction of the distributor (6) respectively, and wherein the piston-in-cylinder arrangements (10, 10a-10h) extend transversely to a radial direction defined by the first or second centre of rotation (5a, 7a), and furthermore comprising a synchronisation apparatus (16), characterised in that the synchronisation apparatus (16) is designed such that the drum (4) and the distributor (6) rotate mutually synchronously, with the synchronisation apparatus (16) being designed as a mechanical coupling comprising a distributor driver (11) which is concentrically connected to the distributor (6), with the distributor driver (11) having a plurality of support spigots (11b) arranged spaced apart in the peripheral direction and extending in parallel to the second centre of rotation (7a), with the drum (4) having a plurality of support spigots (4d) arranged spaced apart in the peripheral direction and extending in parallel to the first centre of rotation (5a), with the support spigots (4d) of the drum and the support spigots (11b) of the distributor driver each being arranged along a circle line having the same diameter, and with the support spigots (1 1b, 4d) being arranged mutually extending such that two respective support spigots (11 b, 4d) are connected via a roller connection (12), with the roller connection (12) being supported rotatably with respect to the support spigots (11b, 4d).
2. A rotary piston machine in accordance with claim 1, characterised in that the synchronisation apparatus (16) includes a sensor for detecting the angle of rotation of the drum (4); and in that the synchronisation apparatus (16) includes a drive apparatus which drives the distributor (6).
3. A rotary piston machine in accordance with one of the preceding claims, characterised in that the secondary bearing (7) as well as the distributor (6) are designed mutually matched such that they form a rotary slider together by the secondary bearing (7) having a support section (7i) for the distributor (6) and at least one first fluid feed (7g) being arranged in the support section (7i), with the first fluid feed (7g) being conductively connected to a fluid inlet (7b), and with the distributor (6) having fluid-conducting passages (6e) which are arranged and designed such that a fluid can be supplied from the first fluid feed (7g) to the piston-in-cylinder arrangement (10, 10a-10h).
4. A rotary piston machine in accordance with claim 3, characterised in that the secondary bearing (7) has a second fluid feed (71) spaced apart in the peripheral direction with respect to the first fluid feed (7g); in that the second fluid feed (71) is conductively connected to a fluid outlet (7c); and in that the distributor (6) has fluid-conducting passages (6e) which are arranged and designed such that a fluid can be led off from the piston-in-cylinder arrangements (10, 10a-10h) via the second fluid feed (71).
5. A rotary piston machine in accordance with claim 3 or claim 4, characterised in that the secondary bearing (7) is rotatably supported and is in particular connected to a fixing apparatus (7d) to fix the secondary bearing (7) at a specific angle of rotation or is in particular connected to a control apparatus to change the angle of rotation in a controllable manner.
6. A rotary piston machine in accordance with any one of the preceding claims, characterised in that the distributor (6) has fluid-conducting passages (6e) which open into an outer opening (6f) and in that the piston-in-cylinder arrangement (10, 10a-10h) has a joint part (13) which is pivotably connectable to the distributor (6), with the joint part (13) having a fluid-conducting passage (13b, 13c) which is arranged such that a fluid-conducting connection is formed between the outer opening (6f) and the inner space of the piston-in-cylinder arrangement (10, 10a-10h).
7. A rotary piston machine in accordance with any one of the claims 1 to 4, characterised in that a plurality of fluid supply lines (7g) are arranged such that at least two piston-in-cylinder arrangements (10, 10a-10h) are fed from a separate fluid supply line (7g).
8. A rotary piston machine in accordance with any one of the preceding claims, characterised in that the piston-in-cylinder arrangement is designed such that a combustion can take place therein.
9. A rotary piston machine in accordance with any one of the preceding claims, characterised in that all the piston-in-cylinder arrangements (10, 10a-10h) arranged mutually spaced apart in the peripheral direction of the drum (4) or in the peripheral direction of the distributor (6) respectively form a multiple piston-in-cylinder arrangement unit (14); and in that at least two multiple piston-in-cylinder units (14) are arranged next to one another in the direction of extent of the first and second centres of rotation (5a, 7a).
10. A rotary piston machine in accordance with claim 9, characterised in that each multiple piston-in-cylinder unit (14) has identical piston-in-cylinder arrangements (10, 10a-10h).
11. A rotary piston machine in accordance with claim 9, characterised in that at least two multiple piston-in-cylinder units (14) have different piston-in-cylinder arrangements (10, 10a-10h, with the piston-in-cylinder arrangements (10, 10a-10h) in particular differing with respect to inner cross-section and/or stroke.
12. A compressor, pump or motor comprising a rotary piston machine in accordance with any one of the preceding claims.
13. A compressor in accordance with claim 12, comprising at least one first and one second multiple piston-in-cylinder unit (14), with at least one piston-in-cylinder arrangement (10a) of the first multiple piston-in-cylinder unit (14) as well as a piston-in-cylinder arrangement (10a) of the second multiple piston-in-cylinder unit (14) being connected in series.
14. A motor in accordance with claim 12, comprising a speed control apparatus which supplies the fluid to the rotary piston machine (1) with respect to amount and/or pressure such that the rotary piston machine (1) has a predefined speed.

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