WO2010089030A2

WO2010089030A2 - Rotary piston internal combustion engine

Info

Publication number: WO2010089030A2
Application number: PCT/EP2010/000358
Authority: WO
Inventors: Helmut Porod
Original assignee: Helmut Porod
Priority date: 2009-02-04
Filing date: 2010-01-22
Publication date: 2010-08-12
Also published as: DE102009008205B4; EP2394023B1; DE102009008205A9; EP2394023A2; WO2010089030A3; DE102009008205A1

Abstract

1.1 Previously unsolved problems for an internal combustion engine having two piston pairs rotating about a central axis are the effective sealing of the chambers from each other, and engine control. The aim of the invention is to solve said problems and additionally provide for efficient lubrication and cooling of the engine. 2.2 The invention relates to two piston pairs Fig. 1.1, each on a piston disc (5), (6) form a recurring working position in an top and a bottom dead center position (UT, OT). Chambers (26 – 29) are formed by means of two pintles (48) at the end faces of the piston and having perpendicular and trapezoidal sealing elements, together with piston rings in the piston disc within a ring-shaped cylinder. The sealing elements of a piston are pressed against the sealing rings of the piston disc and the inner surface of the ring-shaped cylinder by at least one wave spring (175). While a piston pair remains still during sensor-controlled ignition of the fuel-air mixture, the second piston pair is rotated further, together with the working shaft, by a crank angle of 90°/60°/36°, and all working cycles of a four-stroke engine are performed. After another 135°/120°/108°, a new work cycle occurs. The starting process of the engine can be performed by sensors without contact, both by two external, conventional starters, using segments of a circle, and by two internal electronically commutated motors having magnetic discs and controls electronics. By solving said problems, said engine can not only be used universally as a stand-alone, but also as a hybrid engine and hybrid and generator drive. Further advantages result from the fact that the compression can be controlled by means of the pressure limit valve (52).

Description

Rotary piston internal combustion engine

The invention relates to a combustion engine with internal combustion as it is known in relation to the Otto and Diesel working method. Notwithstanding the hitherto known by the construction and working principle stroke, - rotary and rotary engines, the application describes a compact rotary piston internal combustion engine (RKB) according to the preamble of claim 1, whose Arbeitsprihzip is characterized in that for a rectified rotational movement during the starting process and in all operating conditions, two piston pairs in the recurring working position of a top and bottom dead center (QTfUT), directly opposite each other, by pegs form four chambers, and that with piston ring segments, rectangular and trapezoidal sealing elements, a 90 ° crossing, closed sealing limit to annular cylinder, is formed to the chambers and the piston discs and that by sensors both the RKB with external conventional starter, and the two internal, by means of magnetic disk and Hall sensor or position encoder electronically commutated, starters, generators, or motors in Außenpol- construction (EC Motor = ECM), are controlled and controlled without contact in all operating states.

3.1 State of the art

For many years, inter alia, pan, double-wing or rotary piston internal combustion engines are known, for the most part the power transmission from the piston to the working shaft by mechanical engines such as gear and planetary gear, crank mechanisms, and the control of work cycles by eccentric shafts, sliding blocks, control cam linkages and Pawls over- to take. It is also known that one or more piston pairs in an annular cylinder form variable spaces by a controlled mechanism. None of the above-mentioned engine systems known hitherto have been technically or commercially implemented. This is due not only to the usually very complex constructed mechanical power transmission and control systems, but in particular by a lack of thermal and high pressure gas tightness at the sealing boundary between the chambers of the rotating piston, the piston discs and the inner wall of the annular cylinder.

A working and internal combustion engine (DE-OS 1426022, 1969) is equipped with at least two in a cylinder, about a common axis rotating double-piston piston, which include located between their wings working chambers and connected via a control gear such that the one Wing piston, except its common orbital motion with the other wing piston, compared to the latter still performs an additional, the working chambers periodically increasing and decreasing relative movement. With the control gear relative to the planetary pinion eccentric of the eccentric drive is adjustable so that not only increases the degree of compression, but also an increase in the working chamber volume is achieved.

An internal combustion engine (DE-A 1965865 A, 1971) is described in one exemplary embodiment such that a ring cylinder with housing and toothed wheel are stationary. Shaft and flywheel are connected. Four double pistons as piston pair are rigidly connected to the associated piston disc. The circular motion of the pistons is generated by the shaft via the fixed gear, the planetary gear and an eccentric shaft, which are connected via sliding blocks with the piston disc, so that cylindrical spaces periodically increase and decrease. The gear ratio of the planet gears to the fixed gear is 2: 1. Based on the speed of the eccentric shaft, the design corresponds to a four-stroke eight-cylinder piston engine.

An arc-piston internal combustion engine (DE-OS 2353807 A1, 1975) is characterized in that in each case two arc pistons located opposite each other in a ring cavity of the housing are connected to two pairs of curved pistons by two piston levers which are anchored on a pendulum shaft in a crosswise arrangement, which are twisted by turning the two piston levers form mutually four volume-changing combustion chambers in the annular cavity, each of which is delimited by two piston pistons. The control of the gas exchange in the four combustion chambers is performed by rotating a slotted, on a central intake, the funnel-shaped design of the housing and sealed sealing against the funnel-shaped surface control cone.

In a known rotary internal combustion engine (DE-OS 3046725 Al, 1982) two diametrically opposed pistons are attached to two adjoining disc-shaped support means in a ring cylinder. A number of outlets and inlets are arranged on the circumference of the annular cylinder, so that diametrically opposite combustion, suction, compression and ejection chambers are formed at any one time, the position of which displaces along the annular cylinder during the movement of the piston pairs. The respective trailing piston is mechanically locked at the end of the compression process by means of a ratchet wheel assembly against a backward movement, wherein a relative movement is superimposed in the piston rotation direction, so that volume-variable chambers are formed during the rotation of the piston system. Between the piston systems, separate transmission means are provided for connecting the piston systems to the working shaft. A likewise known internal combustion engine (DE-OS 3038500 Al, 1982) with circular orbit of the piston pairs is divided into several zones and receives in each zone a working impulse after the four-stroke cycle. In each zone runs a pair of pistons, a piston of which is designed as a working piston and transmits the working pressure to the main shaft via a lever. An opposed piston is equipped with a pawl and pressure spring, which takes over the support between working and counter-piston in a catch during the firing process. The exhaust and intake valves are actuated by a control linkage and internally toothed gears by control cams.

A known internal combustion engine (DE-OS 3330125 Al, 1985) operates in a two- and four-stroke process with a rotary piston. This rotary piston in a hollow cylinder with one or more fixed separation segments and with one or more piston segments on the shaft, which is mounted in the cylinder bottoms is offset by combustion pressure in a reciprocating motion. The pendulum motion is thereby implemented via gears and freewheels in continuous motion.

In an oscillating piston engine (Oscillating Piston Engine) (US Pat. No. 5,222,463, 1993), eight curved pistons move in an annular combustion chamber (toroid). Each four pistons are mounted on a separate central disc. The two discs are in turn connected to one of two drive shafts, which are guided coaxially outwards. The two discs, with their four pistons each, oscillate in the four-stroke process, so that two pistons each form a pair between which the four bars in the rotating toroid play. The opposite movement of the drive shafts is converted by a crank mechanism into a rotary motion. The piston end faces have a shape corresponding to a flat cone, which keep a compression space in the four chambers, when the pistons are directly opposite each other during the working cycle. Each piston is with equipped with several piston rings to ensure a seal to all annularly moving components.

3.2 Task

The invention has for its object to present a functional, economical and technically feasible engine concept in a compact design with low production costs and new working principle, which not only improved overall efficiency compared to the now built-in motor vehicle reciprocating engine, but also a much simplified sensitive Control and regulation, which includes rotating in an annular cylinder piston pairs. In addition, a closed sealing boundary on the piston and the housing wall, with the 90 ° crossing piston disc to be represented. Another object of the present invention is to provide a high torque, long life, low speed engine that meets today's fuel and energy saving needs as well as low polluting exhaust emissions (eg, CO ₂ emissions), including hydrogen powered or other alternative fuels (Natural gas, biofuels, etc.) can meet. Another object is to provide with little effort a safe, effective and easy cooling of the engine and an integrated between the piston discs oil pump function for a pressure circulation lubrication.

3.3 working principle

The sensor-controlled RKB 50, 60 to be described in this invention with two conventional external starters or with two internal ECM 45, which are contactlessly switchable, controllable and controllable as a starter, generator and as a hybrid drive, magnetic disk and Hall sensor or position sensor, includes the particular two advantageous concept in an annular housing a common axis rotating piston discs, each with two symmetrically arranged pistons as piston pairs (Kp) directly in an upper and lower dead center (OTAJT) face each other a recurring working position for the alternately rectified rotational movement, without restriction by gear or crank gear, taking. With the design of two pins on the end faces of the piston, in the TDC an intake and in the UT a working chamber (Vc) and on the piston rear side of the Kp a compression (Vh) and expansion chamber is formed. The sum of the angular degrees of two pistons with pin and piston stroke is always 180 ° crank angle (Kw). By the expansion force of the compressed and ignited fuel-air mixture between two pistons in the working chamber alternately a Kp, supported by a backstop in the housing, stand and at a selected piston length of 45 ° / 60 ° / 72 ° Kw and the rotational movement from 90 ° / 60 ° / 36 ° Kw are carried out simultaneously with the second Kp, in four chambers, the working cycles of a four-stroke engine and a working shaft (Aw) with flywheel, gear wheel control disc or the rotor with permanent magnets and magnetic disc of the internal ECM, rotated by an oppositely acting backstop.

By thermal pressure and kinetic energy then the piston pairs are further rotated together and directly opposite by 45 ° / 60 ° / 72 ° Kw and after 135 ° / 120 ° / 108 ° Kw a new power stroke (At) started. The pairs of pistons rotate in the ratio 2: 3 / 2,25: 3 / 2,5: 3 to the working shaft without gearbox, producing 8/9/10 At (see Table 1, speed Kp selected with n = 1000 U) / min). Table 1

50 80 130 2.77 1444 I 0.69 8.31, 08: 3

55 70 125 Z O. o OoO! 1389 0.72 8.64 2,16: 3

3.13 1278 0.78 9.39

3.27 1222 0.82 9.82

75 30 105 3.43 1167 0.86 10.29, 57: 3

Within a constant 180 ° Kw comprehensive circle segment in the cylinder of the housing 17, 18, 19, the compression and stroke ratio by the variable length of the pin 48 and / or the piston angle or piston length 1 - 4 and its diameter is determined. In the compression chamber 27, two openings 30 are provided, which are connected to a compressed air line 32 and an electrically controllable valve 52 which can compensate for the compression pressure from the compression to the suction chamber when a piston is located between the two openings. With the help of this valve, the required starter torque and the engine power (eg with a rotary potentiometer on the gas pedal or other actuators), via the variable compression Vc can be controlled. In the expansion chamber is another opening 31 which is closed with a check valve 54 and the chamber 29 opens at low pressure to facilitate the starting process. In the further course of the engine control of the following operating conditions is described:

• Start engine and ignition • Engine control at idle

• Motor control in partial and full load range

3.4 Start engine and ignition process

When the engine is first started with an ignition switch 138, there is still no ignitable mixture in the suction chamber. The piston pairs are rotated out of each mutually random position, with one or both external starters or with the starter function of the internal ECM in the working position of the OTVUT and the Kp b sensor-controlled by a reciprocal locking device or by a Polwendeschalter for Alternate reversal of the direction of rotation of the external conventional starter, or with the starter of the internal ECM by a control electronics via Hall sensor or position sensor, against a backstop (freewheel) stopped in the housing. With the Kp a starter, four work cycles (sucking, compressing, expanding, pushing out) are carried out and a spark is activated for the At.

This is inventively in the locking device possible in that on each side of the housing in the TDC inductive sensors (or a sensor with the same functionality) via two inner circular segments, which are in communication with the piston pairs, four non-contact solenoids 98, 99 Fig. 4 and control two outer circular segments two external conventional starters 139, 140 so that in the direction of rotation of the working shaft Kp a through b and vice versa, two stops on a damper disc with damper spring when reaching the TDC or by changing the direction of rotation with a Polwendeschalter Fig 4.1. is held in the housing 17, 18 as long as until the Kp a or b touch the pin 48. The thereby compressed fuel-air mixture is then further rotated with both piston pairs 45 ° / 60 ° / 72 ° Kw by the starter of Kp a to the UT. If no ignition of the fuel-air mixture, the Kp b is rotated by the starter of Kp b again 90 ° / 60 ° / 36 ° Kw. During the starting process via an internal ECM integrated on the left and right of the motor housing, the alternating direction of rotation is switched by a magnetic disk 112 and with the aid of Hall sensor or position sensor 113 and control electronics, and the O position of the OT / UT is detected. This process is repeated until the ignition start switch is set to "0" or the engine starts automatically, and when the engine is started, the ignition switch 138 is turned to the "1" position. The starting process of the engine is greatly facilitated by the electrically adjustable pressure compensating valve 52 between the chamber 26, 27 and the check valve 54 in chamber 29.

3.5 Engine control in idle

The spark is preferably controlled by a Hall sensor and a Hall wheel with at least two grooves directly with the Kp a, b and two single-filament coils, which are connected to a battery generated. The control of an early and late ignition, as in conventional motors, via a vacuum box which is fed via the intake passage, by pressing the support plate 132, 133 take place automatically.

If the engine is started, the Kp a, b can now alternately by simultaneously entrainment of the working shaft 58, gear control disc 83, 84 or the rotor 102 of the internal ECM by the oppositely acting backstop 75, 76, by 90 ° / 60 Continue turning ° / 36 ° Kw. At the same time all necessary work cycles are carried out. This process repeats until the engine is switched off. The compression pressure in the chamber 27 is via an electrically controllable valve 52 for pressure control in conjunction with the accelerator pedal (e-gas) or other suitable adjusting mechanisms regulated so that both piston pairs after 90 ° / 60 ^o / 36 ° Kw still slightly touch the pin 48 and the idle speed is kept constant. By transferring the expanding thermal gas pressure and the kinetic energy to the second pair of pistons both piston pairs, directly opposite, 45 ° / 60 ° / 72 ° Kw further rotated. The excess fuel-air mixture is returned via the compressed air line 32 into the suction chamber 26. The flywheel supports in this operating state a uniform rotational movement of the working shaft.

3.6 Motor control in partial and full load range

If the supply of the ignitable fuel-air mixture is changed by operating the accelerator pedal, the electrically controllable valve 52 is simultaneously opened or further closed and the compression pressure in the chamber 27 and the operating power or speed of the motor reduced or increased. Also in this operating condition, the following pair of pistons will automatically stop in the OTYUT by the reaction force acting counter to the direction of rotation until the working pair of pistons contacts the stationary pair of pistons at its pin and then back up by transmitting the thermal gas pressure and the kinetic energy or momentum to the UT / OT and next At turns. In addition to the controllable valve 52, the speed of Kp a, b and the power of the engine by the early or late ignition via a vacuum box, which is connected to two rotatably mounted Hall sensors, regulated.

The following special advantages arise for this engine concept, among other things: that in a relatively compact design, a large crank radius, high torque at the same time low speed and high power stroke is possible that is to be expected by the small number of interacting engine parts with low friction losses and thus with an increased mechanical efficiency that by large and exhaust ports, which remain open throughout the expansion path at the At and covered by the sealing function of the pistons on both sides, the volumetric efficiency (grade) can be increased, that with the two internal ECM not only an almost wear-free starting the engine but also when the internal combustion engine is running a parallel hybrid drive 45 or when the ignition is off, a purely electric drive is possible and that the internal combustion engine alternately one of the two internal

ECM drives as a generator and the power generated can be supplied to an energy storage. indungsgemäße task is solved in that

the sum of the angular degrees of a piston pair with pin and piston stroke is always 180 ° Kw, a piston is located after each rotation of a pair of pistons of 135 ° / 120 ° / 108 ° Kw exactly in the position of the TDC between the exhaust and suction and the Spark plugs are arranged between two pistons in the BDC, no valves and valve control are required by a new sealing element concept, in which the piston pairs have a closed sealing boundary at 90 ° to the two piston disks and the housing wall, At the At the Kp a, b are supported in the OT / UT by a backstop in the respective housing and with opposite action of a backstop the working shaft together with the gear control disc 83, 84 or the magnetic disk 112 and the rotor 102 with the externally excited permanent magnet 104 of the internal ECM, can be rotated, the torque alternately one of the two internal ECM with ignited fuel-air mixture and simultaneously from both internal ECM, with the ignition off via the backstop 75, 76 can be transmitted to the working shaft, in the chamber 27th There are two openings 30, which are connected by means of a compressed air line 32 and that this compressed air line has an electrically controllable valve 52 which can equalize the pressure in the compression and suction chamber when a piston is located between the two openings, this valve with the help of a rotary potentiometer on the accelerator pedal or other actuators elek Controlled trically and thus the engine power on the variable compression can be additionally influenced, in the chamber 28, a further opening 31 is located, which is closed with a check valve 54 and at negative pressure (eg

Starting operation) opens this chamber, with the speed sensor 87, an engine management is enabled that optimally adjust the power consumption, fuel consumption and CO ₂ - emissions via a lambda probe, a simple engine start-stop function (not only for hybrid drives) to save fuel consumption Advantageously characterized it is possible that, with stationary piston pairs, the working shaft, together with the energy stored in the flywheel 88, continue to rotate freely and the motor can be started again independently of the rotating working shaft 58, a magnetic disk 112 for each pair of pistons by Hall sensors or position sensor 113, electronically commutated and a control electronics the angular exact reversal reverses, for each pair of pistons a spark plug 42 is available and their ignition with a Hallrad with at least two grooves, a Hall sensor and a Single spark coil is made and that the adjustment of the ignition can be done simultaneously via a vacuum box for both spark plugs, the engine concept variability in the geometric design of the piston winkeis and the piston pin and thus the piston stroke or

Hubverhältnisses and the compression chamber or the compression within the constant circular segment in the cylinder of the motor housing of 180 ° Kw allows the execution of the inner housing and piston cross-section in round or square shape by the new sealing element concept is possible, with a continuous in the piston discs built-in oil pressure circulation lubrication can simultaneously perform a cooling and sealing function of the piston to the individual chambers and the housing interior.

4. Exemplary embodiment

The invention is described in more detail in the construction and the operation with reference to an embodiment shown in the drawings with the piston and pin angle of 45 ° Kw total and a piston stroke of 90 ° Kw in the following.

Show it: 1.1 is a schematic side view of the interior of the engine with the recurring working position of the piston pairs and the division of the annular space into four chambers,

1.2 shows a partial cross section through the annular housing with the two piston discs, the piston and their storage in the housing,

Fig. 2.1 shows an overall cross section through the involved in the motor principle

Components, with the lubricating oil course on a pair of pistons,

2.2 is a partial section through the gear wheel control disk with sprocket and damper disc and the view of the device for locking and positioning of the pistons in TDC and UT,

Fig. 2.3, 2.4 shows the side views of the gear control disk for controlling the starter motors and the locking with two 180 ° Kw opposite circle segments and the position of the sensors in the OT,

Fig. 2.5- 2.7 is a partial cross-section and the isometric view of the internal ECM with the rotor (permanent magnet), stator (solenoid) and the brushless commutation of the magnetic disk by means of Hall sensors or position sensor,

3.1- 3.10 the representation of the working principle with sensor control over circle segments, position wheel and Hall sensor, with one revolution of both piston pairs, using the example of a suction motor,

FIG. 3.11 shows a path-time diagram (s / t diagram) of the two piston pairs to illustrate the alternately rectified rotational movement and the ratio of 2: 3 to the working shaft, FIG. FIG. 3.12 shows a working diagram (p / v diagram) of the sensor-controlled RKB as a naturally aspirated engine in cooperation with the pressure profile in the individual chambers versus the displacement volume (chamber volume), FIG.

4 is a circuit diagram showing the engine control with the ignition, the Hall sensor and Hall wheel, the locking device with solenoids, and the external starter motors via circular segments by sensors and a Zündstartschalter,

Fig. 4.1 shows a portion of the circuit diagram showing the motor control of the conventional external starter with the Polwendeschaltung for reverse rotation,

5.1 to 5.7 the sealing concept of the individual piston and piston discs with piston ring segments and further sealing elements for two alternative piston or cylinder cross sections,

6 shows the isometric view of the oil pump function integrated in the piston disks with pump disks,

6.1-6.6 the sections and bottom view on the piston with the holes for lubrication and cooling of the same and the cover plate used as a check valve,

7 shows the isometric view of the coolant flow in the housing parts with the oil holes, which are integrated in the housing ribs,

8.1, 8.2 the overall external view of the sensor-controlled RKB from left and right, 9 shows the overall external view of the sensor-controlled RKB with two internal ECMs,

FIG. 9.1 shows a block diagram with the internal ECM arranged to the left and right of the RKB, as a function of a parallel hybrid drive.

According to an advantageous embodiment Fig. 1.1 and Fig. 1.2, the engine includes two 180 ° Kw opposite pairs of pistons with the piston 1, 2 (Kp a) and 3, 4 (Kp b), interchangeable on each of a circular piston disc fifth 6 can automatically position themselves axially at the same distance from the inner wall of the housing 17, 18. This is once by the sliding connection of the piston rod 8 in the piston pin 7 and a precise radial backlash adjustability by means of two threaded pins 12 in the threaded bore 11, with spherical and eccentric offset screw end which engages in a sliding block 9 Fig. 5.1- 5.3 or by a Screw connection of the piston 1 - 4 to the piston disc 5, 6 by means of the piston screw 23 and a piston pin 24 Fig 2.5, wherein the piston is displaceable on the piston disc, possible. By cylindrical springs 209, which act on an oil scraper plate 208, 213 side, the uniform distance is maintained. The overhang of the pistons to the adjacent piston disc has a small radial gap 164 for the smooth rotational movement and each piston can be supported for transmitting the torque on a broad basis to the end face of the respective piston disc.

In a piston variant, each of the four pistons has a right-angled and in another variant a circular-arc-shaped cross-section which ends in the lower region in a base 10. FIG. 5.6. These cross sections are designed to four pistons 1-4 with pins 48 at the end faces. These pistons simultaneously perform a valve and sealing function with the closed housing 17, 18, 19 consisting of several parts, with the four chambers 26-29 and with the piston discs. The intake 35 and exhaust port 36 is arranged on the circumference Fig. 1.1 of the housing so that a valve control for sealing the openings in the recurring rotational movements of the piston pairs in the working position of the OT / UT omitted. The housing 17 and 18 has a threaded bore 40, 41 for receiving a spark plug 42 in the UT.

Two piston disks, which are mounted on the outer diameter of the hub 14 on the left and right in the housing 17, 18 by means of ball bearings 15, 16, form a claw-shaped toothing 66, 67 at the end face. Between the two ball bearings and the respective piston disc in the housing each have a backstop (freewheel) 21, 22 which is connected to the hub 14 by a feather key 25, arranged so that alternately a piston discs with a Kp a or b centric to the working shaft 58 can rotate in one direction only.

The second pair of pistons together with the working shaft 58 by an oppositely acting backstop 75, 76 alternately rotated so that during a selected rotation of 90 ° / 60 ° / 36 ° Kw all four known working cycles (suck - chamber 26, compaction chamber 27 , ignite - chamber 28 and ejection - chamber 29) of a reciprocating engine, can be implemented.

By changing the diameter and length of the pin 48 and piston 1 - 4 (piston angle), the compression, the stroke ratio and the chamber volume in all 4 chambers is affected even at the same crank radius R. The sum of the angular degrees of two pistons with the pin 48 together with the expansion 29 and compression chamber 27 is always 180 ° Kw.

The working shaft 58 is supported by sliding or needle bearings 61 in the hub bore of the piston disk Fig. 2.1. On both sides of this shaft, with the claw-shaped toothing 66, 67, an inner clutch plate be 69, 70 with the piston discs 5, and 6, axially coupled. The inner clutch disc is mounted with the ball bearings 72, 73 and 77, 78 on the outer clutch disc. Between the ball bearings, a backstop 75, 76 is concentrically arranged so that the inner 69, 70 via the outer clutch disc (80), (81) with the feather key 82, the working shaft rotates in the piston direction of rotation.

In the further embodiment, a gear wheel control disc 83, 84 with a ring gear 85, 86, for driving the piston pairs in the starting process of the engine Fig. 2.1, by means of external electric starter 139, 140, and in the internal ECM of the rotor 102 with Externally excited permanent magnets 104 and a magnetic disk 112 with the inner clutch plates 69, 70 rigidly connected. The stator (E magnet) 103 of the internal ECM is attached to the housing cover 95, 96 concentrically with the working shaft. The rotor is electronically rubberized or detected by three Hall sensors or position encoders 113 distributed around the stator 103 and also fastened to the housing cover. FIGS. 2.5 to 2.7. At one end of the working shaft is on the outer clutch disc 81, a flywheel 88, in which the torque of the engine is stored and which may be in connection with a mechanical or automatic vehicle clutch and transmission. At the opposite end of the working shaft, an oil rotary duct 89 is provided, which can also accommodate a sensor 87 for speed detection of the working shaft. Also on this page is the installation of a V-belt pulley 92 on the outer clutch disc 80 for driving the required attachment assemblies, e.g. Water pump, alternator, refrigerant compressor, etc. provided.

The working shaft is fixed and centered by two corrugated spring washers or disc springs 90 by means of two nuts 91 (or with other suitable Befestigungsele- elements) to the housing in such a way that the outer

Clutch plate 80, 81 to the inner clutch disc 69, 70 each over the Ball bearings 77, 78, and 15, 16 axially on the left and right housing 17, 18 can be supported. This ensures a length compensation for the existing temperature changes and tolerance compensation of the individual components. The starting process is on the one hand inventively made possible that with a positive axial coupling 66, 67, a connection of a sprocket 85, 86 via the gear control disc 83, 84 to the inner clutch disc 69, 70 and piston disc 5, 6 is produced. The piston pairs a, b are thereby alternately driven by an external starter 139, 140 from any position, within the annular cylinder 19. By means of a sensor 118, 120 which is fixed to the housing cover 95, 96 at top dead center, the starters of the piston pairs a and b are switched on or off without contact via two symmetrically arranged outer circular segments 122, 123. Via two symmetrically arranged inner circle segments 128, 129 is a sensor 125, 126, which is also attached to the housing cover 95, 96 at top dead center Fig. 2.1. switchable, whereby two solenoids 98, 99 can be activated, the two symmetrical operated on each side of the housing cover locks operate, whereby one of the piston pairs a, b is stopped. The lock consists of a stable Bolzenfuhrung 100, 101 with a locking pin 97 and two stops 105, 106, which are connected to a damper disc 110, 111. The gear control disk is rotatably stopped relative to the damper disk, against the damping action of a spring 115, 116 Fig. 2.2- 2.4.

On the other hand, by applying a Polwendeschalter 93, 94 Fig. 4.1 in the conventional external starter or with the magnetic disk 112, the

Hall sensor or position sensor 113, and the control electronics of the internal ECM an alternate direction of rotation reversal possible, so that the piston pairs during the starting process alternately by the backstop 21, 22 in the housing

17, 18 are stopped and the sprung locking device with lifting magnets can be omitted. With an internal ECM arranged to the left and right of the RKB, the following drive variants are advantageously also possible according to the invention in a vehicle FIG. 9, 9.1:

a) Sole vehicle drive by RKB (stand-alone). ECM only as a starter motor. b) Drive with RKB plus external electric motor (serial, parallel, combined hybrid drive) c) Drive with RKB plus reciprocal drive through the two internal ECMs

(parallel hybrid drive, torque addition). d) Alternate generator drive of the internal ECM by the RKB after the start. e) Vehicle drive by pure battery operation of both internal ECM. f) A retroactive drive of the flywheel 88 by braking energy can be done by the freewheel 75, 76, which decouples the working shaft to the piston pairs.

To control the ignition timing Fig. 2.1 for each pair of pistons a Hall sensor 130, 131 is provided which is rotatably mounted on a support plate 132, 133 on the outside of the housing cover 95, 96 and connected via a rod 149. Thus, it is inventively by the provided with at least two grooves Hall wheels 135, 136 on each side possible, a vacuum controlled ignition with a spark plug and Einzelfunkenspule 144, 145 on each side of the housing for Kp a, b at an ignition after each 135 ° / 120 ° / 108 ° crank angle rotation of the working shaft represent. The sensor-controlled, electronic operation for starting and speed control of the motor, together with the position of the Kp a, b, the connected circular segments, the inductive sensors and the Hall wheel to the HaIl- sensors, is shown in Figs. 3.1- 3.10 and in Described below: Fig. 3.1

From any position in the housing of the Kp a, b to each other, they are rotated by the external starter 139, 140 or by the internal ECM to the right in the recurring working position of the OT / UT.

Fig. 3.2

The following Kp b, a is from Kp a, b via circular segments by two solenoids that actuate a lock or by changing direction of rotation reversal of the external starter Fig. 4, 4.1 and the two internal ECM Fig. 2.5- 2.7, in OT / UT sensitively controlled, recorded.

Fig. 3.3

Starter 1 turns Kp a by 90 ° Kw, first aspiration of fresh ignitable fuel-air mixture, Kp b in TDC. Pressure equalization by controllable throttle valve 52 in chamber 26, 27. The check valve 54 compensates for the negative pressure in chamber 28.

Fig. 3.4

Starter 1 turns both Kp a, b directly facing each other and touching the pin with maximum contact by 45 ° Kw to the new working position (total 135 ° Kw), the Kp b is released in the OT, the Kp a stops.

Fig. 3.5

Starter 2 continues to turn Kp b 90 ° Kw, the Kp a is held, priming and first compression of the fuel-air mixture with pressure compensation. The check valve 54 compensates for the negative pressure in chamber 28.

Fig. 3.6

Starter 2 turns Kp a, b 45 ° Kw to the 135 ° Kw of the working position. There is the first ignition of the fuel-air mixture and the first power stroke begins. Fig. 3.7

Due to the expansion force Kp b stops, the working game sucking, compressing, working and pushing out takes place by the rotation of the Kp a by 90 ° Kw at the same time.

Fig. 3.8

Both pairs of pistons continue to rotate by 45 ° Kw up to the working position due to the driving force and the moment of inertia of the Kp a, the second At takes place.

Fig. 3.9

In the second At the Kp b is rotated by 90 ° Kw, the kinetic energy is transferred to the Kp a. The engine runs automatically.

Fig. 3.10 Kp a and b continue to rotate by 45 ° Kw and have moved one full turn from the position of Fig. 3.2. The work cycles are repeated until the ignition is switched off or more fuel-air mixture is supplied.

If there is no further ignition after switching off the engine, the pressure in chamber 26, 27 is compensated by the controlled valve 52 and both pairs of pistons can continue to turn freely on the working shaft to a standstill.

Fig. 3.11

The s / t diagram shows the interplay of the intermittently rotating and stopped Kp a, b in the ratio of 2: 3 to the working shaft and the four resulting At after a full rotation of both piston pairs. Fig. 3.12

The p / v diagram summarizes the working cycles of suction, compression, working and pushing out in the individual chambers with the pressure curve across the Kw of 90 ° (chamber volume VH = Vh + Vc). All the gases in the chambers are stored with the appropriate thermal gas state (overpressure, vacuum) when turning over a 45 ° Kw, until the working position has been regained and the cycle starts again. The order of the chambers starts again from the beginning (chamber 29 becomes chamber 26, etc.).

For the proper functioning of the engine concept according to the invention, the following subconcepts within the engine are of great importance. These include in an advantageous embodiment:

• the sealing concept on pistons, piston discs and housings

• the lubrication concept and

• the cooling concept of the engine

4.1 The sealing concept of the engine

In order to obtain a useful or working performance in the sensor-controlled RKB as in the known "gasoline or diesel" gas engines, is an absolute gas tightness between the individual pistons, the piston disc and the housing and a sufficient compression of the fuel-air mixture , even at high temperatures, required.

This is inventively achieved in the rectangular piston variant Fig. 5.1- 5.4, characterized in that in the two outer grooves 179 of the four pistons, two rectangular shaped sealing elements 158, 159 to the housing 17, 18 and by overlapping shock 161 and radially to the annular cylinder 19 out , seal. The sealing element 158, 159 is at the lower end by overlapping 165 designed so that a sealing connection in the piston groove 182 with the trapezoidal sealing elements 166, 167 to the individual chambers and the 90 ° intersecting piston disc with the sealing rings 170, 171, 172 is formed. Two corrugated springs 175 with three arches generate, in a deeper groove in the piston supporting, according to the invention the required contact pressure in all directions (see arrows a - h, Fig. 5.2 and Fig. 5.3). In the central groove 177 of the piston, two orthogonal oil scraper lubricating members 160 that overlap 183 toward the annular cylinder 19 are inserted. These lubricating elements are also pressed by a corrugated spring 175 with three arcs, radially and at 45 ° in the direction of the arrows ac. For each piston laterally two flat oil stripper plates 208, 213 by two cylindrical springs 209 to the housing wall pressed (see arrows j, k), whereby the excess lubricating oil in the groove 188 through the piston disc through the holes 168, 169 back to Working shaft 58 and then out of the housing.

The arcuate piston variant Fig. 5.5- 5.7 and Fig. 6.1, 6.6 is inventively by a cross section having a base 10 down, shown. The piston groove 162 is led horizontally into the base. The horizontal groove 163 in the base Fig. 6.3 is used, as in the rectangular piston variant, for receiving further, to the piston disc 90 ° crossing trapezoidal sealing elements. The protruding side in both piston variants has a small clearance 164, which corresponds approximately to that of the piston to the housing, to the adjacent piston disk. FIG. 5.6.

Due to the oil pressure in the main oil flow 199, of the oil flowing into the bore 197 in the middle of the piston, the oil stripping plates 208, 213 of the oil scraper lubricating ring segments 153 and the oil scraper lubrication element 160 are additionally supported in their sealing function. FIG. 6.5. With the sealing elements 166, 167 Fig. 5.1- 5.7, the sealing system is closed at the arcuate piston. Two outer sealing rings 170, 171 and a sealing ring 172 arranged between the piston disks with an overlapping 173 or straight joint 178 on the underside of the piston, seal the chambers to the 90 ° intersecting piston disk in the direction of the housing center. According to the invention by a corrugated spring 175 with three arc, the sealing elements 166 with chamfer and 167 in trapezoidal shape, held against the centrifugal forces and simultaneously pressed on the sealing rings 170-172 and end faces of the piston disc.

The compression ring segments 150, 151 have a wide opening width to allow them to overlap with the outer flat sealing elements 166 to prevent leakage due to manufacturing tolerances, thermal effects, or high gas pressure in the housing. The resulting increased gas pressure during compression and combustion of the fuel-air mixture supports in all directions the sealing effect in the chambers to the pistons and piston disks of the design of the sealing system according to the invention. The middle sealing ring 172 whose flanks coincide with the chamfer of the two piston discs, is rotated by a pin 180 which is attached to a piston disc.

With cylindrical springs 63 Fig. 1.1. 2.1 in the holes 68, the

Piston disks with the sealing rings 170, 171 to the inner wall of the housing

17, 18 and the pump disks 215, 216 pressed against the inner surface of the piston disk to support their thermal expansion sealing function.

4.2 The lubrication concept of the engine

Each engine requires a reliable lubrication system for the moving mechanical parts. Fig. 2.1 According to an advantageous embodiment of the invention, a continuous oil pressure recirculation lubrication is designed, which at the same time also assumes a cooling function of the engine pistons and bearings with additional sealing function of the piston to each other and the housing.

In order to ensure a return flow, contrary to the centrifugal forces acting on the oil, from the housing and to maintain the oil circulation, an oil pump function FIG. 6 is advantageously integrated in the piston disks 5, 6.

This is inventively achieved in that

on one side of the working shaft, an oil rotary feedthrough 89 Fig. 2.1 is provided which is sealed with two shaft seals 185 and mounted with two ball bearings 187 on the working shaft 58, - in the center of the working shaft an oil hole 190 is provided, which leads up to the piston discs and that in this bore a thread for receiving at least one check valve 192 (with flow in the screwing) provided and the working shaft is sealingly sealed at both ends frontally, - further holes 194, 195 radially Fig. 6 the pump groove segment 210,

211 tangentially next to the piston rod 8 are led out of the piston discs 5, 6, in an alternative screw the piston 1 - 4 to the piston disc Fig. 2.5 the oil through a central oil hole 194 via the check valve 191 (with flow direction against the screwing) through the Piston screw 23 is guided, in each piston 1-4, the bores 194, 195 Fig. 6.1-6.6 merged with a V-shaped groove 196 to a central vertical bore 197, which exits at the upper end of the piston, are merged, under the oil scrape lubricating ring segment 153 or lubricating element 160, the oil in the groove 198 of the piston can tile on one side via two bores 201 back to the center of the housing, while the housing surface is lubricated in the secondary flow 200 and the oil in the main flow 199 of the oil scraper and lubricating ring at the same time performs a sealing and cooling function to the adjacent piston, in the alternative screw Fig. 2.5 of the piston to the piston plate, the oil on the piston pin 24 back to the holes 201 and the oil stripper plates 208, 213 is performed and at this

Place only necessary for lubrication oil can escape and the main oil flow is passed through the bore 168, 169 back to the working shaft, at each end of the Ölabstreif- Schrnierringsegmentes 153 or lubricating element 160 inserted into the piston oil stripper plate

208, 213 located on both sides of the housing wall in each case the excess oil in the piston, by the pressure of the springs 209 via the V-shaped groove 203 and the bores 201, 202 and the bore 168, 169 Fig. 6 back to the working shaft 58th and leads out of the housing, - the two housings 17, 18 Fig. 2.1 each have two holes 204, 205, which make it possible to lead the oil out of the housing to close the circuit to an oil cooler, the two piston discs 5, 6 radially and axially have a plurality of bores 62 which allow a connection to the axial bores 64, 65 of the inner clutch plates 69, 70 for the lubrication of the bearing between the outer / inner clutch discs, with all these measures all rotating bearing parts can be supplied with oil.

An oil pump function Fig. 6 According to the invention Advantageously achieved in that the two piston discs 5, 6 as well as the engine pistons relative to the continuous rotation of the working shaft always turn after 90 ° / 60 ° / 36 ° Kw alternately once or rotate apart, on the two piston discs radial oil holes 186 are provided in connection are provided to the two pump groove segments 210, 211, between the piston discs two pump rings 215, 216 are provided, which are wider than the circular arc-shaped grooves and guided over the inner diameter in a recess 217 of the piston discs, these pump rings with two cams 218, 219 equipped are exactly in the pump groove segments 210, 211 abut on one side of the groove and which are so long that they can cover the two oil holes 212 after a rotation of 90 ^o / 60 ° / 36 ° Kw at the other end of the groove itself Furthermore, at least two driving pins on each pump ring

221, 222 are located on the outer diameter of the pump rings, which are integrally inserted from the right pump ring into a groove 220 of the left piston disc and vice versa and rotated by this, in the pump groove segments 210, 211 located oil by the relative rotation of the pump rings and Cams and is pressed by the closing check valve 192, at the same time in all provided holes 194 of the piston disc and the engine piston, by the reverse relative rotation of the pump rings and cams a suction effect and the backflow of the oil from the central bore of the engine piston during the intake process thereby prevents that according to the invention for each piston a check valve 191 is provided in the bore 194 Fig. 2.5 or below each piston a sealing plate 224 is dimensioned and fixed so that they once the groove 196, 203 Fig. 6.1, 6.3 in the piston and means two circular arcuate by notching 22nd 7 resulting, movable La see 225, 226 both holes 194, 195 can cover next to the piston rod 8, the capacity of the oil pump by the depth, width and radius of the pump groove segments 210, 211 can be adapted to the requirements.

The oil flowing through the housing Fig. 2.1 must be sealed to the outside. The seal between the two housings 17, 18 and the annular cylinder 19 is effected by two flat or round sealing rings 230, which also simultaneously support the sealing of all four chambers to each other. An axially acting flat sealing ring 231 seals the housing to the inner clutch disc. The axial sealing of the piston disc 5, 6 to the outer clutch disc 69, 70 assumes an O-ring 232. The sealing lips of the ball bearings 77, 78 take over the function of sealing the outer clutch disc and two O-rings 234, 235 to the working shaft.

4.3 The cooling concept of the engine

The heat generated during the combustion process is known to be converted only to a small extent in kinetic energy. The excess heat must be dissipated to the outside via a suitable cooling system.

This is inventively Fig. 7 achieved in that both housing 17, 18 have a cavity 240 which is closed by the two housing cover 95, 96 and on each side of the housing cover two O-rings 244, 245 the space for a flowing cooling medium seal and that the annular cylinder 19 has a cavity 242 inside, through which the cooling medium can flow in the same direction.

On each side in the cavity of the housing and in the annular cylinder 19 designed as a housing rib partition wall 243, 247 is provided which the cooled coolant simultaneously by three Einströmöffhungen 250, 251, 257 opposite to the piston rotation direction leads to the larger heat zone on the exhaust side. The outflow openings 252, 253, 258 are located after a complete inner flushing of the housing and cylinder 19 on the opposite side to the partition wall 243, 247, where the heated coolant is supplied to the water cooler and a thermostatically controlled cooling circuit.

According to the invention, the dividing wall 247 and an opposite rib 248 simultaneously serve to receive the required oil bores 204, 205.

Each individual piston is advantageously cooled in addition to the oil cooling by flushing the front and rear with fresh fuel-air mixture after each full revolution.

4.4 Installation position and increase in performance of the engine concept

The overall motor concept in the exterior view 50, 60, 45 is shown in FIGS. 8.1, 8.2 and 9. In the selected installation position, e.g. the sensor-controlled RKB according to the invention are each mounted with two brackets 260 mounted opposite the housing in order to support the resulting motor torque. The nozzle 262 in a horizontal position on the housing 17 is the connection to a carburetor of the engine. The downwardly leading nozzle 265 on the housing 18 is provided for the connection of a muffler.

A connection from the exhaust port 265 to the Frischgasstutzen 262, the installation of a regulated turbocharger is guaranteed.

With a suction port injection and a supercharger charge in the fresh gas nozzle 262 is to expect a significant increase in engine performance, with low fuel consumption. LIST OF REFERENCE NUMBERS

Number Name Number Name Description Number Name |

Claims

claims

A rotary piston internal combustion engine (RKB) having two pairs of pistons (a) (b) each mounted on a piston disc (5, 6) and in an annular cylinder (19) of a closed housing (17, 18) about a central axis rotate while driving a working shaft (58), characterized in that the pistons (1 to 4) of the piston pairs (a, b) on each end face each have a pin (48) that the piston (1 to 4), and two internal electronically commutated starters, generators, motors (ECM) (102 to 104) in outer pole construction with a magnetic disc (112), by means of sensors (87, 113, 118, 120, 125, 126, 130, 131) controlled without contact or regulated and that a 90 ° crossing sealing border is provided, which by means of corrugated springs (175) and rectangular sealing elements (158, 159) and trapezoidal sealing elements (166) together with piston rings (170 to 172) in the piston discs (5, 6) within the annular cylinder (1 9) in a recurrent working position chambers (26 to 29) form, the work cycles of a four-stroke engine ausfuhr.

2. rotary piston internal combustion engine according to claim 1, characterized in that as chambers in the working position between the end faces of the piston (1 - 4) with the pin at top dead center (TDC) a suction chamber and bottom dead center (UT) a working chamber in that a compression chamber (27) and an expansion chamber (29) are formed on the piston rear side of the piston pairs (a), (b), and that an intake opening (35) for the connection of fresh fuel is located at top dead center (TDC). Air mixture, as well as at bottom dead center (UT) in the housing (17), (18) a spark plug (42) and with distance of a KoI- Bengebels to top dead center (OT) an exhaust port (36) are provided in the expansion chamber.

3. Rotary piston internal combustion engine according to claim 1, characterized in that with a piston angle, that is an angular range

45 ° / 60 ° / 72 °, over which extends a piston with pin (48) and the piston stroke (crank angle), that is the angular range 90 ° / 60 ° / 36 ° (Kw), over which a piston move the working position can be repeated after 135 ° / 1207108 ° (Kw) so that the sum of the angular degrees of two pistons with pin (48) and the piston stroke is always 180 ° (Kw).

4. Rotary piston internal combustion engine according to claim 1 to 3, characterized in that by the expansion force of the compressed and by the spark plug (42) in the bottom dead center (UT) between two pistons in the working chamber (28) ignited fuel-air mixture alternately Piston pair (b) or (a) is moved, while the second pair of pistons (a) and (b) by a backstop (21), (22) in the housing (17), (18) supporting, between the Ku Gellager (15), (16) and the piston disc, concentric on a hub

(14) is stored, a maximum of the period of rotation of 90760 ° / 36 ° (Kw) stops, and that in the chambers (26 - 29) the working cycles of a four-stroke engine are performed, and that then continue to rotate both pairs of pistons together until a new working cycle begins.

5. Rotary piston internal combustion engine according to claim 1 to 4, characterized in that the working shaft (58) with a flywheel (88) and a gear control disc (83), (84) by an oppositely acting, between the inner clutch disc ( 69), (70) and the outer

Clutch disc (80) (81) concentrically mounted backstop (75), (76) by the rotating piston pair (a) or (b) mitge- together or that the control disc (83, 84) is replaced by a rotor (102) of an ECM (102-104) with permanent magnet (104) and a magnetic disc (112), and that on both sides of the housing cover (95), (96) concentrically to the working shaft, a stator, in particular in the form of an electromagnet (103) is fixed and the rotor is driven by a permanent magnet electrically or by the piston pairs.

6. rotary piston internal combustion engine according to claim 2 to 5, character- ized in that in the compression chamber (27) of the annular

Cylinder (19) two openings (30) are provided, which are connected by means of a compressed air line (32), and that this compressed air line (32) has an electrically controllable throttle and check valve (52) through which a pressure drop from the compression ( 27) is compensatable towards the intake chamber (26) when a piston (1-4) is located between the two openings (30), and that there is a further opening (31) in the expansion chamber (29) a check valve (54) is closed and opens at negative pressure, this chamber.

7. A rotary piston internal combustion engine according to claim 1 to 6, characterized in that the control and regulation of the spark for two spark plugs (42) contactlessly via a sensor (130), (131), each with a rod (149) connected support discs (132), (133) is mounted, wherein the sensor (130), (131) about a central axis of the housing cover (95), (96) is rotatably mounted, and thereby the timing of the ignition is adjustable.

8. A rotary piston internal combustion engine according to claim 5 to 7, characterized in that with a positive axial coupling (66), (67) a rigid connection of a sprocket (85), (86) via the gear

Control disc (83), (84) or a rotor (102) with permanent magnet (104) and a magnetic disc (112) of the ECM (102 - 104) is replaced, for inner clutch disc (69), (70) and piston disc (5), (6) is produced and characterized by the piston pairs (a), (b) by an external starter (139) (140) by means of a sensor (118 ), (120) which is fixed to the housing cover (95), (96) at top dead center, via two symmetrically arranged outer circle segments (122, 123) or each of an internal ECM (102 - 104), from an arbitrary position within the annular cylinder (19), the piston pairs (a) and (b) detected without contact or electronically commutated by Hall sensors or position sensor (113) are controlled and regulated.

9. rotary piston internal combustion engine according to claim 8, characterized in that via two symmetrically arranged inner circular segments (128), (129) a sensor (125), (126) on the housing cover (95), (96) at top dead center is fixed, is switchable, wherein when switching the sensor (125) of the solenoid (98) or a Polwendeschalter (93) of the

Piston pair (b) is activated, and wherein when switching the sensor (126) of the solenoid (99) or another Polwendeschalter (94) of the piston pair (a) is activated, and wherein the lifting magnets (98), (99) two symmetrical locks or the Polwendeschalter (93, 94) or the electronically commutated, controlled and controlled rotor (102) of

ECM (102-104), reverse the direction of rotation alternately, stopping one of the piston pairs (a), (b).

10. rotary piston internal combustion engine according to claim 1 to 9, character- ized in that in a circular arc-shaped piston variant, the piston (1-4) have a base (10) and outer grooves (162) of the piston (1-4) at least two Kompressionsringsegmente (150), (151) having a Öffhungsweite corresponding to the width of the two piston discs (5) and (6), and that in a right-angled in cross-section piston variant in an outer groove (179) two each for the compression required rectangular sealing elements (158, 159) form sealing boundaries to the cylinder surface, wherein a central groove (177), (198) for oiling and aiding the seal, an oil scrape lubricating ring segment (153) and two right angle oil scraper lubricating elements (160) overlapping (183) the cylindrical housing (19) and which components of an oil pressure circulation Lubrication are provided.

11. A rotary piston internal combustion engine according to claim 10, characterized in that a corrugated spring (175) designed with three arcs in the horizontally extending and deeper groove (163), (182), (177), (179) is arranged and arranged with the two outer arcs in the deeper groove (163),

(182), (177), (179) is supported, and that with the spring force of the central bow form the trapezoidal sealing element (167) with its front and flank surface and at the same time the mean trapezoidal sealing ring (172) and the two outer flat sealing elements (166) on the end face of the piston discs (5), (6) are pressed and fixed, and that the two

Ends of the corrugated, horizontally compressed spring can be supported at 45 ° either directly to the sealing elements (166) or at the cutting or inner edge to the rectangular sealing elements (158), (159), so that a sealing effect in all directions (a - h ), (j, k), even at standstill of the piston pairs (a, b), is given.

12. A rotary piston internal combustion engine according to claim 1 to 11, characterized in that the inner clutch disc (69), (70) together with the gear control disc (83), (84) or the rotor (102) with permanent magnet (104 ) and magnetic disk (112) as a unit on the outer

Clutch disc (80), (81) in the ball bearings (72), (73) and (77), (78) is mounted, wherein the unit by means of a sliding bearing (61) or a needle bearing in the concentric bore of the piston discs (5). , (6) is supported together with the working shaft (58) with little axial play via a spring washer (90) to the housing (17), (18), and that the outer clutch disc (80), (81) with the working shaft (58 ) and the flywheel (88) by a feather key (82) is connected and in standstill the piston pair (a) and / or (b) is rotatable relative to the inner clutch disc in one direction.

13. Rotary piston internal combustion engine according to claim 1 to 12, characterized in that as components of an oil pressure circulation lubrication and at least two cross-driver pin (221), (222) are provided by means of which by the movement of the piston discs (5), (6) and the piston pairs (a), (b) between the piston discs arranged pump rings (215), (216) are driven, which are each equipped with two cams (218) (219) which in Pumpututsegmenten (210), (211) of Piston disc (5, 6) abut on one end face of the groove and which are so long that they oil holes (212) are covered by a rotation of 90 ^o / 60 ° / 36 ° Kw at the other end of the groove, and that with cylindrical springs (63) in the piston disc (5, 6) the sealing function of the piston discs (5), (6) to the housing (17), (18) and the pump discs (215),

(216) is supported on the inside of the piston discs.

14. Rotary piston internal combustion engine according to one of claims 1 to 13, characterized in that the power increase via a connection düng from the exhaust port (262) to the Frischgasstutzen (265) a regulated

Exhaust Turbo charging is possible, and that via the Frischgasstutzen (265) a suction pipe injection and / or supercharging is guaranteed, and / or that this engine has a start-stop function, by which in standing piston pairs (a), (b) the working shaft (58 ) along with the energy stored in the flywheel (88) continues to rotate freely and the engine is restartable independently of the rotating working shaft (58), and / or in the housing (17) (18) between the spark plugs (42) in the working chamber (28) a fuel injection nozzle (43) is arranged.

15. A rotary piston internal combustion engine according to any one of claims 1 to 14, characterized in that with a left and right to this ange- arranged internal ECM with the function as starter, generator and EC motor, the mode of operation of the RKB as stand-alone drive is operable and with an external electric motor a serial, parallel, or combined hybrid drive is feasible, that by alternating connection of the two internal ECM to the RKB a parallel hybrid drive can be realized that with the RKB off sole operation of the internal ECM is realized, and / or that a retroactive drive of the flywheel (88) by braking energy with the freewheel (75), (76), the working shaft decoupled to the piston pairs, can take place.