WO1995034750A1

WO1995034750A1 - Internal-combustion engine, compressor or pump

Info

Publication number: WO1995034750A1
Application number: PCT/EP1995/001881
Authority: WO
Inventors: Robert Schnetzer
Original assignee: Robert Schnetzer
Priority date: 1994-06-10
Filing date: 1995-05-17
Publication date: 1995-12-21
Also published as: AU2565295A; WO1995034749A1

Abstract

The invention concerns two internal-combustion engines as well as rotary compressors or pumps derived from them. The two engines are each characterized by a very simple and compact design and consist essentially of a cylindrical housing in which two interlocking rotary pistons are mounted so that their axes are symmetrical, the pistons executing an oscillating motion in one engine and an alternating rotary motion in one direction in the other engine. The drive is transmitted in both cases through a lever, con-rod and crank in a rotary motion, the crankshaft of the second engine rotating, in addition, about the axis of the cylinder in a similar way to the planet wheel of a planetary gear.

Description

V e r b r e n n u n g s m o t o r, K o m p r e s s o r o d e r P u m p e

Technical field

The invention relates to two internal combustion engines which operate according to the rotation principle and can be used to drive motor vehicles, ships, airplanes and devices. Furthermore, the present invention relates to a group of compressors and pumps which can be derived from the internal combustion engines according to the invention.

PRIOR ART A large number of different rotary piston machines are currently known to us. Such is e.g. the Wankel engine. The rel. high production costs and problems with sealing have prevented the correct breakthrough of this engine to this day. In contrast, the gasoline and diesel engine could be improved somewhat with the help of multi-valve technology and turbocharging as well as better injection technology in the performance range. However, these motors still have a rel. high manufacturing costs and poor conversion of the fuel into mechanical kinetic energy.

The object of the invention is two rotary piston engine types, each consisting of a cylindrical housing with side covers and two centrally mounted shafts equipped with rotary pistons, which perform a back and forth movement at a certain angle, or at which second type, the rotary lobes perform an alternating, unidirectional movement. A motor similar in construction has become known from US Pat. No. 5,133,317. The simple construction of the construction results in a very favorable price-performance ratio of this engine.

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According to the invention, this is achieved by the two series of the above type from the first row in that in a cylindrical housing, two interlocking, double-acting and axially symmetrically mounted rotary piston shafts with their rotary pistons rotate back and forth by an angular amount. At the same time, two disks for the control of the inlet and outlet bores in the cylinder housing perform a uniform rotational movement in one direction. The power is transmitted in a rotary motion using a lever, connecting rod and crank. The second series is characterized in particular by the fact that in a cylindrical housing that can be closed on both sides, only two interlocking, axially symmetrical rotary lobe shafts with rotary lobes rotate alternately and with changing angular velocity, in one direction and, as a result, and outlet bores in the housing, open and close. The power transmission takes place as with the described first series, by means of lever, connecting rod and crank in a rotary motion. In addition, these parts also perform a uniform rotational movement in one direction. Similar to the planetary gear of a planetary gear, the crankshaft rotates around a fixed sun gear. Furthermore, the present invention relates to a group of pumps and compressors which can be derived from the aforementioned internal combustion engines insofar as bores are provided in the cylinder housing of the aforementioned engines instead of the bores for the spark plugs for the exchange of the working media become.

Compared to internal combustion engines of a similar design, the engines according to the invention are distinguished by a very simple construction. This also makes it possible to significantly reduce manufacturing costs. All essential components of these motors have cylindrical surfaces that are easy to grind and can be easily manufactured with high precision. The seal also poses no problems. Almost absolute tightness can be achieved with conventional sealing elements. Thanks to the special wedge-shaped design of the combustion chambers and the uniformly high temperatures of the rotary lobes and the cylinder wall, it is possible to achieve almost complete combustion of the fuel and thus to considerably reduce the proportion of toxic exhaust gases, especially carbon monoxide. Another advantage of these motors is their small size. In comparison to a Wankel engine of the same power, the dimensions of the engines according to the invention can be reduced by approximately 20%. At the same time, this leads to a mass reduction of approximately 30%. The motors according to the invention do not require a separate distribution system for the fuel / air mixture, since the rotor parts automatically close and open the holes provided for this purpose. The engines can be equipped with known ignition and carburetor systems. With appropriate dimensioning and sealing, it is also possible to charge the work spaces by means of a turbocharger. It is also possible to use diesel as fuel instead of spark plugs. The lubrication of these motors can be carried out in a conventional manner, with additional lubrication, in some cases entirely being dispensed with when using ceramic motor parts.

BRIEF DESCRIPTION OF THE DRAWINGS The two series are explained in more detail below using an example and with reference to the accompanying drawings, in which:

FIG. 1 a longitudinal section through the engine, series 1,

FIG. 2 a section through the cylinder, series 1, acc. the line AA in FIG. 1, FIG. 3 shows a section through the cylinder, series 1, continued from FIG. 2, FIG. 4 the top view of the control disk with inlet opening, series 1, FIG. 5 shows a cross section along the line BB in FIG. 4, FIG. 6 the top view of the housing cover of the series 1, FIG. 7 shows a cross section along the line CC in FIG. 6,

FIG. 8 a section through the cylinder, engine variant 1, series 1,

FIG. 9 shows a section through the cylinder, engine variant 1, continued. v. FIG. 8th,

FIG. 10 shows a longitudinal section through the motor of the series 2,

FIG. 11 a section through the cylinder, series 2, acc. the line D-D in FIG.10, FIG. 12 shows a section through the cylinder of series 2, continued. v. FIG. 11, FIG. 13 a section through the crank mechanism, according to FIG. the line E-E in FIG. 10, FIG. 14 the top view of the housing cover of the series 2, FIG. 15 shows a cross section along the line F-F in FIG. 14, FIG. 16 a section through the cylinder, engine var. 1, series 2, FIG. 17 shows a section through the cylinder, engine var. 1, continued v. FIG. 16, FIG. 18 shows a section through the cylinder, engine var. 2, series 2, FIG. 19 shows a section through the cylinder, engine var. 2, continued v. FIG. 18, FIG. 20 shows a system cross section through motor var. 3, series 2, FIG. 21 shows a system cross section through engine var. 3, continued v. FIG. 20, FIG. 22 shows a system cross section through engine var. 4, series 2,

FIG. 23 shows a system cross section through engine var. 4, continued v. FIG. 22, FIG. 24 shows a system cross section through engine var. 5, series 2, FIG. 25 is a cross-section through system _^ motor Var. 5, continued v. FIG. 24, FIG. 26 to FIG. 31 different rotary piston cross-sectional shapes, FIG. 32 to

FIG. 34 shows a possible arrangement of the combustion chamber and the sealing strips, FIG. 35 shows a section through a compressor or pump in the operating state, FIG. 36 a section d. a compressor or pump, continued. v. FIG. 35.

In FIG. 1 the motor of the series 1 according to the invention is shown in longitudinal section. The engine consists of the cylindrical housing 1, in which, arranged radially, there are four symmetrical, mutually opposite bores for receiving spark plugs 11 (see also FIGS. 2 and 3). The cylindrical housing 1 can be closed by housing covers 3 and 5 on its two end faces. In the housing cover 3 there is at least one bore 13 for the supply of the fuel-air mixture to its distribution channel 26 and in the housing cover 5 there is at least one bore 15 for the discharge of the exhaust gases via the collection duct 27 (see also FIGS. 6 and 7). The holes 13, 15 and their channels 26, 27 can optionally only in one of the two housing covers can be arranged or also double, ie provided on both sides. Likewise, it is also possible to produce a housing cover and the cylinder jacket from one part, so that the cylinder housing only consists of two parts. In the cylindrical housing 1 there are two axially symmetrical and rotatable annular disks 2 and 4 which are mounted in the main bearings 18. These are pushed onto the rotary piston shafts and provide with their bores (inlet and outlet opening on both sides, in one disk, or divided between both disks). , for a corresponding exchange of the working media from the collecting and distribution channel 26, 27 to the working spaces 21 to 24 (see also FIG. 4 and 5). Instead of individual, large bores, several smaller openings or radially or tangentially running slots in the control disks ensure a better support of the piston sealing strips 25 (see also FIG. 32). Sealing of the work spaces can be ensured, for example, by sealing rings 9, which are embedded in the housing 1 with claw teeth. Likewise, the sealing of the distribution and collection channels of circumferential sealing rings 16 can be ensured. The disks 2 and 4 rotate synchronously in one direction and slide on the housing covers 3 and 5. On the rotary lobe shafts 7a and 8a, two symmetrically opposite lamellae are each designed as rotary lobes and are so nested that the lamellae of one rotor part 7, in the free Space between the fins of the other rotor part 8 fit. The two rotary piston shafts 7a and 8a can be used as a guide by means of bolts 6 or as shown in FIG. 10 shown, be pushed into each other in such a way that they lead each other in their opposite back and forth rotations. The size of the slats 7 and 8 is such that their end faces slide on the control disks 2 and 4 and on the inner surface of the cylindrical housing 1. Due to the special design of the fins, four wedge-shaped chambers 21, 22, 23, 24 are thus formed in the motor housing, the volume of which can be changed by the movement sequence of the rotary pistons 7 and 8.

The power transmission (not shown) can be converted by the two double-acting rotary pistons, connected to the rotary piston shafts 7a and 8a, in each case via a lever and a connecting rod, onto one or two separate crankshafts into a rotary movement. The two disks 2 and 4 are driven by this crankshaft in the ratio 1: 2, so that when two crankshaft revolutions occur, the disks rotate once. The rotary piston shaft with the two rotary pistons can be manufactured from one part or from several parts, which are then assembled. The rotary pistons can be hollow, open to the outside and, as shown in FIG. 32 and 33 is shown, can be provided with conventional sealing elements. The motor can be equipped with air or water cooling in a manner known per se, a corresponding cooling jacket being arranged around the motor housing. The mode of operation of the motor of the first series is described below with reference to FIG. 1, 2 and 3 explained in more detail:

While the two control disks 2 and 4 rotate synchronously and evenly in one direction, the two rotary piston shafts with the rotary pistons 7 and 8 perform an opposite back and forth rotation. As shown in FIG. 2 is shown, a fuel-air mixture is sucked into the working space 21 via the released inlet bore 12, a gas sucked in before is compressed in the space 22 and a gas compressed before it is brought to an explosion by the spark plug 11 in the space 23. In room 24, the exhaust gas from the previous work cycle is expelled at the same instant via the outlet bore 14 that has just been released. In FIG. 3 is the continuation of FIG. 2 can be seen. Thus, within a "stroke", four complete bars, i.e. two work cycles take place within one revolution of the crank.

In section through the cylinder of FIG. 8 and 9 is an engine variant of series 1 of the previously described engine, shown in the operating state. This is one and the same engine, but with twice the number of spark plugs 11 in the cylindrical housing 1, inlet bores 12, 13 and bores 14, 15 for the discharge of the exhaust gases. The control discs 2 and 4 rotate synchronously in a ratio of 1: 4 to the crank. In the cylindrical housing on the rotary piston shafts 7a and 8a there are 4 fins 7 and 8, which are designed so that the fins of the one rotary piston 7 fit into the intermediate spaces of the rotary piston 8 and in turn perform an opposite reciprocating movement. With this engine, four complete work cycles take place within one crank revolution.

In FIG. 10 the motor of the series 2 according to the invention is shown in longitudinal section. The engine consists of the housing parts 1, 28 and 29, in which, radially or axially arranged, there is a bore for receiving a spark plug 11. Due to the ignition of the fuel before the respective crankshaft dead center is reached, two spark plugs, correspondingly placed in the cylinder housing, ensure an even more precise merging of the compression or combustion chambers of the rotary pistons 7, 8 with the spark plugs 11. This is on the two end faces Cylinder housing 1 can be closed with the housing covers 28 and 29. In the housing cover 28, the bore 13 for the supply of the fuel-air mixture and the bore 15 for the removal of the exhaust gases are arranged (see also FIGS. 14 and 15). Optionally, the bores for the supply and discharge of the working media can also be provided in both housing covers and in the cylindrical housing 1, one or more times, at the appropriate place, with several smaller openings or radial or instead of individual large bores tangential slots can be arranged. Optionally, a housing cover and the cylinder jacket can be made from one part, so that the cylinder housing consists of only two parts. On the rotary piston shafts 7a and 8a, two symmetrically opposite lamellae 7 and 8 are each designed as rotary lobes and are nested in such a way that the lamellae of one rotor part 7 fit into the free space between the lamellae of the other rotor part 8. The two rotary piston shafts 7a and 8a are mounted in the main bearings 18 and can be used as a guide, as already shown in FIG. 1, by means of bolts 6 or as in FIG. 10 shown, be pushed into each other in such a way that they lead each other in their different rotary movements. The slats 7 and 8 are designed in size so that they slide with their end faces on the inside of the cylindrical housing 1 and on the housing covers 28 and 29. In contrast to the first series, the two rotary lobe shafts with their rotary lobes rotate in this direction, alternately, with changing angular velocity, in one direction. As shown in FIG. 13, the power is transmitted from the two double-acting rotary pistons 7 and 8, which are connected to the rotary piston shafts 7a and 8a, via the levers 7b and 8b to the two connecting rods 7c and 8c on the two crankshafts 7d and 8d. These are in turn connected to one another via the ring gear 34 to the ring gear 33 of the housing cover 29, in the ratio 1: 2. It is also possible with this series to have the power transmitted from the two connecting rods to just one crankshaft.

The operation of the motor of the second series takes place with reference to FIG. 10, 11 and 12 and is explained in more detail below using an example:

During the rotational movement of the crankcase 30 and 31, the two crankshafts 7d and 8d, similar to the planet wheels of a planetary gear, also rotate about their own axis at double speed. As a result, the two rotary piston shafts 7a, 8a with the double-acting rotary pistons 7, 8 perform an alternating rotary movement with changing angular velocity in one direction and thus produce working spaces 21 which are variable in volume in the cylindrical housing 1 between the rotary pistons to 24. In FIG. 11, this engine is shown in the working state, a fuel-air mixture being drawn in via the released inlet bore 13 in the working space 21, a gas drawn in before it being compressed in the space 22 and a gas compressed in front of it being sparked by the spark plug 11 in the space 23. In the room 24, the exhaust gas from the previous work cycle is expelled at the same moment via the just released outlet duct 15. In FIG. 12 is the continuation of FIG. 11 can be seen. Thus, during a rotation of the crankcase, 16 complete cycles, that is to say four work cycles, take place in the working spaces 21 to 24. In section through the cylinder of FIG. 16 and 17, motor variant 1 of series 2 is shown in the operating state. This is the engine as described above, but with twice the number of spark plugs 11 in the cylindrical housing 1, inlet bores 13 and bores 15 for removing the exhaust gases. The crankcase rotates in a ratio of 1: 4 to the crankshafts located therein. In the cylindrical housing there are 4 lamellae 7 and 8 each on the rotary lobe shafts 7a and 8a, which are designed so that the lamellae of the rotary lobe 7 fit into the spaces between the rotary lobes 8 and, with changing angular velocity, move in one direction rotate. With this engine, 32 complete cycles, ie eight work cycles, take place within one revolution of the crankcase.

In section through the cylinder of FIG. 18 and 19, motor variant 2 of series 2 is shown in the operating state. In particular, this engine is characterized by three bores arranged symmetrically offset by 120 °, for receiving spark plugs 11 in the cylindrical housing 1 and in each case three inlet bores 13 and bores 15 arranged symmetrically offset by 120 ° for the removal of the exhaust gases in the housing cover 28 The crankcase rotates at a ratio of 1: 6 to the crankshafts inside. In the cylindrical housing there are two fins 7 and 8 on the rotary piston shafts 7a and 8a, which are designed so that the fins of the rotary piston 7 fit into the spaces between the rotary pistons 8 and in turn perform a movement rotating in one direction. With this engine, two working cycles take place within one crankshaft revolution.

In the system section through the cylinder of FIG. 24 and 25, motor variant 5 of series 2 is shown in the operating state. It is essentially the one already shown in FIG. 18 and 19 described engine, but each with twice the number of spark plugs 11 in the cylindrical housing 1, inlet bores 13 and bores 15 for removing the exhaust gases in the housing cover 28. The crankcase rotates in a ratio of 1:12 to the crankshafts located therein. In the cylindrical housing there are 4 lamellae 7 and 8 on each of the rotary lobe shafts 7a and 8a, which are designed so that the lamellae of one rotary lobe 7 fit into the spaces between the rotary lobes 8 and, with changing angular velocity, move into a direction turn. With this engine, four working cycles take place within one crankshaft revolution.

In the system section through the cylinder of FIG. 20 and 21, engine variant 3 of series 2 is shown in the operating state. In the cylindrical housing 1 there are two symmetrically opposite bores for receiving spark plugs 11 and in the housing cover 28 there are two inlet ports arranged symmetrically opposite one another. Bores 13 and bores 15 are provided for the discharge of the exhaust gases, check valves (not shown) being provided in these openings. The crankcase rotates in a ratio of 1: 4 to the crankshafts located therein. In the cylindrical housing there are on the rotary lobe shafts 7a and 8a in each case two lamellae 7 and 8, which are designed such that the lamellae of the rotary lobe 7 fit into the interstices of the rotary lobe 8 and alternate, with changing angular velocity, turn in one direction. In contrast to the previously mentioned motors of both series, the rotary lobes of this motor only have a single-acting effect, ie there are only two effective working spaces in the cylindrical housing 1. With this engine, two working cycles therefore take place simultaneously within two crankshaft revolutions.

In the system cross section of FIG. 22 and 23, engine variant 4 of series 2 is shown in the operating state. It is the same motor as that previously shown in FIG. 20 and 21 has been described. In the cylindrical housing 1 of this engine there are three bores arranged symmetrically offset by 120 ° for receiving spark plugs 11 and in the housing cover 28 three inlet bores 13 and bores 15 arranged symmetrically offset by 120 ° are provided for the discharge of the exhaust gases , check valves must also be provided in these openings. The crankcase rotates 1: 6 to the crankshafts inside. In the cylindrical housing there are three lamellae 7 and 8 on each of the rotary lobe shafts 7a and 8a, which are designed so that the lamellae of the rotary lobe 7 fit into the spaces between the rotary lobes 8, which in turn rotate alternately in one direction. With this motor, too, the rotary lobes work only single-acting, as with the aforementioned, i.e. there are only three effective working spaces in the cylindrical housing 1. With this engine, three work cycles take place simultaneously within two crankshaft revolutions.

In the system cross section of FIG. 35 and 36 a pump or compressor is shown in the operating state. This machine can be of the in FIG. Derive 10 shown engine of the series 2 in that two holes 13, 15 for the inlet and outlet of the working media are located in the side housing cover 28 instead of the hole for the spark plug 11. The in FIG. 13 crankcase shown with the crankshafts located therein is used in the opposite way, as a drive for the rotary piston shafts. Essentially, all of the motors in the second series can be derived using the measures, pumps or compressors mentioned above. On the other hand, in the case of the two motors of the first series, the additional bores 13, 15 are to be arranged in the two control disks, the collecting and distribution channels in the housing covers being able to be used several times.

Claims

3? claims

1. Internal combustion engines of the first series, consisting of a cylindrical housing which can be closed on both sides, with bores for the installation of spark plugs and exchange of working media, as well as two rotatably mounted control disks and rotary piston shafts in this housing with lamellae designed as rotary pistons, thereby characterized in that there are four, as var., eight bores for spark plugs (11) arranged in pairs offset by approximately 180 ° in the housing (1), in each case at least one bore in the end caps (3, 5) ( 13, 15) and their distribution or collection channel (26, 27) are arranged in the control disks (2, 4), one each, in the case of the variant, two bores (12, symmetrically offset by approximately 180 °) 14) are provided for the exchange of the working media, on the rotary piston shafts (7a) and (8a), inside the housing, two each by approx. 180 °, in the case of the variant, four slats (7, 8) which depend separately of each other, forming four in the Var., eight variable in its volume, wedge-shaped working chambers (21, 22, 23, 24) by supply alternately and turn apart and whose torque is in each case removed from the rotary shafts.

2. Internal combustion engine according to claim 1, characterized in that the two Steuer¬ disks synchronously and evenly in a ratio of 1: 2, in the Var. in a ratio of 1: 4 to the crankshaft, which converts the reciprocating motion of the rotary pistons into a rotary motion by means of a lever and connecting rod, the control disks are each designed to be slidable with their outer contours on the inner wall of the housing cover and the bores in the control disks in the radius of the cylinder axis Collection and distribution channels of the housing cover are identical, so that the working media can be exchanged between them, the bores (12, 14, 13, 15) and channels (26, 27) for exchanging the working media on only one Side of the cylindrical housing or on both sides, ie are arranged in two, the sealing of the working spaces in the area of the control disk and cylinder housing is ensured by two sealing rings (9) which are fixed in the cylinder housing by means of axial claws against rotation and are therefore axially displaceable, and in each case with the surface with the rotary pistons. ben and the control discs are designed to be slidable, the sealing of the distribution and collecting channels is ensured by two circumferential sealing rings arranged on both sides of the channel in the housing cover, which are axially displaceable and either rotate synchronously with the control discs or in the housing covers against rotation are fixed.

3. Combustion engines of the second series, consisting of a cylindrical housing that can be closed on both sides, with holes for the installation of spark plugs and exchange of working media, as well as two rotary piston shafts that are rotatably mounted and pushed into one another, each with two, three or four symmetrical ones arranged slats, characterized in that in the housing (1) one, at the 1st Var., Two bores for spark plugs (11) arranged offset by approx ., each have two bores (13, 15) arranged symmetrically offset by approximately 180 ° and on the rotary piston shafts (7a) and (8a), inside the housing, two each by approximately 180 °, in the 1st Var ., Four lamellae (7, 8) arranged offset by 90 °, which, depending on one another, form four, in the case of the 1st variant., eight wedge-shaped chambers (21, 22, 23, 24) whose volume can be changed by turn alternately, with changing angular velocity in one direction and the torque is taken from two crankshafts, which in addition to their own rotation also around the axis of the cylinder housing in a ratio of 2: 1, with the 1st Var. in a 4: 1 ratio.

4. Internal combustion engines of the second series according to claim 3, characterized gekennzeich¬ net that in the housing (1), three by about 120 °, in the Var. 5, six bores for spark plugs (11) arranged symmetrically offset by approximately 60 ° are in one of the end caps (28, 29), three each by approximately 120 °, in the Var. 5, each are six bores (13, 15) arranged symmetrically offset by approximately 60 ° and on the rotary piston shafts (7a) and (8a), within the housing, two each by approximately 180 °, in the case of the Var.

5, four slats (7, 8) arranged offset by approximately 90 °, which are dependent on one another, four, in the Var. 5, eight, wedge-shaped work spaces (21, 22, 23, 24) which can be changed in their volume form by rotating alternately and with changing angular velocity, in one direction and the moment of which is taken up by two crankshafts, which are in addition to their own Rotation also around the axis of the cylinder housing in a ratio of 6: 1, with the Var. 5 in a 12: 1 ratio, rotate.

5. Internal combustion engines of the second series according to claim 3 and 4, characterized in that in the housing (1), two by about 180 °, in the Var. 3, three around

Bores for spark plugs (11), arranged symmetrically offset by 120 °, are in one of the end caps (28, 29), two each by approximately 180 °, in the Var. 3, in each case three bores (13, 15) symmetrically offset by approximately 120 ° with non-return valves are arranged and on the rotary piston shafts (7a) and (8a), inside the housing, two each by approximately 180 °, at the Var. 3, three lamellae (7, 8) arranged offset by 120 °, which are dependent on one another, two, in the case of the var. 3, form three wedge-shaped work spaces that can be changed in volume by rotating alternately and with changing angular velocity in one direction and the torque of which is taken from two crankshafts, which in addition to their own rotation also rotate around the axis of the cylinder housing in a ratio of 4: 1, at the Var. 3 in the ratio 6: 1, rotate.

6. Internal combustion engines according to claim 3 to 5, characterized in that there is an additional spark plug at a corresponding distance from each spark plug, so that before reaching the two crankshaft dead points, the ignition at a precise point is made, the spark plugs can also be arranged in the side housing covers, the bores (13, 15) for the supply and discharge of the working media also in both housing covers and in the cylindrical housing (1) several times, can be provided at the appropriate place.

7. Internal combustion engines according to claim 1 to 6, characterized in that the lamellae of one rotor part fit into the interstices of the other, thereby miteinan¬ by a connecting bolt (6), axially symmetrically and rotatably connected or in such a way that they are guide each other and are designed to be slidable with the end faces of the lamellae on the two control disks and on the inner surface of the housing (l), the lamellae also shown in FIG. 14 to FIG. 19 shown cross-sectional shapes, instead of individual large bores, several smaller openings or radial or tangential slots in the control disks (2, 4) and in the housing covers (28, 29) are arranged at the appropriate place power transmission from the two rotary piston shafts can also be absorbed by a crankshaft via a lever and a connecting rod.

8. Internal combustion engine according to claim 1 to 7, characterized in that with appropriate dimensioning of the engines, the combustion air supply can be supported by means of turbochargers, are in the cylindrical housing (1), instead of the spark plugs, injection nozzles, which the Allows use of diesel, gas or the like as fuel for injection.

9. Compressor or pump, consisting of a cylinder housing which can be closed on both sides, with bores for the exchange of working media, and two rotary piston shafts, which are rotatably mounted and are nested inside each other, each with two, three or four symmetrically arranged fins, characterized in that that they can be derived from the internal combustion engines characterized in claims 1 and 2 in that instead of the holes for the spark plug (11), twice the number of holes (13, 15) are in the two control disks and the crankshaft in reverse is used as a drive for the rotary lobe shafts, can be derived from the internal combustion engines characterized in claims 3 to 8, so that instead of the holes for the spark plug (11), in the side housing covers (28, 29) or in the housing (1 ), there are twice the number of inlet and outlet openings for the exchange of working media the and the rotating around the cylinder axis and self-rotating crankshaft is used in the opposite way as a drive for the rotary piston shafts. ιo. Internal combustion engine, compressor or pump, according to claims 1 to 9, characterized ge indicates that the cylinder jacket (1) and its housing cover, the rotary pistons and the control disks are coated with a corresponding ceramic material or are made of ceramic material, a housing cover and the cylinder jacket made from one part are manufactured. CHANGED REQUIREMENTS

[at the international office on 11 October 1995 (October 11, 1995) received; original claims 1-10 replaced by new claims 1-10 (3 pages)]

1. Combustion engines of the first series, consisting of a cylindrical housing that can be closed on both sides, with staggered bores for the installation of spark plugs and two axially symmetrically rotatable control units

5 discs with staggered holes, characterized in that in the housing (1) four, as Var. there are eight bores for spark plugs (11) arranged in pairs offset by approx. 180 °, in each case at least one bore (13, 15) and its distribution or collection channel (26, 27) are arranged in the end caps (3, 5) are, in the control disks (2, 4) one, at the Var. two each offset by approx. 180 °

10 ordered bores (12, 14) are provided for the exchange of working media, on the rotary piston shafts (7a) and (8a), within the housing, two each by approx. 180 °, in the case of the Var. four lamellae (7, 8) arranged offset by approximately 90 ° are, which are dependent on one another, four, in the Var. form eight wedge-shaped work spaces (21, 22, 23, 24) which can be changed in volume by alternating to and from one another

15 rotate and the torque is taken from the rotary lobe shafts.

2. Internal combustion engines of the first series according to claim 1, characterized in that the two control disks synchronously in a ratio of 1: 2, in the Var. Turn the control disks 1: 4 to the crankshaft, which converts the reciprocating motion of the rotary pistons into a rotary motion by means of a lever and connecting rod.

20 because their outer contours are designed to be slidable on the inner wall of the housing cover and the bores in the control disks are identical in the radius of the cylinder axis to the collection and distribution channels of the housing cover, so that the working media can be exchanged between them, the bores ( 12, 14, 13, 15) and channels (26, 27) for the exchange of working media on only one side of the cylindrical housing

25 houses or on both sides, i.e. are arranged twice, the sealing of the working spaces in the area of the control disk and cylinder housing can be ensured by sealing rings (9) which are fixed in the cylinder housing by means of axial claws against rotation and are therefore axially displaceable, and in each case with the surface, with the rotary pistons and the control discs are slidable, the seal

30 of the distribution and collection channels can be ensured by circumferential sealing rings arranged in the housing cover, which are axially displaceable and either rotate synchronously with the control disks or are fixed in the housing cover against rotation.

3. Combustion engines of the second series, consisting of a cylindrical housing that can be closed on both sides, with holes for the installation of spark plugs and

Exchange of the working media as well as two rotary piston shafts rotatably mounted in one another in this housing, each with two, three or four symmetrically arranged lamellae, characterized in that in the housing (1) one, at the 1st Var. two holes for spark plugs (11) offset by approximately 180 ° are arranged in one

CHANGED BUTT (ARTICLE 19) of the end caps (28, 29) two holes (13, 15) arranged next to each other, in the 1st Var. There are two bores (13, 15) staggered by approx. 180 ° and on the rotary piston shafts (7a) and (8a), inside the housing, two each by approx. 180 °, for the 1st Var. four slats (7, 8) arranged offset by approx. eight wedge-shaped chambers (21, 22, 23, 24) which can be changed in their volume form by rotating in one direction at varying angular speeds and the torque of which is taken up by two crankshafts, which have a ratio of 2 : 1, at the 1st Var. in a ratio of 4: 1 to the rotation around the axis of the cylinder housing. 4. Combustion engines of the second series, Var. 2 according to claim 3, characterized ge indicates that in the housing (1) three by about 120 °, in the Var. 5 six bores for spark plugs (11) arranged offset by approximately 60 ° are, in one of the end caps (28, 29) each three by approximately 120 °, in the Var. 5 are each six bores (13, 15) offset by approximately 60 ° and on the rotary piston shafts (7a) and (8a), within the housing, two each by approximately 180 °, in the case of the Var. 5 are four slats (7, 8) arranged offset by approx. 90 °, which are dependent on one another, four, in the Var. 5 form eight wedge-shaped work spaces (21, 22, 23, 24) which can be changed in volume by rotating in one direction with changing angular velocity and taking their moment from two crankshafts, which are in a ratio of 6: 1, at the Var. 5 in a ratio of 12: 1 to the rotation around the axis of the cylinder housing.

5. Combustion engines of the second series, var. 3 according to claim 3 and 4, characterized in that in the housing (1) two by about 180 °, in the Var. 4 three bores for spark plugs (11), offset by approx. 120 °, are two in each of the end caps (28, 29) by approx. 180 ° for the Var. 4 three bores (13, 15) with non-return valves are arranged offset by approx. 120 ° and on the rotary piston shafts (7a) and (8a), within the housing, two each by approx. 180 °, at the Var. 4 are three slats (7, 8) arranged offset by approximately 120 °, which, depending on one another, are two in the case of the Var. 4 form three wedge-shaped work spaces that can be changed in volume by rotating in one direction at changing angular speeds and the torque of which is taken from two crankshafts, which vary in a ratio of 4: 1, with the Var. 4 in a ratio of 6: 1 to the rotation around the axis of the cylinder housing.

6. Internal combustion engines according to claims 3 to 5, characterized in that there is an additional spark plug at a corresponding distance from each spark plug, so that even before reaching the two crankshaft dead spots, the ignition is secured at a precise point, the spark plugs also in the lateral housing covers can be arranged, the bores (13, 15) for the supply and discharge of the working media can also be provided in both housing covers and in the cylindrical housing (1), one or more times, at the appropriate place.

7. Internal combustion engines according to claim 1 to 6, characterized in that the lamellae of one rotor part fit into the interstices of the other, being connected to one another by a connecting bolt (6), axially symmetrically and rotatably, or are set one inside the other in such a way that they drive each other and are designed to be slidable with the end faces of the lamellae on the two control disks or housing cover and on the inner surface of the housing (1), the lamellae also the one shown in FIG. 14 to FIG. 19 can have cross-sectional shapes as shown, instead of individual large bores, several smaller openings or slots for media exchange in the control disks (2, 4) and in the housing covers (28, 29) are arranged in a corresponding place power transmission from the two rotary piston shafts can also be absorbed by a crankshaft via a lever and a connecting rod. 8. Internal combustion engines according to claim 1 to 1, characterized in that with appropriate dimensioning of the engines, the combustion air supply can be supported by means of turbochargers, are located in the cylindrical housing (1), instead of the spark plugs, injection nozzles, which Allows use of diesel, gas or the like as fuel for injection. 9. Compressors or pumps, consisting of a lockable cylinder housing on both sides with holes for the exchange of working media and two rotatably mounted in this housing, nested rotary piston shafts, each with two, three or four symmetrically arranged fins, characterized in that they can be derived from the internal combustion engines characterized in claims 1 to the extent that instead of the holes for the spark plug (11), twice the number of holes (13, 15) are in the two control disks and the crankshaft in the opposite way as the drive used for the rotary lobe shafts can be derived from the internal combustion engines characterized in «Claims 3 to 8, so that instead of the bores for the spark plug (11) there are in the side housing covers (28, 29) or in the housing (1) there are twice the number of inlet and outlet openings for the exchange of working media n and the crankshaft rotating and self-rotating about the cylinder axis is used in the opposite way as a drive for the rotary piston shafts.

10. Internal combustion engines, compressors or pumps according to Claims 1 to 9, characterized in that the cylinder jacket (1) and its housing cover, the rotary pistons and the control disks are coated with a suitable ceramic material or can be produced from ceramic material, a housing cover and the cylinder jacket made from one part, or cylinder jacket and both housing covers can consist of two parts.