WO1982001032A1

WO1982001032A1 - Rotary piston machine

Info

Publication number: WO1982001032A1
Application number: PCT/EP1981/000146
Authority: WO
Inventors: Rmc Kg Rotationsmasch
Original assignee: Kathmann P
Priority date: 1980-09-11
Filing date: 1981-09-11
Publication date: 1982-04-01
Also published as: EP0048415A1

Abstract

In a rotary piston machine with a casing (22) wherein there is mounted a substantially circular rotor (12) containing a plurality of sealed pistons or sliding parts (14) guided between the rotor and the casing, the guiding of the sliding parts is effected by a guiding device arranged inside the rotor with a guiding element (16) of a polygonal shape or with rods, or by a guiding device located substantially outside the rotor, with guiding cams on the cover and the bottom of the casing, which are coupled with the sliding parts in the rotor. The rotor may have in its cylindrical wall a combustion chamber between at least one pair of neighbouring sliding parts. The casing may have one or a plurality of crescent-shaped curvatures which are used as suction or explosion chamber. The device driving - or driven by - the machine may operate in an electromagnetic mode, the rotor forming the armature and the casing forming the stator of a rotating electric machine. This is particularly the case when using the present machine as a pump for toxic or dangerous liquids. The winding of the stator may also be arranged in the cover and the bottom of the center and the rotor is then formed in this embodiment with a flat air-gap.

Description

Rotary piston machine

The present invention relates to a rotary piston machine with a) a housing which forms a rotor chamber which is delimited by an inner wall of the housing, b) a rotor which is rotatably mounted about an axis in the rotor chamber, c) piston-like or slide-like power parts which are mounted radially displaceably in the rotor, d) a sealing arrangement for the sliding sealing of the power parts, the rotor and the rotor chamber with respect to one another and e) a power part control device which, when the rotor in the rotor chamber rotates, results in a forced displacement of the power parts of the rotor.

Such a rotary piston machine is known from DE 27 28 165C3 and EP 0007535A1. In these known rotary piston machines, the rotor contains a single one, the rotor diametrically penetrating power section, the opposite ends of which are opposite a cylindrical outer surface of the housing inner wall and are sealed with respect to this by the sealing arrangement. The rotor is mounted eccentrically in the rotor chamber and the power part control device contains a guide pin which is essentially concentric with respect to the rotor chamber and which engages in a guide groove of the power part.

DE 28 53 423A1 discloses a seal between three bodies which are movable relative to one another and which, in the described or in a modified form, can advantageously be used in the present rotary piston machines.

A disadvantage of the known rotary piston machines is that they are only able to carry out a single compression and expansion process per revolution of the rotor. This not only results in relatively high power to weight ratios, but also does not result in the machine running excessively smoothly. This lack can. can be countered by increasing the number of power parts per rotor, no longer use the known device for positive or positive control of the power parts. The known rotary piston machines can also be improved in other respects, as will be explained in the following.

The present invention is therefore based on the object of advantageously developing rotary piston machines of the type mentioned at the outset. In particular, rotation to piston engines with three or more, more preferably five power units are given, the radial Hubbewe- ^' gations with respect to the rotor by a new type of control device (that is, not by springs that push the power parts outwards) are controlled in such a way that a perfect seal is guaranteed and that special types of working cycles can be carried out.

In the case of the present rotary piston machines, the rotor contains a predetermined, preferably odd number of radially displaceable power parts. The specified number is greater than 2, a preferred value is five.

When the rotor rotates in the rotor chamber, each power part is forcibly and positively shifted with respect to the rotor by the control device.

In a first type of the present rotary piston machine, the control device is located inside the rotor, similar to the known case. In this case it can contain a polygonal control body, the number of pages of which is equal to the number of power parts. With their end facing away from the inner wall of the housing, the power units are each coupled to one side of the polygonal control body, which is rotatably mounted in the center of the rotor chamber.

In another embodiment of the invention, the power units are coupled via a connecting rod assembly having a rotatably mounted in the center of the disk rotor chamber ge ^¬.

In a preferred, different type of the present rotary piston machine, the control device is located outside the rotor. The control device works

OMPI based on the principle of a control cam and can then each contain a groove-like control cam in a cover and in a bottom of the housing, into which axially parallel bearing bolts engage, which penetrate the power units transversely. However, the control function can also be implemented in a corresponding manner by a magnetic system.

Rotary piston machines of the present type can be used both as a fluid pump and as a fluid-operated motor. In the latter case, particular advantages are achieved in that a combustion chamber is provided in the rotor between two adjacent power units.

Special configurations of the rotary piston machines of the present type working with "external control" are distinguished by particularly low wear.

Embodiments of the present rotary piston machine, in which the rotor chamber has a non-circular cross section, result in particularly high efficiencies when used as an internal combustion engine. The non-circular design of the rotor chamber enables the expansion space to be chosen larger than the compression space in a rotary machine operating as a four-stroke internal combustion engine, so that very high fuel utilization can be achieved.

Exemplary embodiments of the invention are explained in more detail below with reference to the drawings, and further features and advantages of the invention will also be discussed.

Show it: 1 shows a longitudinal section of a rotary piston machine according to a first embodiment of the invention;

Fig. 2 shows a cross section in a plane II-II of Fig. 1;

5

3 shows a plan view of a clutch or control part of the rotary piston machine according to FIGS. 1 and 2;

'Fig. 4 shows a side view of the control part according to FIG. 3;

10th

5 shows a side view of a power unit of the rotary piston machine according to FIGS. 1 and 2;

6 shows a view of the power section according to FIG. 5 seen in the direction of arrows VI-VI ^' ; ^•

7 shows a diagrammatic representation of a rotary piston machine according to a second embodiment of the invention; 20th

8 shows an axial section of a preferred, third embodiment of a rotary piston machine according to the invention;

2 ^* 5 FIG. 9 shows a simplified cross section in a plane IX-IX of FIG. 8, the rotor in the right half of the drawing being shown in a top view (not _' cut);

10 shows a plan view of a housing cover of the rotary piston machine according to FIG. 8 seen in the direction of arrows X-X;

11 is a plan view of the rotor of the rotary piston

35 machine according to Fiσ. 8th; 12, 13 and 14 show a longitudinal section, a side view and a top view of a power unit for the rotary piston machine according to FIGS. 8 and 9;

FIG. 15 shows a sectional view corresponding to FIG. 9 of an embodiment of the present rotary piston machine with power parts designed as a flat slide valve;

FIG. 16 is a cross section through a Rotationskolbenma- ^• _jQ the invention machine in accordance with a modified Gehäu¬ sekonstruktion that includes a magnet assembly;

Fig. 17 is a schematic cross-sectional view of a rotary piston machine according to the invention; in which 15 the power units are controlled magnetically;

FIG. 18 is a plan view of a rotary piston machine with a device which enables the use of the machine as a pump ode ^'r compressor to control the flow rate is 20 hei constant drive speed;

19a shows an axial section of a control disk for a rotary piston machine of the type shown in FIG. 8;

25th

FIG. 19b shows a top view of a housing cover of a rotary piston machine with a control disk mounted therein in accordance with FIG. 19a;

30 is a schematic cross-sectional view of a

Housing of a rotary piston machine, the rotor chamber of which has a non-circular cross section;

35 21 shows a perspective illustration of a rotor for the rotary piston machine according to FIG. 20, only the region of a single working chamber being shown in more detail;

22 is a simplified cross-sectional view of a modified rotor for the rotary piston machine according to FIG. 20, the upper and lower halves corresponding to two different variants.

The same or corresponding parts of the different embodiments are denoted by reference numerals which correspond in the one and tens positions. It is therefore generally not necessary to mention or describe such parts again once they have been explained.

The rotary piston machine shown in Figures 1 and 2 as the first embodiment of the invention. consists essentially of a housing 10, a rotor 12, in which power parts 14 are mounted so as to be radially displaceable, and a clutch or control part 16.

The housing 10 consists of a bottom 18, a cover 20 and an annular housing part 22, which will be referred to as "housing ring" in the following. These three parts are held together by schematically indicated screw bolts 24.

The inner wall of the housing forms a rotor chamber 23, which has the shape of a straight circular cylinder in the machine according to FIGS. 1 and 2.

The rotor 12, which has essentially the shape of a circular disk, has a shaft end 26 on one end face and a bearing collar 28 on the other end face, with which it is rotatably mounted about a rotor axis 30, which a central axis 32 of the rotor chamber 23 is eccentric. For example, two roller bearings 34, 36 are used for storage, of which the roller bearing 34 is located in an opening in the base 18, through which the stub shaft 26 is guided to the outside, while the other is seated on a journal 38 which passes through an annular groove 40 is formed in the housing cover 20.

As shown in FIG. 2, five power units 14 are arranged in rotor 12 at equal angular intervals of 72 ° each. The power units have an essentially circular cross-section and are radially displaceably mounted in corresponding radial bores of the rotor and, with respect to these bores, are provided by conventional means (not shown). tional piston rings sealed, which are inserted in piston ring grooves 33 (FIGS. 5 and 6). At their outwardly directed ends, the power parts each have a cylindrical rounding 42 and a slot 44 (FIG. 6) for receiving sealing elements, as seen in the axial direction of the rotor (FIG. 6). At the other, inner end 46, the power parts taper in a wedge shape as seen in the axial direction (FIG. 6), where they form a hook-shaped extension 48, which is somewhat shortened in the axial direction, and a coupling slot 50.

The control part 16 shown in more detail in FIGS. 3 and 4 has a bearing bush 52 with which it is rotatably mounted on a bearing journal 54. The bearing pin 54 is attached to the housing cover 20 such that the axis of rotation of the control part 16 coincides with the axis 32 of the rotor chamber. The control part 16 also has an upstanding collar 56 which extends into the interior of the rotor and which has the shape of a polygome with as many sides as there are power units and which engages with its sides in a coupling slot 50 of a power unit, as in FIG Fig. 1 is shown. (In FIG. 1, only one power section is shown because of the five-fold symmetry of the rotor power section arrangement).

The control part 16 and the power parts are dimensioned and arranged in such a way that the outer ends of the power parts during the rotation of the rotor 12 eccentrically mounted in the rotor chamber are forcibly guided along a cylindrical outer surface 58 of the rotor chamber with a substantially constant close distance will. Furthermore, the inside diameter of the bearing collar 28 is dimensioned so large that the control part 16 can be inserted into the rotor 12 and the coupling slots of the power parts.

-t OMPI In order for the rotary piston machine described to function properly, it is necessary to properly seal the inner wall of the housing delimiting the rotor chamber, the rotor and the power units in relation to one another. For this purpose, a sealing arrangement can be used, as is known from DE 28 53 423A1. This known sealing system can also be simplified in that the sealing body no. 1 is omitted and the sealing parts no. 4 are attached laterally to the angle sealing strips no. 2 (see FIG. 3 of DE 28 53 423A1).

In the rotary piston machine shown in FIGS. 1 and 2, the frontal sealing of the power parts 14 with respect to the inner wall of the housing takes place by means of two sealing elements 60 and 62, which are designed similarly to the sealing elements in FIG. 3 of DE 28 53 423A1. The sealing elements 60, 62 are pressed apart by a first spring arrangement 64 and pressed against flat end faces 66 and 68 of the base 18 and cover 20, respectively. Furthermore, the sealing elements 60, 62 are pressed radially outward against the outer surface 58 by a second spring arrangement 70. The sealing of the flat end faces of the rotor with respect to the housing end faces 66 and 68 takes place by means of sealing strips 72 in the form of an annular sector, which are inserted into a corresponding circular groove in the rotor end faces and each extend between two adjacent sealing elements 60 and 62, respectively .

The sealing elements 60, 62 and the sealing strips 72 can meet in sealing plates 74 which surround the slots 44 in the region of the rotor 12. The sealing plates can be circular. Such a sealing plate is shown schematically in Fig. 2.

The housing 10 further includes a fluid inlet 76 and a fluid outlet 78, di ^* e, as shown in Fig., From ent speaking perforations 2 shows the housing ring 22 may be be¬. However, the inlet and the outlet can also be formed by corresponding openings in the base 80 and / cover 20, as is shown, for example, in FIG. 20.

A work space 79 is formed in each case by two adjacent power parts 14, the outer jacket surface of the rotor and the inner wall of the housing. When using the rotary piston machine according to FIGS. 1 and 2 as a pump or compressor, the rotor 12 is driven in the direction of the arrow 80 via the shaft stub 26. The working space, which is in position 79a, has a relatively small volume because of the eccentricity of the rotor with respect to the rotor chamber. The volume increases with the rotation of the rotor, as a comparison with the working space located in position 79b shows. A fluid to be pumped is thereby sucked through the inlet 76. In position 79c, the working space has reached its greatest volume and the fluid contained therein is expelled through outlet 78 as the rotor continues to rotate, while the working space is reduced again, as positions 79d and 79e show. When the rotor 12 rotates, the working parts 14 perform movements both in a radial and in a tangential plane with respect to the housing.

7 is a simplified cross-sectional view of a rotary piston machine, which differs from that according to FIGS. 1 and 2 primarily in that the power part control device is not as in FIGS. 1 and 2

OMPI contains a polygonal control body but a connecting rod arrangement. The housing, rotor and rotor bearing can be designed as in the case of the rotary piston machine according to FIGS. 1 and 2. Furthermore, like in FIGS. 1 and 2, five piston-like power parts 114'a to 140e are in corresponding radial bores of the rotor 112 slidably mounted. The sealing arrangement can be designed as explained below; for the sake of simplicity, only one sealing element 162 is indicated for the power part 114c.

The power units 114b to 114e are each connected via a connecting rod bearing 182 and a bearing pin 184 to a connecting rod 186 which can be pivoted about the axis of the pin 184, similarly to a conventional reciprocating piston engine. At the end facing away from the connecting rod bearing 182, each connecting rod 186 is coupled via a further rotary bearing 188 to a disk 190 which is rotatably mounted on a central bearing pin 154 which, like the bearing pin 54 (FIG. 1), is coaxial with the axis 132 of the rotor chamber 123 is attached to a housing cover (not shown in FIG. 7). The power part 114a is also connected via a bearing 182 with a bearing pin 184 to a connecting rod 186a, but this connecting rod is attached to the disc 190 by a non-pivotable fastening 192, e.g. screwed in, so that the connecting rod 186a serves as a driver for the disc 190 when the rotor 112 rotates and rotates it around the bearing pin 154 in accordance with the rotation of the rotor.

Through the described central to the rotor chamber 123

Connecting rod arrangement ensures that the end faces of the power parts 114 in close, essentially constant distance along the outer surface 158 of the rotor chamber and the seal arrangement can function properly. Here, too, the rotor has an opening 194 (corresponding to the inner diameter of the bearing collar 28 in FIG. 2) which is dimensioned so large that the connecting rod arrangement with the disk 190 can be mounted inside the rotor.

The connecting rod 186a maintains its fixed radial position when the rotor 112 rotates in the rotor chamber 123, while the other connecting rods carry out oscillating movements due to the eccentricity of the rotor axis on the one hand and the axis of the rotor chamber and the bearing pin 154 on the other hand.

In the rotary machine according to FIG. 7, the end faces of the power parts are not cylindrically rounded, but are chamfered in a wedge shape. Inlet and outlet for a fluid to be pumped or a driving fluid are not shown in FIG. 7. The rotary piston machine according to FIG. 7, like that according to FIGS. 1 and 2, can be operated as a vacuum pump or as a compressor or, when fed with a pressure fluid, can operate as a hydraulic or pneumatic motor.

The described conrod bearing with the disc 190 has in comparison to the known conrod bearings (see for example US 35 37 432 A1 and US 40 61 450 A1) that the conrods do not need to be cranked or forked, so that the machine is flat , is highly resilient and allows large radial power unit strokes. The bearing pin 154 can also be rotatably mounted in an opening of the cover 20 by means of a rotary bearing (not shown), for example a roller bearing, wherein the bearing pin can be fixedly or also rotatably connected to the disk 190. As a result, the bearing wear at high speeds can be reduced and the machine remains functional even when a bearing is blocked. The same applies to the bearing journal 54 of the machine according to FIGS. 1 and 2.

The rotary machines described above contained a power part control device arranged in the interior of the rotor. A significant simplification can now be achieved in that the relative movement taking place between the power parts and the rotor is controlled outside the rotor, ie the power part control device is located outside the rotor, in particular essentially in the lid and bottom of the housing house. Such an "external" power unit control device can be implemented in a structurally simpler manner than the internal control described above, and the rotor can also be supported on both sides by a simple shaft stub. Another major advantage of external control is that more complex control programs can also be implemented. For example, the power units can perform several stroke cycles with one revolution of the rotor, which is particularly advantageous when the present rotary piston machine is used as an internal combustion engine, since the four work cycles of a four-stroke engine can be realized, for example, with one revolution of the rotor. The external control can in particular be brought about by a control cam arranged in the housing and which can be easily produced. The assembly of a rotary piston machine with external control is also easier than that with an internal control and the external control is also less prone to failure. An exemplary embodiment of a rotary piston machine with external control is explained in more detail below with reference to FIGS. 8 to 14.

The rotary piston machine according to FIG. 8 agrees in many respects with that according to FIG. 1, the following explanations will therefore be restricted essentially to the new features.

In the rotary piston machine according to FIG. 8, the rotor 212 is not only supported by a stub shaft in the bottom of the housing, but is rotatably supported by a continuous shaft 226 in the bottom 218 and in the cover 220. The shaft 226 runs in roller bearings 234, 236. The rotor is fastened to the shaft by a wedge 237.

The rotor 212 (FIG. 11) contains five radial bores 213, in each of which a power part 214 with a circular cross section is mounted so as to be radially displaceable. The power parts 214 (FIGS. 12 to 14) have at their inner ends a bore 215 which, when the power part is mounted, runs in the axial direction and is located in the vicinity of the inner end of the power part. The bores 215 each receive a control pin 217, the ends 219 of which extend outward through radial slots 221 of the rotor. In the bottom 218 as well as in the cover 220 there is a circular, _* groove-like control curve

225 provided, in which the ends 219 of the control pins 217 engage directly or via bearing pieces 227 (FIG. 10 or roller bearings).

8 and 9, the radial sealing of the power parts 214, which are circular in cross section, does not take place, as in FIGS. 5 and 6, by means of piston rings, but rather by semi-ring-shaped seals which are inserted in grooves 233 which are located in the rotor in the Near the outer ends of the bores 213 (see Figs. 8 and 11). The ends of these semicircular seals lie in recesses at the ends of the annular sector-shaped sealing strips 272, which in turn are pressed against the end faces of the rotor chamber by springs (not shown) in bores 273 (FIG. 9). The semi-ring-shaped seals are pressed against the power part by flat corrugated springs arranged in the groove base.

The control cams 225 are concentric to the lateral surface 258 of the housing and control the displacement of the power parts while the rotor rotates about its eccentric axis 230. The housing is provided with inlet and outlet openings not shown in FIG. 11, similar to the housing of the rotary piston machines according to FIG. 2 and the machine according to FIG 1 and 2.

FIG. 15 shows a cross-sectional view corresponding to FIG. 2 or FIG. 9 of an embodiment of the present rotary piston machine, in which the rotor 312 mounted eccentrically in the rotor chamber 323 contains five power parts 314, which essentially have the shape of flat slides have rectangular cross-section. The flat slides can be provided with cavities in order to reduce the weight. Flat gate valves have the advantage over cylindrical, piston-like power parts that they require less space. 0 With the same cubic capacity, the machine can therefore be made smaller or more power units can be provided than would be possible using piston-type power units, or the machine's output can be increased. The control of the displacement of the power units with respect to the rotor is carried out by control cams, as has been explained with reference to FIG. 8. The end face of the power parts designed as a flat slide valve is sealed off from the lateral surface 358 by sealing elements corresponding to the sealing elements 60 and 62 in FIGS. 1 and 2. Only the sealing element 360 can be seen in FIG. 18. The end faces of the rotor are again sealed off from the inner wall of the housing by sealing strips 372 in the form of annular sectors. Sealing strips 331, which run axially, serve to seal the flat side surfaces 329 of the slide-shaped power parts 314. The sealing strips 372 can have cutouts at their ends, into which the sealing strips 331 engage in order to achieve the best possible seal.

The sealing strips are pressed against the flat side surfaces of the power units by corrugated springs. The sealing arrangement essentially corresponds to that of the machine according to FIGS. 8 to 14.

The control of the displacement of the power parts with respect to the rotor can be supported or effected by magnetic forces, in particular electromagnetic forces. For example, as indicated schematically in FIG. 16, magnet coil windings 481, which generate a radial magnetic field, can be arranged in the housing ring 422. The power parts 414 are pressed radially outwards against the outer surface 458 by centrifugal forces and / or spring forces and contain permanent magnets which have a pole on the end facing the outer surface 458 with the same sign as the pole generated by the windings 481, so that repulsive forces occur. which guide the end faces of the power units without contact and at a close distance along the outer surface 458. The rotor in this case is made of a non-magnetic material, such as bronze. The magnetic windings in the housing ring 422 can consist of two solenoid coils, the turns of which run in the circumferential direction around the rotor chamber 423 and are connected to one another in such a way that, when excited with a direct current of suitable strength, axially in the middle of the housing ring 422 on the An annular magnetic pole is formed on the inside and outside of the housing ring 422.

To generate a radial magnetic field, however, a series of winding loops with axially extending conductors can also be provided in the housing ring 422, similar to the stator of an electric motor. However, these winding loops are switched such that only north or south poles are formed on the inside of the housing ring 422.

Furthermore, the windings in the housing ring 422 can form stator windings of a three-phase motor and can be fed with a suitable alternating current or multiphase current when the machine is operated as a pump or compressor, so that a rotating field is created in the rotor chamber 423. This rotating field is used to drive the rotor, whereby either the rotor and / or the power units interact magnetically with the rotating field and form the rotor of the three-phase motor. In a rotary piston machine designed in this way, a mechanical drive of the rotor can be dispensed with, so that the housing can be made completely closed except for the inlet and outlet. ^"

The electromagnetic forces generated in the housing ring 422 can also be used to keep the sealing elements 460 of the power units in contact with the outer surface 458. In this case, the power units are controlled by an internal or external control of the type described above with respect to the rotor and are made of non-magnetic material. The springs for pressing the sealing elements against the inner wall of the housing can then be omitted. The sealing elements consist of magnetic material, such as ferrite, or contain one.

It is also or additionally possible to effect the external control described with reference to FIG. 8 not by control curves, but by magnetic forces. For this purpose, magnetic windings are then provided in the cover or bottom of the housing, preferably in both, which generate magnetic poles which act like control cams and have a corresponding course. The power units can then consist of non-magnetic material and inserts, for example similar to the control pin 217 in Fig. 8 from magnetic material, which cooperate with the cam magnet poles. On the other hand, the power parts can also consist of magnetic material and have such a shape, in particular have projections which serve as follower elements for the "magnetic control curve". The rotor of such a machine is made of non-magnetic material. A cross section of a rotary piston machine with magnetic control cams is shown schematically in FIG. 21. The lid and base contain two coaxial solenoid windings 583 and 585, which are concentric with the rotor chamber 523, between which, with the same polarity, a ring-shaped magnetic pole is created, which acts as a magnetic control curve 525 for magnetic insert bolts 517 of the power parts 514. The insert bolts 517 can be made of soft magnetic material. An advantageous alternative consists in making the insert bolts 517 from permanent magnet material and poling them so that they are held radially between the windings 583, 585 without contact by magnetic repulsive forces.

In Fig. 17 also two windings of five Stator¬ are indicated 587, which are arranged in the housing ring 522 and ange¬ existing with the good conductive material such as aluminum or copper rotor 512 form a ^'induction motor. The rotor can also contain short-circuit windings or a permanent magnet system in a known manner.

In the case of the present rotary piston machines, the working space stroke, ie the change in volume of a working space with one revolution of the rotor, can be made variable by making the eccentricity of the rotor axis in the rotor chamber variable. When the present rotary piston machine is used as a pump or compressor, the delivery rate can thereby be made variable even at a constant drive speed. The eccentricity of the rotor axis can be changed, for example, as shown in FIG. 18. In this • rotary piston machine, the shaft end 26 of the rotor is not mounted in a fixed pivot bearing in the housing cover or bottom, but rather is displaceable. For this purpose, in the rotary piston machine shown in FIG. 18, a diametrically extending elongated hole 41 is provided in the housing base 18, in which a bearing piece 43 is slidably mounted. The stub shaft 26 of the rotor is rotatably mounted in the bearing piece 43. On one side of the bearing piece 43, a threaded block 45 with an internal thread is fastened, into which a threaded spindle 47 engages, which is connected to a drive device 49, e.g. a small electric motor. If the rotor is also supported on the other side, a similar displacement device is provided there, with Serge being carried on both sides by a mechanical or electrical coupling for synchronous movement of the bearing pieces 43. The rotary piston machine can otherwise be designed as one of the embodiments described above.

»

In the position shown in FIG. 18, the rotor axis 30 is concentric with the rotor chamber 23, so that there is no change in volume when the rotor rotates there is a work space between each of two power units. When the rotor is driven, the delivery rate of the rotary piston machine is therefore zero. If the bearing piece 43 is moved in one direction by actuating the drive device 49, the delivery rate per revolution increases Zero from up to a maximum value which corresponds to the maximum possible eccentricity of the rotor in the rotor chamber 23. The same, but with the opposite direction of conveyance, occurs when the bearing piece is displaced radially from the central position in the other direction How to continuously change the delivery rate and delivery direction of a rotary piston machine of the type described, which works as a pump or compressor, even with a constant drive speed of the rotor between zero and a positive and negative maximum value.

The further developments described below with reference to FIGS. 19 to 22 open up further fields of application for the present rotary piston machine and contribute to a further improvement in the functionality of the rotary piston machines described. By using a control disk, as will be explained with reference to FIG. 19, the wear of a rotary piston machine operating with external control of the type described with reference to FIG. 8 can be considerably reduced. The use of at least one revolving combustion chamber, as is explained with reference to FIGS. 20 to 22, ensures high efficiencies when the present machine is used as an internal combustion engine. The non-circular design of the housing cross section explained with the aid of the same figures enables a rotary piston working as a four-stroke combustion engine. machine to choose the expansion space larger than the compression space, so that very good fuel utilization c

^ can be achieved.

Instead of the circular control curves 225 described in FIG. 8, which serve to control the displacement of the power parts, an annular control disk 700 can be used, as shown in axial section in FIG. 19a and in a top view in FIG. 19b is. Each control disk 700 is rotatably supported in an annular groove corresponding to the control cams and has circular-arc-shaped recesses 702 for the storage of the ends 719 of the bearing or control pins 715 of the power units. In Fig. 19b only two such recesses are shown to simplify the drawing. The ends 719 of the bearing bolts are supported in the recesses 702 via ball bearings 704 or correspondingly curved sliding pieces 706 in such a way that they have a certain amount of play in the circumferential direction with respect to the control disk 700. The control disk can furthermore have a radial slot 708 into which a driver pin 701 attached to the relevant end face of the rotor 712 of the machine engages. The function of the driver pin can also be taken over by one of the control bolts, which is then mounted immovably in the guide disk in an azimuthal manner. In operation, the control disk 700 rotates with the rotor 712, but eccentrically to the latter, the radial movement of the power units being controlled by the control bolts mounted in the recesses 702. The control bolts (possibly with the exception of the control bolt serving as a driver) perform a certain pendulum movement about their azium-central (seen in the circumferential direction) central position when the control disc 700 rotates due to the eccentricity between the rotor 712 and the control disc 700, which is made possible by the correspondingly shaped recesses 702. / "STTRI ^"

O PI A modification of the control disk described is shown on the right in FIG. 19b. Here the control disk has a continuous annular groove 702 '(the cross section of the control disk is then approximately U-shaped). The control bolts 719 are mounted in the annular groove 702 * via sliding pieces 702 (or ball bearings 704). A control pin is extended and engages in a corresponding hole in the bottom of the ring groove 702 * so that it acts as a driver.

By using control disks 700, the stress and thus the wear on the power unit control are considerably reduced.

The suitability of rotary machines of the type described above can be considerably improved by further measures. First, a machine with more than one compression and / or expansion space can be realized by a non-circular design of the control curve and by a corresponding design of the rotor chamber cross-section, and when the machine is used as an internal combustion engine, the ratio of intake space to work or expansion space enlarge so that the hot combustion gases can relax further than was previously possible, possibly up to almost 1 bar, which improves the efficiency accordingly. A machine of this type is shown in Figure 20, which shows a substantially simplified cross-sectional view of the housing. The rotary machine also contains a rotor 712, which is only shown schematically in FIG. 21 and which, for example, as can be seen from FIG.

In the rotary machine shown in FIGS. 20 to 22, the cross section of the lateral surface 758 of the annular housing part 722 no longer has the shape of a circle like the circumference of the rotor 712, but is approximately egg-shaped.

The rotation chamber has approximately the shape of a straight elliptical cylinder. This shape is produced by two diametrically opposite bulges 751, 753 which are approximately crescent in cross section and which are preferably of different sizes. Correspondingly shaped control curves are located in the bottom and cover of the housing, of which a control curve 725 is shown in FIG. The lid and / or the bottom of the device

OMFI In the embodiment of the present rotary machine shown in FIG. 20, 1 housing are also provided with a twist-shaped inlet slot 776 and a twist-shaped outlet slot 778, which are located on the

5 are a pair of the mutually facing ends of the crescent-shaped bulges 751 and 753.

The circular disk-shaped rotor 712 shown in perspective or in cross section in FIGS. 21 and 22 contains

10 of this embodiment of the present rotary machine, five piston-like or slide-like power units 714, which are spaced apart from one another by 72 °, and only one of which is shown in FIG. If you ignore the different sizes of the bulges,

15 the axis 130 of the rotor is located in the middle of the rotor chamber. The power units are slidably mounted in corresponding bores 727 of the rotor. The sealing arrangement for the power units and the rotor is. not shown in detail, it can be in a known per se

20 manner or as explained above.

The power units 714 are pushed through by control bolts 717, the ends of which are guided in the control cams 725, as has been explained with reference to FIG. 8. 25th

In the present embodiment of the rotary machine, the rotor 712 is provided with a combustion chamber 755 in its cylindrical side surface 712a between two power units in each case. Of each combustion chamber two axially offset grooves 761 extend ^'■ ^"•' to the

Form flow channels to the adjacent bores 727 and can have a relatively small depth. The combustion chambers 755 are preferably approximately hemispherical, as can be seen from the cross section in FIG. 22. Each combustion chamber oc ^J 755 can be provided with a spark plug 757, which sits in an oblique bore and is connected to an associated distributor contact. The distributor contacts are located on one flat end face of the rotor 712 and cooperate in a manner known per se with a counter-contact, not shown, which is located on the inside of the housing cover and is connected to an ignition coil.

20 to 22 works similar to a ten-cylinder four-stroke engine, as will be explained in the following.

The five power units 714 are only symbolized in FIG. 20 by their dash-dotted center planes intersecting the rotor axis 730. The rotor should turn clockwise. A work space 779, to which a combustion chamber 755 belongs, is formed between two power parts. A work space also includes the azimuthal (in the circumferential direction) depressions 761, which extend from the combustion chamber to the bores 727 containing the power parts. If two power units are in positions I and II, the working space enclosed between them has a minimum volume corresponding to the top dead center in a piston engine. If the rotor continues to rotate clockwise, the front power section in the direction of rotation begins to enter the gusset-shaped bulge 752 and runs through the inlet slot 776; the intake stroke begins. When the power units have reached positions III and IV, the volume of the workspace under consideration has a first maximum corresponding to bottom dead center, the intake stroke has ended and the compression stroke now begins, during which the power units under consideration move in positions V and VI . In the last mentioned positions, which are again the upper one Correspond to the dead center in a piston engine, the volume of the work space in question again has a minimum, the compression cycle has ended and the ignition takes place (with regard to early or late ignition, the conditions are similar to those for a piston engine).

As the rotor continues to rotate, the volume of the work space under consideration increases, which corresponds to the expansion or work cycle. In positions VII and VIII of the power parts under consideration, the work area has its largest volume and when turning further, the outlet slot 778 is released. There now follows the exhaust stroke, in which the combustion products are conveyed through the outlet slot 778 into the exhaust. The exhaust cycle ends when the power sections under consideration return to their starting position in positions I and II.

The cycle described is followed by all five working chambers in succession. With one revolution of the rotor, five complete four-stroke cycles take place. This results in a high performance weight and ^" a quiet

Run.

Because the bulge 752, which goes into the volume of the suction space, is selected to be smaller than the volume of the bulge 751, which goes into the volume of the expansion or working space, a very extensive expansion, for example up to about atmospheric pressure, can be achieved, which one has a high degree of efficiency, since the combustion gases can be expanded to a very large extent. -29-

20 to 22 can be modified in various ways. For example, the spark plugs 757 provided in each combustion chamber 755 of the rotor can be replaced by a single spark plug 757 *, which is located in the conversion of the housing and is arranged such that it communicates with the working space containing the compressed gas.

The rotary machine according to FIGS. 20 to 22 can of course also be operated as a diesel engine, with the spark plugs 757 or 757 'then being replaced by glow plugs. It is also possible to work with direct injection of the fuel, which is particularly advantageous in the case of an engine operating on the diesel principle. In this case, an injection nozzle 789 can open into each combustion chamber, in particular into each combustion chamber 755, which is supplied with fuel by an injection pump via a suitable line and distributor system _* for example via a hollow shaft 726, which has a radial bore 791, which performs the distributor function for the fuel when the rotor rotates about the substantially fixed hollow shaft.

A single injector 789 'disposed in the housing ring 722 can also be used.

The combustion chambers 755 can also be provided both with a spark plug 757 and with an injection nozzle 789, as is shown schematically in the lower left in FIG. 22.

If the rotary machine described is operated as an internal combustion engine without direct fuel injection into the working chambers, the inlet slot 776 is of course equipped with a carburetor or a Intake manifold injector connected.

The fuel can also be burned in an external combustion chamber 771, which supplies compressed gas independently of the engine. In the case of an engine of the type described with reference to FIGS. 20 and 22, the combustion chambers 755 are then omitted and two further slots 767, 769 are provided which are connected to the inlet and outlet of the outer combustion chamber 771. The rotary machine then sucks in air through the inlet slot 776, which air is conveyed through the slot 767 into the external combustion chamber 711, which is only shown schematically. The external combustion chamber 771 is also supplied with fuel via an inlet K. The combustion gases generated in the outer combustion chamber 771 are fed to the slot 769 serving as the inlet slot and expand in the working space passing through the gusset 751 until they can flow out through the outlet slot 778. The connecting lines between the slots 767, 769 and the outer combustion chamber 771 can contain valves 775, 777 in order to be able to reliably control the inflow and outflow of gas into and from the outer combustion chamber 771.

The valves can generally consist of simple check valves or can be controlled in the usual way.

When a pressure medium source, for example, there is a steam generator, a compressed air or pressure oil source and the like. Available that none of the respective rotary machine itself supported or compressed combustion air compels be¬ of ^"the machine acc. Fig. Operated 20 so may that In each case, two working chambers work simultaneously in the working ⁽ expansion) cycle or in the exhaust cycle, in which case pressure medium is then fed to both the slot 776 and the slot 769. The rotor can also contain more or less than five power parts. An odd number of line parts, for example five, is generally preferable to an even number, since the work cycles are then better offset from one another and the result is a more uniform run than with an even number of power parts.

It was already mentioned in connection with FIG. 17 that the machine can be driven or driven, as described, also in an electromagnetic manner, by using the rotor as an armature or short-circuit rotor and the housing as a stator of a rotating electrical machine are trained. This is particularly useful when using the present machine as a pump for aggressive or dangerous fluids. The stator winding can also be arranged in the bottom and cover of the housing and the rotor is then designed in the manner of a disc rotor.

If the present rotary piston machine is designed as a working machine, all or part of the work generated can be taken from it by an integrated electromagnetic generator which can be designed similarly to the above-mentioned electromotive drive machines.

A rotary piston machine of the type shown in FIG. 20 with two (or more) bulges 751, 752 of different sizes can also be used advantageously for multi-stage processes. For example, in the machine according to FIG. 20, a compressive pressure medium (e.g. steam) supplied by an external pressure medium source can be released in two stages under workload. In this case, the pressure medium is fed in through the inlet 776 and partially relaxed in the smaller chamber 752.

- • ξtJREA The partially relaxed pressure medium exits through the outlet 767 and is fed into the inlet 769 (if necessary after reheating). The second expansion stage now takes place in the larger chamber or bulge 751, and the pressure medium, which is expanded in two stages, emerges from outlet 778.

Analogously, the machine according to FIG. 20 can also be operated as a two-stage compressor. In this case, the fluid to be compressed is fed to the opening 769. The first compression stage takes place in the larger chamber or bulge 751. The pre-compressed pressure medium exits from opening 778 and is fed to opening 776, whereupon it is subjected to a second compression stage in the smaller chamber or bulge .752. The two-stage compressed pressure medium then emerges from the opening 767.

A rotary piston machine of the type explained with reference to FIGS. 20 to 22 can of course also have more than two bulges corresponding to bulges 751 and 752, which can be of the same or different sizes, so that even more work cycles or expansion or compression stages available.

Those skilled in the art will recognize that the described exemplary embodiments can also be modified in another way and that certain features that have been described in one exemplary embodiment can also be used in other exemplary embodiments.

Claims

1. Rotary piston machine with a) a housing (10) which forms a rotor chamber (23) which is delimited by an inner wall of the housing, b) one which is rotatably mounted in the rotor chamber (23) about an axis (30) Rotor (12), c) a number of piston-like or slide-like power parts (14) which are mounted radially displaceably in the rotor (12), d) a sealing arrangement (60, 62, 72) for the sliding sealing of the power parts (14), the rotor (12) and the rotor chamber (23) with respect to one another and e) a power part control device which, when the rotor (12) rotates in the rotor chamber (23), causes a forced displacement of the power parts (14) the rotor (12) causes 1 characterized in that f) the number of power parts (14) slidably mounted in the rotor (12) is greater than 2, and that g) the power part control device contains a polygonal 5 control part (16), which by one to the rotor chamber

(23) concentric axis (32) rotatably mounted and coupled to the power parts (14) (Fig. 1 and 2).

2. Rotary piston machine according to claim 1, d a -

10 due to the fact that the control part (16) has a polygonal collar (56) with which the power parts (14) are essentially immovable in the radial direction, but are slidably coupled in the circumferential direction.

15

3. Rotary piston machine according to the preamble of

Claim 1, in which f) the number of slidably mounted in the rotor (112)

Power parts (114) is greater than 2, and that

20 9) the power part control device contains connecting rods (186), the ends of which are remote from the power parts and are rotatably mounted about an axis (132) coaxial to the rotor chamber (123), that is to say that

^Is' 25) h is the associated power part (114a) facing away from the end of a connecting rod (186a) rotatably mounted on a disc (194) which is mounted rotatably about 4ie axis (132) of the rotor chamber (123), and that i) the associated power units (114, ...)

30 th ends of the other connecting rods (186b, ...) on the disc (194) are pivotally mounted (Fig. 8).

4. Rotary piston machine according to the preamble of claim 1, d a d u r c h g e k e n n z e i ch-

35 n e t that the power section control device

(219, 225) is arranged essentially outside the rotor. 5. Rotary piston machine according to claim 4, characterized in that the power part control device contains at least one in the housing (10) arranged control cam (225).

6. Rotary piston machine according to claim 4, that the power part control device contains a magnet system that performs the function of a control curve.

7. Rotary piston machine according to one of the preceding claims, that the rotor chamber has the shape of a circular cylinder, and that the essentially circular rotor is rotatably mounted about an axis eccentric to the axis of the rotor chamber.

8. Rotary piston machine according to one of claims 4 to 6, characterized in that the rotor chamber has a non-circular cross-section and that the power part control device is so designed that it rotates more than one stroke cycle of the power parts in the rotor chamber with one revolution of the rotor in the rotor.

9. Rotary piston machine according to one of the preceding claims, d a d u r c h g. The fact that the housing (510) and the rotor (512) contain an electromagnetic device (587) corresponding to an AC machine.

10. Rotary piston machine according to claim 8, that the cross-section of the rotor chamber has approximately the shape of a circle with at least two crescent-shaped bulges (751, 752) and that the bulges

MPI (751, 752) have different cross-sectional areas.

11. Rotary piston machine according to one of the preceding claims, that a combustion chamber (755) is provided on the circumference of the rotor (712) between two power parts (714) in each case.

12. A rotary piston machine as claimed in claim 11, wherein each combustion chamber (755) contains at least one of the following devices:

α a spark plug (757); ß a fuel injector (789).