EP0048415A1 - Rotary-piston machine - Google Patents

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

• a) einem Gehäuse, das eine Rotorkammer bildet, welche durch eine Gehäuseinnenwand begrenzt ist,
• b) einem in der Rotorkammer um eine Achse drehbar gelagerten Rotor,
• c) kolben- oder schieberartigen Leistungsteilen, die im Rotor radial verschiebbar gelagert sind,
• d) einer Abdichtanordnung zum gleitenden Abdichten der Leistungsteile, des Rotors und der Rotorkammer in bezug aufeinander und
• e) einer Leistungsteil-Steuervorrichtung, die bei einer Drehung des Rotors in der Rotorkammer eine zwangsweise Verschiebung der Leistungsteile bezüglich des Rotors bewirkt.

The present invention relates to a rotary piston machine

• a) a housing which forms a rotor chamber which is delimited by an inner wall of the housing,
• b) a rotor rotatably mounted about an axis in the rotor chamber,
• c) piston-like or slide-like power parts which are mounted in the rotor so as to be radially displaceable,
• 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 unit control device which, when the rotor rotates in the rotor chamber, causes the power units to be displaced with respect to 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.

From _D E 28 53 423A1 a seal between three bodies movable relative to each other is known, which can be used in the described or in a modified form with advantage in the present rotary piston machines.

A disadvantage of the known rotary piston engine that they in each case only a single Scar Compression _K per revolution of the rotor and are able to perform expansion process. Not only does this result in relatively high power-to-weight ratios, but also the machine does not run excessively smoothly. This lack can. countered by increasing the number of power units per rotor, no longer use the known device for the forced or positive control of the power units. 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, rotary piston machines with three or more, in particular five, power parts are to be specified, the radial stroke movements of which gations with respect to the rotor by a novel control device forcibly (so not by springs that push the power parts outwards) so 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 predetermined 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 units. With their end facing away from the housing inner wall, the power parts 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 parts are coupled via a connecting rod arrangement to a disk rotatably mounted in the center of the rotor chamber.

In a preferred, different type of the present rotary piston machine, the control device is located outside the rotor. The control device works 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 magnet 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, special advantages are achieved in that a combustion chamber is provided in the rotor between two adjacent power units.

Special designs of the rotary piston machines of the present type working with "external control" are characterized 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 efficiency can be achieved.

• Fig. 1 einen Längsschnitt einer Rotationskolbenmaschine gemäß einer ersten Ausführungsform der Erfindung;
• Fig. 2 einen Querschnitt in einer Ebene II-II der Fig. 1;
• Fig. 3 eine Draufsicht auf ein Kupplungs- oder Steuerteil der Rotationskolbenmaschine gemäß Fig. 1 und 2;
• Fig. 4 eine Seitenansicht des Steuerteiles gemäß Fig. 3;
• Fig. 5 eine Seitenansicht eines Leistungsteiles der Rotationskolbenmaschine gemäß Fig. 1 und 2;
• Fig. 6 eine in Richtung von Pfeilen VI-VI gesehene Ansicht des Leistungsteiles gemäß Fig. 5;
• Fig. 7 eine schematische Darstellung einer Rotationskolbenmaschine gemäß einer zweiten Ausführungsform der Erfindung;
• Fig. 8 einen Axialschnitt einer bevorzugten, dritten Ausführungsform einer Rotationskolbenmaschine gemäß der Erfindung;
• Fig. 9 einen vereinfachten Querschnitt in einer Ebene IX-IX der Fig. 8, wobei der Rotor in der rechten Hälfte der Zeichnung in Draufsicht (nicht geschnitten) dargestellt ist;
• Fig. 10 eine Draufsicht auf einen Gehäusedeckel der Rotationskolbenmaschine gemäß Fig. 8 gesehen in Richtung von Pfeilen X-X;
• Fig. 11 eine Draufsicht auf den Rotor der Rotationskolbenmaschine gemäß Fig. 8;
• _Fig. 12, 13 und 14 ein Längsschnitt, eine Seitenansicht und eine Draufsicht auf ein Leistungsteil für die Rotationskolbenmaschine gemäß Fig. 8 und 9;
• Fig. 15 eine Fig. 9 entsprechende Schnittansicht einer Ausführungsform der vorliegenden Rotationskolbenmaschine mit als Flachschieber ausgebildeten Leistungsteilen;
• Fig. 16 einen Querschnitt durch eine Rotationskolbenmaschine gemäß der Erfindung mit einer abgewandelten Gehäusekonstruktion, die eine Magnetanordnung enthält;
• Fig. 17 eine schematische Querschnittsansicht einer Rotationskolbenmaschine gemäß der Erfindung; bei der die Leistungsteile magnetisch gesteuert werden;
• Fig. 18 eine Draufsicht auf eine Rotationskolbenmaschine mit einer Vorrichtung, die bei Verwendung der Maschine als Pumpe oder Verdichter eine Steuerung der Förderleistung bei konstanter Antriebsdrehzahl ermöglicht;
• Fig. 19a einen Axialschnitt einer Steuerscheibe für eine Rotationskolbenmaschine der in Fig. 8 dargestellten Art;
• Fig. 19b eine Draufsicht auf einen Gehäusedeckel einer Rotationskolbenmaschine mit einer in diesem gelagerten Steuerscheibe gemäß Fig. 19a;
• Fig. 20 eine schematische Querschnittsansicht eines Gehäuses einer Rotationskolbenmaschine, deren Rotorkammer einen nichtkreisförmigen Querschnitt hat;
• Fig. 21 eine perspektivische Darstellung eines Rotors für die Rotationskolbenmaschine gemäß Fig. 20, wobei nur der Bereich einer einzigen Arbeitskammer genauer dargestellt ist;
• Fig. 22 eine vereinfachte Querschnittsansicht eines abgewandelten Rotors für die Rotationskolbenmaschine gemäß Fig. 20, wobei die obere und die untere Hälfte zwei verschiedenen Varianten entsprechen.

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.

• 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;
• 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;
• 5 shows a side view of a power section of the rotary piston machine according to FIGS. 1 and 2;
• FIG. 6 shows a view of the power unit according to FIG. 5 seen in the direction of arrows VI-VI;
• 7 shows a schematic illustration of a rotary piston machine according to a second embodiment of the invention;
• 8 shows an axial section of a preferred, third embodiment of a rotary piston machine according to the invention;
• 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);
• FIG. 10 shows a plan view of a housing cover of the rotary piston machine according to FIG. 8 seen in the direction of arrows XX;
• FIG. 11 shows a plan view of the rotor of the rotary piston machine according to FIG. 8;
• _F ig. 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;
• 16 shows a cross section through a rotary piston machine according to the invention with a modified housing construction which contains a magnet arrangement;
• 17 is a schematic cross-sectional view of a rotary piston machine according to the invention; in which the power units are controlled magnetically;
• 18 shows a plan view of a rotary piston machine with a device which, when the machine is used as a pump or compressor, enables the delivery rate to be controlled at a constant drive speed;
• 19a shows an axial section of a control disk for a rotary piston machine of the type shown in FIG. 8;
• 19b shows a plan view of a housing cover of a rotary piston machine with a control disk mounted therein in accordance with FIG. 19a;
• 20 shows a schematic cross-sectional view of a housing of a rotary piston machine whose rotor chamber has a non-circular cross section;
• FIG. 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 FIGS. 1 and 2 as the first exemplary embodiment of the invention essentially consists 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 is essentially in the form of a circular disk, has a stub shaft 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 is relative to a central axis 32 of the rotor chamber 23 is eccentric. For storage, for example, two roller bearings 34, 36, of which the roller bearing 34 is located in an opening in the base 18, are guided through the stub shaft 26 to the outside, while the other is seated on a journal 38 which is through an annular groove 40 in the housing cover 20 is formed.

As shown in FIG. 2, five power units 14 are arranged in rotor 12 at equal angular intervals of 72 ° each. The power parts have an essentially circular cross section and are radially displaceably mounted in corresponding radial bores of the rotor and are convex with respect to these bores by means not shown tional piston rings sealed, which are used in piston ring grooves 33 (Fig. 5 and 6). At their outward-facing ends, the power parts each have a cylindrical rounding 42, as seen in the axial direction of the rotor (FIG. 6), and a slot 44 used to accommodate sealing elements (FIG. 6). At the other, inner end 46, the power parts taper in a wedge shape as seen in the axial direction (FIG. 6) and 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 furthermore has an upstanding collar 56 which extends into the interior of the rotor and which has the shape of a polygome with the same number of sides as there are power units and which engages with its sides in each case in a coupling slot 50 of a power unit, as in FIG. 1 (only one power section is shown in FIG. 1 because of the five-fold symmetry of the rotor-power section arrangement).

The control part 16 and the power parts are dimensioned and arranged such that the outer ends of the power parts are forcibly guided along a cylindrical circumferential surface 58 of the rotor chamber at a substantially constant close distance when the rotor 12 is eccentrically mounted in the rotor chamber. Furthermore, the inner 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.

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 to the side of the angle sealing strips No. 2 (see FIG. 3 of DE 28 53 423A1).

In the embodiment illustrated in Figures 1 and 2, rotary piston engine, the end-face sealing of the _L occurs eistungsteile 14 with respect to the housing inner wall by two sealing elements 60 and 62, which are formed similarly to the sealing elements in Figure 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 annulus sectors, 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 dense plates can be circular. Such a sealing plate is shown schematically in Fig. 2. The housing 10 also has a fluid inlet 76 and a fluid outlet 78, which, as shown in FIG. 2, can consist of corresponding openings in the housing ring 22. However, the inlet and the outlet can also be formed by corresponding openings in the base 80 and cover 20, as shown for example in FIG. 20.

A working space 79 is formed by two adjacent power parts 14, the outer circumferential 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 via the shaft end 26 in the direction of arrow 80. 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 delivered is thereby sucked in through the inlet 76. In position 79c the working space has reached its maximum 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 shown in positions 79d and 79e. 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 contains a polygonal control body but a connecting rod assembly. The housing, rotor and rotor bearing can be designed as in the rotary piston machine according to FIGS. 1 and 2. Furthermore, as in FIGS. 1 and 2, five piston-like power parts 114a to 140e are slidably mounted in corresponding radial bores of the rotor 112. The sealing arrangement can be designed as explained below; for the sake of simplicity only one sealing element 162 for the power part 114, c is indicated.

The power units 114-b 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), coaxial with the axis 132 of the rotor chamber 123 a housing cover, not shown in FIG. 7, is attached. The power section 114a is also connected to a connecting rod 186a via a bearing 182 with a bearing pin 184, but this connecting rod is attached to the disc 190 by a non-pivotable attachment 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.

The described central to the rotor chamber 123 _P leuelstangenanordnung ensures that the end faces of the power modules ₁₁₄ in close, substantially constant distance along the outer surface 158 of the rotor chamber and the sealing 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 during the rotation of the rotor 112 in the rotor chamber 123, while the other connecting rods carry out oscillating movements owing 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 conveyed or a driving ig are in _F. 7 not shown. The rotary piston engine according to Figure 7 can as that according to Figures 1 and 2 are operated as a vacuum pump or as a compressor or when supplied with a pressurized fluid as a hydraulic or p _re -. Operate matic motor.

The described connecting rod bearing with the disc 190 has in comparison to the known connecting rod bearings (see for example US 35 37 432 A1 and US 40 61 450 A 1) that the connecting rods do not need to be cranked or forked, so that the machine builds flat, high is resilient and allows large radial power unit strokes.

The bearing pin 154 can also be made by means of a pivot bearing, not shown, e.g. of a roller bearing can be rotatably mounted in an opening of the cover 20, wherein the bearing pin can be fixedly or also rotatably connected to the disk 190. As a result, 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 included a power part control device disposed inside the rotor. A significant simplification can now be achieved in that the relative movement taking place between the power units and the rotor is controlled outside the rotor, i.e. the power unit control device is located outside the rotor, in particular essentially in the lid and bottom of the housing. 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 complicated control programs can also be implemented. For example, the power units can perform several lifting cycles with one revolution of the rotor, which is particularly advantageous when using the present rotary piston machine as an internal combustion engine, since e.g. let the four working cycles of a four-stroke engine be realized 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 corresponds in many respects to that according to FIG. 1, the following explanations will therefore also be restricted essentially to the new features.

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 holes 215 each receive a control pin 217, the ends 219 of which extend outward through radial slots 221 of the rotor. A circular, groove-like control cam 225 is provided in the bottom 218 and in the cover 220, into which the ends 219 of the control bolts 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 near the outer ends of the bores 213 (see FIGS. 8 and 11). The ends of these semi-circular 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 bores 273 (FIG. 9), not shown. The semi-ring-shaped seals are pressed against the power section 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 units while the rotor rotates about its eccentric axis 230. The housing is provided with not shown in Figure 11 inlet and outlet ports, similar to the housing of the rotary piston engine according _{to FIGS.} 2 and the machine according to FIG. 8 accordingly operates in a manner quite analogous to the machine described above according to FIGS.

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 eccentrically mounted in the rotor chamber 323 contains five power parts 314 which have the form of flat slides with an essentially 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. 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 performance of the machine can be increased. The displacement of the power units with respect to the rotor is controlled by control curves, 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 housing inner wall by sealing strips 372 in the form of annular sectors. Sealing strips 331, which run axially, are used 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 units with respect to the rotor can be supported or brought about 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 magnet windings in the housing ring 422 can consist of two solenoid coils, the windings of which run circumferentially 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 inside and outside of the housing ring 422 in each case an annular magnetic pole is created.

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 poles 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 parts 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 means of control cams 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, e.g. similar to the control pin 217 in Fig. 8 made of magnetic material which cooperate with the cam magnetic 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, an annular magnetic pole is formed, which acts as a magnetic control curve 525 for magnetic insert bolts 517 of the power units 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 two of a total of five stator windings 587 are also indicated, which are arranged in the housing ring 522 and with which made of a highly conductive material, e.g. Aluminum or copper existing rotor 512 form an induction motor. The rotor can also contain short-circuit windings or a permanent magnet system in a known manner.

In the present rotary piston machines, the working space stroke, that is, 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 shifting device is provided there, with a mechanical or electrical coupling ensuring that the displacement of the bearing pieces 43 on both sides is synchronized. 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 runs concentrically with the rotor chamber 23, so that there is no change in volume of the rotor rotation be sawn _gives' place work spaces between each 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 from zero to a maximum value which corresponds to the greatest 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. In this way, the delivery rate and delivery direction of a rotary piston machine of the type described, which works as a pump or compressor, can be continuously changed 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 working with external control of the type described with reference to FIG. 8 can be considerably reduced. The use of at least one rotating combustion chamber, as will be explained with reference to FIGS 20 to 22, ensures high efficiency in use of the present machine as Innenbrennkraf _t machine. The non-circular design of the housing cross section explained with the aid of the same figures enables a rotary piston operating as a four-stroke internal combustion engine machine the expansion space to choose greater than the _K om pressionsraum so that a very good fuel efficiency can be achieved.

Instead of the circular control cams 225 described in FIG. 8, which serve to control the displacement of the power units, an annular control disc 700 can be used, as is shown in axial section in FIG. 19a and in a top view in FIG. 19b. Each control disk 700 is rotatably mounted in an annular groove in accordance with the control curves and has circular-arc-shaped recesses 702 for the storage of the ends 719 of the bearing or control bolts 715 of the power units. In Fig. 19b only two such recesses are shown to simplify the drawing. In the recesses 702, the ends 719 of the bearing bolts are supported 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 immovably mounted in the guide washer. 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-tale (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, as a result of the correspondingly shaped recesses 702 is made possible.

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 annular groove 702 ', so that it acts as a driver. By using control disks 700, the stress and thus the wear of the power section control are considerably reduced.

The suitability of rotary machines of the type described above can be significantly 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 is increased, 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 shown only schematically in FIG. 21 and, for example, as can be seen from FIG. 22, can contain five piston-like or slide-like power units.

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 opposed 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 Ge 20 are also provided with a gusset-shaped inlet slot 776 and a gusset-shaped outlet slot 778, which are located on one pair of the mutually facing ends of the crescent-shaped bulges 751 and 753, respectively, in the embodiment of the present rotary machine shown in FIG. 20.

In this embodiment of the present rotary machine, the circular disk-shaped rotor 712 shown in perspective or in cross section in FIGS. 21 and 22 contains 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. 22 below is. If one disregards the different sizes of the bulges, 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 designed in a manner known per se or as explained above.

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

In the present embodiment of the rotary machine, the rotor 712 is provided in its cylindrical side surface 7 ₁ 2a with a combustion chamber 755 between two power parts in each case. Two axially offset recesses 761 extend from each combustion chamber, which 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 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 ar work together in a manner known per se with a mating contact, not shown, which is located on the inside of the housing cover and is connected to an ignition coil.

20 to 22 operates similarly 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 (circumferential) 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-like 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 to positions V and VI. In the last-mentioned positions, the top again

Correspond to the dead center in a piston engine, the volume of the work space in question has a minimum again, the compression cycle has ended and the ignition takes place (with regard to early or late ignition there are similar conditions as with 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.

All five work chambers run through the cycle described in succession. With one revolution of the rotor, five complete four-stroke cycles take place. This results in a high performance and a smooth run.

Characterized in that the bulge 752, which enters nsaugraumes in the volume of _A, is chosen to be smaller than the volume of the bulge 751, which is received in the volume of the expansion or working space, a very substantial expansion, for example, can be up to about atmospheric pressure, to reach what has a high degree of efficiency, since the combustion gases can be expanded to a very large extent.

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 in such a way that it communicates with the working space containing the compressed gas.

20 to 22 can of course also be operated as a diesel engine, in which case the spark plugs 757 or 757 'are 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 working space, in particular into each combustion chamber 755, which is supplied with fuel by an injection pump via a suitable line and distributor system, e.g. via a hollow shaft 726, which has a radial bore 791, which, when the rotor rotates about the essentially fixed hollow shaft, performs the distribution function for the fuel.

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 at the bottom left in FIG. 22.

If the rotary machine described is operated as an internal combustion engine without direct injection of the fuel into the working chambers, the inlet slot 776 is of course with a carburetor or 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. Fuel is also supplied to the outer combustion chamber 771 via an inlet K. The combustion gases generated in the external 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.

If a pressure medium source, for example a steam generator, a compressed air or pressure oil source and the like, is available that does not require combustion air that is itself conveyed or compressed by the rotary machine in question, the machine can be operated according to Fig be operated. 20 so that each two working chambers operate simultaneously clocked in _Arb eits- (expansion) stroke or "in the exhaust. In this case, both the slot 776 and the slot 769 are then supplied with pressure medium.

The rotor can also contain more or less than five power parts. An odd number of line parts, e.g. five is generally preferable to an even number, since then the work cycles are better offset from one another and the result is a more even run than with an even number of power units.

It had already been mentioned in connection with FIG. 17 that the machine can be driven or driven, as described, also in an electromagnetic manner, in that the rotor is designed as an armature or short-circuit rotor and the housing as a stator of a rotating electrical machine . 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 (for example steam) supplied by an external pressure medium source can be released in two stages with work performed. In this case, the pressure medium is fed in through the inlet 776 and partially expanded in the smaller chamber 752.

The partially relaxed pressure medium exits through the outlet 767 and is fed into the inlet 769 (if necessary after reheating). The second _E ntspannungsstufe now takes place in the larger chamber 751 or bulge and the two-stage relaxed pressure medium passes out of the outlet 778 from.

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 emerges from the opening 778 and is fed to the 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 protrusions corresponding to protrusions 751 and 752, which can be of the same or different sizes, so that one then has even more work cycles or expansion or compression stages Has available.

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

Claims (12)

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) a rotor (12) rotatably mounted in the rotor chamber (23) about an axis (30), c) a number of piston-like or slide-like power parts (14) which are mounted in the rotor (12) so as to be radially displaceable, 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 unit control device which, when the rotor (12) rotates in the rotor chamber (23), causes the power units (14) to be displaced with respect to the rotor (12), 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 control part (16) which is rotatably mounted about an axis (32) concentric to the rotor chamber (23) and is coupled to the power parts (14) (FIGS. 1 and 2). 2. Rotary piston machine according to claim 1, characterized in that the control part (16) has a polygon-shaped collar (56) with which the power parts (14) are coupled substantially immovably in the radial direction, but are displaceably coupled in the circumferential direction. 3. Rotary piston machine according to the preamble of claim 1, in which f) the number of power parts (114) displaceably mounted in the rotor (112) is greater than 2, and that g) the power part control device contains connecting rods (186) whose ends facing away from the power parts are rotatably mounted about an axis (132) coaxial with the rotor chamber (123),
characterized in that h) the end of a connecting rod (186a) facing away from the associated power part (114a) is attached in a rotationally fixed manner to a disk ( ₁₉ 4) which is rotatably mounted about the axis (132) of the rotor chamber (123), and that i) the ends of the other connecting rods (186b, ...) facing away from the associated power parts (114, ...) are pivotably mounted on the disk (194) (Fig. 8). 4. Rotary piston machine according to the preamble of claim 1, characterized in that the power part 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 control cam (225) arranged in the housing (10). 6. Rotary piston machine according to claim 4, characterized in that the power part control device contains a magnet system which performs the function of a control curve. 7. Rotary piston machine according to one of the preceding claims, characterized in that the rotor chamber has the shape of a circular cylinder, and that the substantially circular disk-shaped rotor is rotatably mounted about an axis eccentric to the axis of the rotor chamber. 8. Machine according to one of claims 4 to 6, characterized in that the rotor chamber has a nichtkreisförmi ^g s cross-section and that the power supply control device is formed so that it in one revolution of the rotor in the rotor chamber more than one stroke cycle of the power modules in the Rotor causes. 9. Rotary piston machine according to one of the preceding claims, characterized in 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, characterized in 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 (751, 752) have different cross-sectional areas. 11. Rotary piston machine according to one of the preceding claims, characterized in that a combustion chamber (755) is provided on the circumference of the rotor (712) between each two power parts (714). 12. Rotary piston machine according to claim 11, characterized in that each combustion chamber (755) contains at least one of the following devices: a a spark or glow plug (757); B a fuel injector (789).

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