EP2292896A2 - Rotary piston combustion engine - Google Patents

Abstract

The rotary piston-internal combustion engine has four circular disks (1,2,3,4), which have a piston area of greater diameter and an intermediate area of smaller diameter. The former disk and third disk are connected to a shaft. The latter disk and fourth disk are connected to a working shaft (8) with their front surfaces turned away from each other. The third disk is rotated around an angle in the direction of the former shaft.

Description

The invention relates to a rotary piston internal combustion engine.

Rotary piston internal combustion engines are known in numerous designs. So revealed the DE 2 218 132 A1 a rotary piston internal combustion engine in which a plurality of individual units are assembled in tandem design. Each of the units consists of two circular rotary pistons mounted on parallel shafts, each of which is provided over a part of its circumference with a recess in the form of a circular ring section resulting from meshing engagement with a piston of one unit as the compression space and with the other piston of the same unit serves as an expansion or work space. In this case, each unit of two circular rotary pistons is enclosed by a housing that consists of two side walls and a jacket, which has the shape of two intersecting circles in the axial normal section. In order to provide a rotary engine with several units, for example with four cylinders, the individual housings of the individual units must be arranged side by side. Between the compression space of a unit and the expansion space of a second unit arranged next to this unit, a connecting line is provided in order to be able to move the fuel-air mixture generated and compressed in the one compression space via the connecting line into the expansion space of the adjacent unit. This design has the disadvantage that the connection of several units to a multi-cylinder rotary piston internal combustion engine in the axial direction takes up much space, so that a multi-cylinder rotary piston internal combustion engine builds relatively wide in the axial direction. Also, each case the housing of the individual units must be sealed, which means a considerable effort.

So revealed the US 4,236,496 A a rotary machine with separate piston discs which rub against partitions of separate chambers. This rotary machine dates back to Pappenheim's developments of 1636, Jones of 1848, the Root's Blower of 1866 and Behrens of 1867. There arise disadvantageously large sliding surfaces and a heavy load on the gears. Also, the local rotary machine has no connection channel with igniter, connection channel input and connecting channel output, wherein the latter open in the region of the lateral surfaces of the piston discs and are successively closed.

DE 36 27 962 A1 discloses a to US 4,236,496 A similar rotary machine in which there are intermediate plates between individual rotary lobes. This leads as in the rotary machine US 4,236,496 A To large sliding surfaces between rotary and intermediate plates, which leads to large losses in compression and performance. In addition, then results in a heavy load on the gears, and the construction is very complex and requires a lot of space.

DE 43 23 345 C2 discloses a rotary piston internal combustion engine with two substantially equal, round, mutually perpendicular discs which rotate about mutually perpendicular axes of rotation. This results in disadvantageously high axial forces.

The invention is therefore based on the object to provide a rotary piston internal combustion engine, which overcomes the disadvantages mentioned above and in particular allows a compact, powerful and easy-to-seal construction and energy-saving operation.

This object is achieved by the features of claim 1. Advantageous embodiments and preferred developments can be taken from the subclaims.

Fig. 1:

eine schematische Draufsicht auf ein erstes Ausführungsbeispiel einer Drehkolben-Brennkraftmaschine gemäß der Erfindung mit aufgeschnittenem Gehäuse von oben;

Fig. 2:

eine schematische Seitenansicht auf die Drehkolben-Brennkraftmaschine aus Fig. 1 entlang der Schnittlinie A-A;

Fig. 3:

eine schematische Seitenansicht auf die Drehkolben-Brennkraftmaschine aus Fig. 2 entlang der Schnittlinie B-B;

Fig. 4 a-f:

schematische Darstellungen unterschiedlicher Betriebszustände während eines Arbeitszyklus der Drehkolben-Brennkraftmaschine entsprechend der Ansicht in Fig. 2;

Fig. 5 a-c:

eine schematische Seitenansicht der Drehkolben-Brennkraftmaschine nach Fig. 2 für unterschiedliche Steuerwinkel;

Fig. 6:

eine schematische Schnittansicht einer erfindungsgemäßen Drehkolben- Brennkraftmaschine in axialer Richtung;

Fig. 7:

eine schematische Draufsicht auf die Drehkolben-Brennkraftmaschine aus Fig. 6 entlang der Schnittlinie C-C;

Fig. 8:

eine schematische Schnittansicht entsprechend Fig. 2 durch eine Weiterbildung der Drehkolben-Brennkraftmaschine des ersten Ausführungsbeispiels;

Fig. 9:

eine schematische Seitenansicht auf ein zweites Ausführungsbeispiel einer Drehkolben-Brennkraftmaschine gemäß der Erfindung mit

Fig. 10:

eine schematische Seitenansicht auf die Drehkolben-Brennkraftmaschine aus Fig. 9 entlang der Schnittlinie D-D.

Other features and advantages of the invention will become apparent from the following description of preferred embodiments with reference to the accompanying drawings. These show:

Fig. 1:

a schematic plan view of a first embodiment of a rotary piston internal combustion engine according to the invention with cut housing from above;

Fig. 2:

a schematic side view of the rotary piston engine Fig. 1 along the section line AA;

3:

a schematic side view of the rotary piston engine Fig. 2 along the section line BB;

Fig. 4 af:

schematic representations of different operating conditions during a working cycle of the rotary piston internal combustion engine according to the view in Fig. 2 ;

Fig. 5 ac:

a schematic side view of the rotary piston internal combustion engine according to Fig. 2 for different control angles;

Fig. 6:

a schematic sectional view of a rotary piston internal combustion engine according to the invention in the axial direction;

Fig. 7:

a schematic plan view of the rotary piston engine from Fig. 6 along the section line CC;

Fig. 8:

a schematic sectional view corresponding Fig. 2 by a development of the rotary piston internal combustion engine of the first embodiment;

Fig. 9:

a schematic side view of a second embodiment of a rotary piston internal combustion engine according to the invention with

Fig. 10:

a schematic side view of the rotary piston engine Fig. 9 along the section line DD.

An in Fig. 1 to 3 schematically illustrated rotary piston internal combustion engine has as essential components six substantially identical slices 1 to 6. The discs 1 and 5 are also referred to as intake-side outer discs, while the discs 2 and 6 are also referred to as output-side outer discs. The discs 3 and 4 are also referred to as middle, inlet or driven side discs. The disks 1 to 6 basically consist of circular disks, which have a piston region of larger diameter and an intermediate region of smaller diameter, as seen from Fig. 2 evident. The two areas each occupy about half of the slices 1 to 6.

The discs 1, 3 and 5 are mounted on a shaft 7, while the discs 2, 4 and 6 are arranged on an output shaft 8. Both shafts 7, 8 rotate in opposite directions in the motor operation in the Fig. 2 shown directions, the shaft 7 thus counterclockwise and the output shaft 8 in a clockwise direction. In order to ensure a synchronous running of the shafts 7, 8, they have in Fig. 1 to 3 not shown, intermeshing gears, which ensure a coupling in the rotation ratio 1: 1.

As in particular from Fig. 1 As can be seen, the discs 1 and 2, 3 and 4 and 5 and 6 respectively form mutually associated pairs of discs. The intermediate regions and piston regions of the associated pairs of disks are arranged on the shaft 7 and the output shaft 8 so that they engage with each other in meshing engagement. On the basis of in Fig. 2 completely visible inner discs 3 and 4 is easily seen that during approximately half an opposite rotation of the two discs 3 and 4, the inner periphery of the intermediate portion of the inlet side disc 3 on the outer circumference of the piston portion of the driven-side disc 4 rolls (in Fig. 1-3 and 4a, b and f shown). On the other hand, during the other half counter rotation, the inner circumference of the intermediate portion of the driven side pulley 4 rolls on the outer periphery of the piston portion of the intake side pulley 3 (in FIG Fig. 4 ce shown).

This in Fig. 2 behind the disc pair 3, 4 lying outer disc pair 1, 2 as well as in Fig. 2 not visible disc pair 5, 6 are arranged opposite the disc pair 3, 4 by a control angle α on the shaft 7 and 8 twisted. As will be described later, this twist angle can be changed to set the compression.

The disks 1 to 6 are surrounded by a housing 9, which consists essentially of two interconnected on their longitudinal sides sub-cylinders. In the in Fig. 2 left, designated as a compression cylinder 10 part cylinder is above a reaching over all discs 1, 3, 5 inlet opening 11 for a fuel-air mixture. In the in Fig. 2 right, as the expansion cylinder 12 designated partial cylinder is located below a only in the region of the outer discs 2, 6 extending outlet 13 for the combusted fuel-air mixture, in the region of the middle disc 4 runs this sealingly on the expansion cylinder 12 from.

The peripheral sides and side flanks of the disks 1-6 sealingly abut the walls of the compression and expansion cylinders 10, 12 and the peripheral sides or side flanks of the adjacent disks 1-6, respectively. The fuel-air mixture located in the compression cylinder 10 can thus pass from the compression cylinder 10 into the expansion cylinder 12 only via a connecting channel 14. As in particular from Fig. 3 As can be seen, there are connection channel entrances 15 at the bottom on the front-side outer sides of the compression cylinder 10, while a connecting channel exit 16 in the circulation area of the expansion-side central disc 4 extends into the expansion cylinder 12. The connection channel inputs 15 are also denoted by RLO, the connection channel output 16 also by VKA.

In order to ignite the fuel-air mixture, which is compressed in the compression cylinder 10 and the connecting channel 14, 14 spark plugs 17 and in the region of the connecting channel output 16, a spark plug 18 are provided in the region of the connecting channel inputs.

The operation of the rotary piston internal combustion engine according to the invention will now be based on a duty cycle in 4 a) to f) and the table attached at the end of the description.

Fig. 4 a) shows the position of the discs 1-4 at the beginning of a cycle. The inlet opening 11 is closed in the region of the discs 1 and 5, while it is open in the region of the central inlet-side disc 4 for the intake of fuel-air mixture.

In the lower region of the compression cylinder 10, the connection channel inputs 15 are opened, while the connection channel outlet 16 is closed by the expansion-side central disc 4. Thus, in the lower region of the compression cylinder 10 befindliches fuel-air mixture is compressed by all three discs 1, 3 and 5 in the intermediate region and in the connecting channel.

In the expansion cylinder 12, the expansion phase ends in the region of the outer disks 2 and 6, which still close the outlet 13. The burned exhaust gases in the area of Intermediate portion of the central disc 4 are slidably displaced in the direction of the outlet 13 and thus throttled to the outlet 13.

Subsequently, from the state in Fig. 4 a) starting initially in the area of the middle disc 3 of the compression cylinder 10 sucked up the top fuel-air mixture, which then successively slices 1, 5 of the compression cylinder 10 open with their intermediate regions to the inlet opening 11. As a result, fuel-air mixture is increasingly sucked into the vacant space between the compression cylinder 10, the disk circumferences of the discs 1, 3, 5 and 2, 4, 6.

In the lower region of the compression cylinder 10, the fuel-air mixture between the compression cylinder 10, the disk circumferences of the discs 1, 3, 5 and 2, 4, 6 is further compressed, the connecting channel exit 16 still through the central disc 4 of the expansion cylinder 12th is closed.

Meanwhile, in the expansion cylinder 12, the outlet 13 through the windows 2 and 6 increase open, the exhaust gases in the region of the discs 2, 4 6 are throttled out to the outlet 13 and discharged there.

In Fig. 4b) is still sucked in the area of the discs 1, 3, 5 above, while in the region of the middle disc 3 below the compression is completed. The compression in the region of the outer panes 1, 5 below, however, continues, wherein the fuel-air mixture located there is subsequently pushed further into the connecting channel 14. In the expansion cylinder 12, exhaust gas is still expelled from the region of the middle disk 4, as well as from the areas of the outer disk 2 and 6.

This process will be after Fig. 4b) at still open connection channel inputs 15 and closed connection channel output 16 continues until the in Fig. 4c) shown state is reached. In the upper region of the compression cylinder 10, fuel-air mixture is sucked through the inlet opening 11 in the region of all three disks 1, 3 and 5.

The connection channel inputs 15 are - starting with Fig. 4c) - Then closed by the outer discs 1 and 5, so that the compression process by the Slices 1 and 5 is completed. At the same time the connecting channel output 16 is released in the expansion cylinder 12 through the middle disc 4, so that the compressed fuel-air mixture can get into the expansion cylinder 12. Subsequently, the still in the connecting channel 14 located compressed fuel-air mixture is ignited by the spark plugs 17 and 18, so initially only a combustion takes place in the region of the connecting channel 14 and the intermediate region of the middle disc 4 and thus only this is driven.

Starting from Fig. 4c) As before, exhaust gases in the region of the disk 4 as well as in the region of the disks 2 and 6 are expelled through the outlet opening 13. The suction process in the region of the middle disc 3 is terminated at the moment in which the front in the direction of rotation edge of the piston portion of the disc 3 sweeps over the inlet 11. In the area of the outer panes 1 and 5, fuel-air mixture continues to be drawn in as before. Compression no longer takes place in the compression cylinder 10.

With reaching the in Fig. 4 d) shown position, the suction in the region of the middle disc 3 is completed, wherein the located in the region of the disc 3 fuel-air mixture is moved downward. Likewise, further in the area of the discs 1 and 5, fuel-air mixture is sucked. At this time, the areas of the disks 2 and 6 are then completely opened to the connection channel exit 16, so that in the areas of the disks 2, 4 and 6 fuel-air mixture is burned and expansion takes place. The disc 2 and 6 thus also serve as Nachbrennkammern. The discharge in the region of the middle disc 4 is completely finished, while the exhaust gases in the region of the discs 2 and 6 are further ejected.

Subsequently, then at the in Fig. 4 e) shown position, the intake of the fuel-air mixture in the compression cylinder 10 is completed completely by closing the inlet 11 by means of the outer discs 1 and 5. The connection channel inputs 15 are still closed, while the connection channel output 16 is still open. Similarly, the exhaust gases in the expansion cylinder 12 below in the area of the discs 2 and 6 further expelled until the in Fig. 4 f) shown position is reached. Then, the outlet 13 is closed by the outer discs 2, 6. In the upper region of the expansion cylinder 12, combustion and expansion continue to take place in the region of the disks 2, 4, 6.

With the end of the suction of the fuel-air mixture in the compression cylinder 10 in Fig. 4 e) begins now in the compression cylinder 10 of the compression process of the located in the lower region of the compression cylinder 10 fuel-air mixture with still closed connection channel inputs 15 and is up to in Fig. 4 f) shown position continued.

Then begins in Fig. 4 f) the suction in the region of the middle disc 3 above. Through the leading edge of the middle disc 4 of the connecting channel output 16 is closed. Only then are then released by removing the direction of rotation in the rear end of the piston portion of the outer disks 1, 5, the connection channel inputs 15 so that the compressed fuel-air mixture can be introduced into the connecting channel 14. In the in Fig. 4 f) shown state is then also the expulsion of the exhaust gases into the outlet 13 finished when the leading in the direction of rotation edges of the outer discs 2, 6, the in Fig. 4 f) have reached shown position.

This completes a work cycle and starts a new work cycle.

The control of the rotary piston internal combustion engine can take place, inter alia, by controlling the fuel supply, controlling the ignition timing and controlling the compression.

In Fig. 5 a) to 5 c) It is shown how a different compression can be set by a different control angle α at the ignition time. The adjustable firing angle α is achieved in that the middle disc pair 3, 4 is rotated relative to the outer disc pairs 1.5 and 2, 6. So is in Fig. 5 a) shown a small ignition angle α, in which the fuel is less compressed than, for example, in Fig. 5 b) or Fig. 5 c) , In the Fig. 5 a) shown position is suitable for light fuels such as alcohol, gases, etc. For medium heavy fuels, such as low octane gasoline, the control angle α is after Fig. 5b) suitable for heavy fuels such as high octane gasoline in Fig. 5c) suitable control angle α makes sense.

The setting of the ignition angle α based on the angular adjustment of the middle discs 3, 4 will now be based on 6 and 7 explained. As far as there are the same elements as in Fig. 1 to 5 are shown again, the same designations and reference numerals are used.

In Fig. 6 only the structure of the expansion cylinder 12 is shown, the compression cylinder is formed accordingly. To the in Fig. 6 left end face of the expansion cylinder 12, a control block 19 is mounted. The output shaft 8 extends through both the expansion cylinder 12 and the control block 19 and is there rotatably mounted respectively via ball bearings 20, 21.

In the control block 19, a gear 22 is fixedly connected to the output shaft 8, wherein the gear 22 engages in a corresponding gear on the shaft 7 and thus ensures the synchronous running of the shafts 7, 8. The gear 22 can be connected via screw 23 fixed to a second, equally trained gear 24. The second gear 24 is fixedly connected to a control sleeve 25.

The control sleeve 25 has the in Fig. 6 shown cross section and is rotatably mounted relative to the output shaft 8 by means of ball bearings 26, 27 on the expansion cylinder 12 and its housing mounted. On the control sleeve 25 in turn, the outer disc 2 and 6 are fixed. In this case, the control sleeve 25 in the region of the disc 2, a hollow cylindrical recess 28 into which a mounted on the output shaft 8 corresponding annular control disk 29 extends. From the control disk 29 rich control bolt 30 in Fig. 7 recognizable bean-shaped, elongated openings 31 in the one side wall of the hollow cylindrical recess 28 of the control sleeve 25. The control pin 30 extend into corresponding holes in the middle disc 4th

If the gears 22, 24 are not connected to one another via the connecting screws 23, the output shaft 8 can be rotated relative to the control sleeve 25 by the control angle α, which is limited by the length of the openings 31. To adjust the control angle α, only the connection between the gears 22 and 24 has to be released, then the control angle α has to be set, and then the gears 22 and 24 have to be firmly connected again. For this purpose, distributed over the circumference of the gear 24 numerous threaded holes can be arranged, in which the connecting screws 23 of the gear 22 can be used differently. Thus, the control angle α between the middle pair of disks 3,4 and the outer disk pairs 1, 2 and 5, 6 can be changed in a fast manner.

Instead of the gear 24 and the corresponding gear on the shaft 7, these gears can also be replaced by discs which are not related to each other. The synchronization of the shafts 7, 8 then takes place via the gear 22 and the meshing with this gear on the shaft. 7

Alternative adjustment options of the control angle exist, for example, instead of the fixed connection between the two gears 22 and 24 after Fig. 7 an externally controllable angle adjustment of the pairs of discs 1,2, 5,6 and 3,4 is made possible. This could be done for example hydraulically, electromagnetically or with centrifugal force control.

In order to increase the power of the engine even further, in a further development of the invention Fig. 8 an additional inlet 32 may be provided in the expansion area of the expansion cylinder 12, through which a certain amount of water can be introduced into the expansion area. By the combustion of the fuel-air mixture in the expansion cylinder 12, the sprayed water is evaporated, whereby the expansion and the expansion pressure in the expansion cylinder 12 are further enhanced (boost effect).

In FIGS. 9 and 10 an alternative embodiment of the rotary piston internal combustion engine is shown. This is different from the one in Fig. 1 to 7 shown embodiment in that instead of three pairs of discs 1,2, 3,4 and 5,6 only two pairs of discs 1,2 and 3,4 are used, the pair of discs 5, 6 from Fig. 1 was omitted. Otherwise, the structure and functioning of the in FIGS. 9 and 10 shown rotary piston internal combustion engine of the rotary piston internal combustion engine with three disc pairs in Fig. 1 to 7 , Compared to the basically functional design with two pairs of discs 1,2 and 3,4, the embodiment with three disc pairs 1,2, 3,4 and 5,6 has the advantage that the symmetrical design with two outer disc pairs 2, 1 and 5 , 6 an asymmetrical load distribution as in the embodiment in FIGS. 9 and 10 is avoided. Thus, in the execution after FIGS. 9 and 10 arising pulsating axial forces, which lead to significantly higher friction of the side surfaces of the discs to each other and the housing can be avoided.

The rotary piston internal combustion engine is preferably made of refractory materials, such as ceramics. In particular, this applies to the discs 1-6 and the inner walls of the compression and expansion cylinders 10, 12. When using such refractory materials very high temperatures in the expansion space can be achieved, the rotary piston internal combustion engine then can operate largely without additional cooling in operation. Alternatively or in combination, however, conventional materials used in engine construction can also be used.

Advantages of the rotary piston internal combustion engine according to the invention are that the expansion forces generated are completely transferred to the working shaft 8. In addition, the rotary piston internal combustion engine according to the invention runs wear-free, lubrication is not necessary, eliminating all the problems associated with the oil supply, oil pressure and oil temperature control in conventional engines. In addition, the rotary piston internal combustion engine according to the invention has no valves, camshafts, toothed belts, toothed chains, pulleys, oil sump or partitions. In addition, the largest torque is generated at the ignition. The ignition of the spark plugs 17, 18 at the connection channel input 15 or connection channel output 16 can also be controlled differently in order, for example, to achieve direction-controlled combustion from the connection channel inputs 15 to the connection channel output 16.

reference numeral

1

outer disc (inlet side)

2

outer disc (driven side)

3

inner disc (inlet side)

4

inner disc (driven side)

5

outer disc (inlet side)

6

outer disc (driven side)

7

wave

8th

output shaft

9

casing

10

compression cylinder

11

inlet

12

expansion cylinder

13

outlet

14

Connection channel (VK)

15

Connection channel input (RLO)

16

Connection channel output (VKA)

17

Spark plugs RKE

18

Spark plug VKA

19

control block

20

Ball bearing output shaft

21

Ball bearing output shaft

22

Gear shaft side

23

connecting bolts

24

Gear sleeve side

25

control sleeve

26

Ball bearing control sleeve

27

Ball bearing control sleeve

28

hollow cylindrical recess

29

control disc

30

control bolt

31

bean-shaped, elongated openings

32

Boost input

Left chamber (suction compression) connecting channel Right chamber (expansion output) Figure 4 description
Suction - compression Suck up Comp below RV below VKA above Expansion above Output below description
Expansion - output FIG. 4 1 3 5 1 3 5 1-4 5-4 1-4 5-4 2 4 6 2 4 6 a) Suction disc 3 top feed to discs 1, 5 closed compression discs 1, 3, 5 bottom X X X X X X On To X X X End of expansion 2, 6
Exhaust gas disc 4 Displacement of the exhaust gases
sliding to the exit (throttled) a) ↓ Suction disc 3 top opening feed discs 1, 5 top compression discs 1, 3, 5 bottom X X X X On To X X X Disc 4 exhaust gases forwarded.to the exit.
Slice 2; 6 exhaust gases throttled to the exit ↓ b) Suction disc 1,3,5 at the top end compression disc 3 below compression discs1, 5 below + displacement X X X X X On To X X X Emission of exhaust gas disc 4
Slices 2-6 (throttled) b) ↓ End of compaction disc 3 below compression discs1, 5 below X X X X X On To X X X Emission of exhaust gas disc 4
Slices 2-6 (throttled) ↓ c) Aspirate disc 1, 3, 5 End of compression disc 1, 5 below X X X To On X X X X Start of the expansion disk 4 c) ↓ End suction disc 3 above. Aspirate disc 1.5 above. End compression disc 1; 5 below. In the connection channel VKE 1-4; 5-4 X X X X To On X X X X X X Ejection of the exhaust gas disk 4 thereafter ejection of the exhaust gases 2; 6 (throttled) if necessary injection of H2O into expansion cylinder. ↓ d) End suction, disc 3 medium is moved down, and end of the suction disc 1, 5 X X To On X X X X X X Emission of the exhaust gas disc 4, 2.6
Expansion 4, 2, 6 Above
Afterburning slices 2,6 d) ↓ Suction disk 1, 5 above. X X To On X X X X X X Emission of the exhaust gas disks 2, 6
Expansion 4, and 2; 6 ↓ e) End suction disc 1.5 compression discs 1, 3 and 5 X X X To On X X X X X Exhaust emissions Disc 2, 6
Output disc 4 end e) ↓ Aspirate disc 3 above X X To On X X X X X Expansion disc 2, 6 ↓ f) Aspirate disc 3 above Compression 1, 3, 5 X X X X To To X X X X Close VKA through disc 4
End exhaust of the exhaust disc 2, 6 f)

Claims (11)

Rotary piston internal combustion engine having at least four substantially identically formed round discs (1, 2, 3, 4), each having a piston region of larger diameter and an intermediate region of smaller diameter, wherein on a first shaft (7) a first disc (1) and a third disc (3) twisted by a control angle (α) in the direction of rotation of the first shaft (1) and a second disc (2) on an output shaft (8) parallel thereto and a control disc (α) in the direction of rotation Output shaft (8) twisted fourth disc (4) abutting each other with their end faces sealingly against each other, the first shaft (7) and the output shaft (8) are coupled for synchronized counter-rotation with each other, wherein the first disc (1) of the second disc (2 ) or the third disc (3) of the fourth disc (4) and are arranged on the first shaft (7) and the output shaft (8), that in each case the lateral surface of the piston area the one disc (1, 3) during one part of the opposite rotation of the discs on the lateral surface of the intermediate portion of their respective associated disc (2, 4) rolls sealingly and during the other part of the revolution, the lateral surface of the intermediate portion of a disc (1, 3) on the lateral surface of the piston portion of the associated other disc (2, 4) sealingly rolls, wherein the first disc (1) and third disc (1) of the first shaft (7) sealingly from a compression cylinder (10) and the second disc (2) and fourth disc (4) of the output shaft (8) are sealingly surrounded by an expansion cylinder (12), the compression cylinder (10) and the expansion cylinder (12) are interconnected at a mutually facing longitudinal transition opening in which the associated Rolling discs (1,2,3,4) on each other, wherein on the longitudinal side of the compression cylinder (10) has an inlet (11) for a fuel-air mixture and on an end face of the compression cylinder (10) lying in the direction of rotation of the first shaft (7) behind the inlet (11) is a connection channel inlet (15) which is not covered by the intermediate area of the first disc (1) and is defined by the piston area of the first disc (1 ) Is closed, wherein the inlet (11) by the lateral surfaces of the piston areas of the first disc (1) and third disc (3) can be closed successively, wherein from the connection channel entrance (15) a connecting channel (14) to a connection channel exit (16) opening in the area of the lateral surface of the fourth disc (4) in the expansion cylinder (12), wherein the connecting channel exit (16) in the direction of rotation of the output shaft (8) in front of an opening in the region of the second disc (2) outlet (13) of the expansion cylinder (12), wherein the outlet (13) through the lateral surface of the Piston portion of the second disc (2) is closable, and wherein in the connecting channel (14) at least one ignition device (17, 18) for igniting in the connecting channel (14) located fuel-air mixture is provided. Rotary piston internal combustion engine according to claim 1, characterized in that on the first disc (1) and second disc (2) facing away from the third disc (3) and fourth disc (4) a fifth disc (5) or sixth disc ( 6) on the first shaft (7) and the output shaft (8) is arranged, which in the same manner as the first disc (1) and second disc (2) on the shafts (7, 8) are arranged, wherein the fifth disc (5) facing the end face of the compression cylinder (10) is another to the connecting channel (14) associated connection channel input (15) which is not covered by the intermediate portion of the fifth disc (5) and by the piston portion of the fifth disc (5) is closable. Rotary piston internal combustion engine according to claim 2, characterized in that the inlet (11) by the lateral surfaces of the piston portions of the first disc (1), third disc (3) and fifth disc (5) is successively closed. Rotary piston internal combustion engine according to claim 3 or 4, characterized in that the outlet (13) by the lateral surface of the piston portion of the sixth disc (6) is closable. Rotary piston internal combustion engine according to one of the preceding claims, characterized in that the control angle (α) between the third disc (3) or fourth disc (4) and the other discs (1,5, 2, 6) of the first shaft (7) and the output shaft (8) is jointly adjustable. Rotary piston internal combustion engine according to one of the preceding claims, characterized in that the inlet (11) in the direction of rotation of the first shaft (7) behind the points of contact of the rolling discs (1,2; 3, 4; 5, 6) adjacent to the transition opening , Rotary piston internal combustion engine according to one of the preceding claims, characterized in that the one or more connection channel inputs (15) in the direction of rotation of the first shaft (7) in front of the points of contact of the rolling discs (1,2; 3, 4; 5, 6) adjacent to Transition opening is located. Rotary piston internal combustion engine according to one of the preceding claims, characterized in that the connecting channel output (16) in the direction of rotation of the output shaft (8) behind the points of contact of the rolling discs (1,2; 3, 4; 5, 6) adjacent to the transition opening. Rotary piston internal combustion engine according to one of the preceding claims, characterized in that the outlet (11) in the direction of rotation of the output shaft (8) before the points of contact of the rolling discs (1,2; 3, 4; 5, 6) adjacent to the transition opening. Rotary piston internal combustion engine according to one of the preceding claims, characterized in that the discs (1-6) are made of a heat-resistant material, in particular a ceramic material. Rotary piston internal combustion engine according to one of the preceding claims, characterized in that in an expansion cylinder (12) in the direction of rotation of the output shaft (8) behind the connecting channel outlet (16) and in front of the outlet (13) lying area an additional boost inlet (32) for introducing water into the expansion cylinder (12) is provided.

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