EP2394023B1 - Rotary piston internal combustion engine - Google Patents

Description

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 according to 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 working principle 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 an upper and lower dead center (OT / UT), directly opposite each other, form four chambers by pins, and that with piston ring segments, right-angled 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 method (EC Mo gate = ECM), are controlled and regulated 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 Take over pawls. 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 revolving double-wing piston, which include between their wings located working chambers and are connected together via a control gear such that the one wing piston, except its common orbital motion with the other wing piston, with respect to the latter still an additional, the working chambers periodically increasing and decreasing relative movement performs. 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-OS 1965865 A; 1971 ) Is described in one embodiment, that a ring cylinder with housing and gear fixed. 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 opposite in a ring cavity of the housing arc piston are connected by two cross-anchored on a pendulum shaft piston levers to two pairs of curved pistons, which form by rotating the two piston levers mutually four volume-changing combustion chambers in the annular cavity, each of two curved pistons be limited. 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 piston internal combustion engine ( DE-OS 3046725 A1; 1982 ) In a ring cylinder two diametrically opposed pistons are attached to two abutting disc-shaped support means. At the circumference of the annular cylinder a number of outlets and inlets are arranged, so that at any time diametrically opposed combustion, suction, compression and ejection chambers are formed whose position shifts during the movement of the piston pairs along the annular cylinder. The respective trailing piston is mechanically locked at the end of the compression process by means of a ratchet wheel against a backward movement, wherein in the piston rotation direction, a relative movement is superimposed, so that volume-variable chambers are formed during rotation of the piston system. Between the piston systems, separate transmission means are provided for connecting the piston systems to the working shaft. in a catch the support between working and counter-piston takes over 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 A1; 1985 ) works in two- and four-stroke 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) ( U.S. Patent 5,223,463; 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 move with their four pistons in the four-stroke process oscillating in opposite directions, so that each two pistons form a pair between which play the four bars in the rotating toroid. 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 equipped with several piston rings to ensure a seal to all annularly moving components.

The DE 44 28 341 A1, which is considered the closest prior art, A1 relates to a rotary piston working machine with an even number, ie at least two in an annular, with spaced inlet and outlet openings provided cylinder space movable working piston, each at one of at least two about a common motor main axis rotatable and relatively movable piston carriers are arranged, wherein the two piston carriers by means of a mechanical Forced to each circulation movements are imposed with periodic speed change, such that for the purpose of forming a compression space of one or more defined points of the annular cylinder space associated deceleration or a stoppage of a piston carrier a trailing movement of the other piston carrier and a purpose of forming an expansion space subsequent further movement of a piston carrier is associated with a renewed trailing movement of the other piston carrier. The piston carriers are formed as circular, flat discs on which the working pistons are fastened or made in one piece with these, and which are provided with a curvature of their peripheral surface corresponding to the cross-sectional shape of the cylinder space.

The DE 306 613 C relates to an explosion engine with two each attached to an impeller and alternately circulating in an annular space, temporarily held by controlled locking pieces piston. A Sperrstückenpaar is controlled by each of two rigidly connected to the wheels Schaltringen in which associated with the motor axis Mitnehmerräder each with a resilient latch, through which the latter in misfires or overloading of the machine one or both pistons are taken.

The DE 195 25 803 A1 relates to a device for controlling the power of a rotary piston engine with electronic control unit. Between a drive shaft and a transmission shaft, a flexible shaft connection is arranged, which consists of two adjacent claw-like mutually overlapping discs, which are fixedly connected to the engine shaft and the transmission shaft and in the direction of rotation of the waves have a limited by the claw-like overlaps game that means a sensor system can be determined. The sensor system is connected to an electronic control unit. Between the two adjacent discs elastic elements are arranged to transmit power.

The WO 91/10820 A1 refers to a rotary piston internal combustion engine. In machines of this type, the working chambers and the separated by the piston portions, the working chambers of the rotating inside the housing at a uniform speed rotor against each other are permanently sealed. For this purpose, each piston has an axially parallel, radially open outer groove and two radially extending, at their radially outer ends in the outer groove opening, after opposite end faces axially open side grooves. In the outer groove is an elongated, arranged under the action of a spring with its one longitudinal side surface radially against a part-cylindrical inner surface of the rotor outer wall fitting, acting as an axial seal ceramic sealing strip. Next located in the side grooves depending on an elongated, under the action of a spring with its one longitudinal side surface axially against an inner surface of the adjacent end side part fitting, acting as an axial seal ceramic sealing strip. In the mouth region between the outer groove and the side grooves, the sealing strips lie in an overlapping area over a wide area against each other.

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, compared to the built-in motor vehicle today reciprocating engine not only one achieved overall improved efficiency, 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 about a common axis rotating piston discs, each with two symmetrically arranged pistons as piston pairs (Kp) directly in an upper and lower dead center (OT / UT) face each other a recurring working position for the alternately rectified rotational movement, without limitation 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 piston pairs rotate to the working shaft without gears in the ratio 2: 3 / 2.25: 3 / 2.5: 3 and it will generate 8/9/10 At . (see Table 1, speed Kp selected with n = 1000 rpm).

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 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.

• Motor starten und Zündvorgang
• Motorsteuerung im Leerlauf
• Motorsteuerung im Teil- und Vollastbereich

In the further course of the engine control of the following operating conditions is described:

• Start engine and ignition
• Engine control in 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 randomly coming out position, with one or both external starters or with the starter function of the internal ECM in the working position of the OT / UT and 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 according to the invention 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, contactless four solenoids 98, 99th Fig. 4 and two external circular segments two external conventional starters 139, 140 control so that in the direction of rotation of the working shaft , the Kp a through b and vice versa, two stops on a damper disc with damper spring when 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 b again rotated by the starter Kp of 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 switch is set to position "0" or the engine starts automatically. 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 is repeated 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 ° / 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 OT / UT 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 by transmitting the thermal gas pressure and the kinetic energy or the moment of inertia turn again until UT / OT and next At . In addition to the controllable valve 52 , the speed of Kp a, b and the power of the engine through the early or late ignition via a vacuum box, which is connected to two rotatably mounted Hall sensors, regulated.

• dass in einer relativ kompakten Bauweise ein großer Kurbelradius, ein hohes Drehmoment bei gleichzeitig niedriger Drehzahl und hoher Arbeitstaktfolge möglich wird,
• dass durch die geringe Anzahl der zusammenwirkenden Motorteile mit geringen Reibungsverlusten und dadurch mit einem erhöhten mechanische Wirkungsgrad zu rechnen ist,
• dass durch große Ein- und Auslasskanäle, die über den ganzen Expansionsweg beim At geöffnet bleiben und durch die Abdichtfunktion der Kolben auf beiden Seiten abgedeckt werden, der volumetrischen Wirkungsgrad (Gütegrad) erhöht werden kann,
• dass mit den beiden internen ECM nicht nur ein beinahe verschleißfreies Starten des Motors, sondern auch bei laufendem Verbrennungsmotor ein paralleler Hybridantrieb 45 oder bei abgeschalteter Zündung ein rein elektrischer Antrieb möglich ist und
• dass der Verbrennungsmotor abwechselnd einen der beiden internen ECM als Generator antreibt und der erzeugte Strom einem Energiespeicher zugeführt werden kann.

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 duty cycle is possible,
• that due to the small number of interacting engine parts with low friction losses and thus with increased mechanical efficiency,
• that the volumetric efficiency (grade) can be increased by large inlet and outlet channels, which remain open over the entire expansion path at the At and covered by the sealing function of the pistons on both sides
• that with the two internal ECM not only a nearly wear-free starting of the engine, but also with the internal combustion engine, a parallel hybrid drive 45 or with switched off ignition, a purely electric drive is possible and
• the internal combustion engine alternately drives one of the two internal ECMs as a generator and the generated current can be supplied to an energy store.

• die Summe der Winkelgrade von einem Kolbenpaar mit Zapfen und Kolbenhub immer 180° Kw beträgt,
• ein Kolben sich nach jeder Drehung eines Kolbenpaares von 135°/120°/108° Kw genau in der Position des OT zwischen der Abgas- und Ansaugöffnung befindet und die Zündkerzen zwischen zwei Kolben im UT angeordnet sind,
• durch ein neues Dichtelementkonzept, bei der die Kolbenpaare eine sich 90° kreuzende geschlossene Dichtgrenze zu den beiden Kolbenscheiben und zur Gehäusewand aufweisen, keine Ventile und Ventilsteuerung erforderlich sind,
• beim At das Kp a, b sich im OT/UT durch eine Rücklaufsperre im jeweiligen Gehäuse abstützen und mit entgegengesetzter Wirkung einer Rücklaufsperre die Arbeitswelle zusammen mit der Zahnrad- Steuerscheibe 83, 84 oder die Magnetscheibe 112 und der Rotor 102 mit dem Fremderregten Permanentmagnet 104 des internen ECM, mitgedreht werden kann,
• das Drehmoment abwechselnd eines der beiden internen ECM bei gezündetem Kraftstoff-Luft-Gemisches und gleichzeitig von beiden internen ECM, bei abgeschalteter Zündung über die Rücklaufsperre 75, 76 auf die Arbeitswelle übertragen werden kann,
• in der Kammer 27 sich zwei Öffnungen 30 befinden, die mittels einer Druckluftleitung 32 verbunden sind und dass diese Druckluftleitung ein elektrisch regelbares Ventil 52 aufweist, das den Druck in der Verdichtungs- und Ansaugkammer ausgleichen kann, wenn sich ein Kolben zwischen den beiden Öffnungen befindet,
• dieses Ventil mit Hilfe eines Drehpotentiometers am Gaspedal oder anderen Stellorganen elektrisch geregelt und damit die Motorleistung über die veränderliche Verdichtung zusätzlich beeinflusst werden kann,
• sich in der Kammer 28 eine weitere Öffnung 31 befindet, die mit einem Rückschlagventil 54 verschlossen ist und bei Unterdruck (z.B. beim Startvorgang) diese Kammer öffnet,
• mit dem Drehzahlsensor 87 ein Motormanagement ermöglicht wird, dass den Leistungsbedarf, Verbrauch und CO₂ - Ausstoß über eine Lambdasonde optimal einstellen kann,
• eine einfache Motor Start- Stoppfunktion (nicht nur für Hybridantriebe) zur Einsparung des Krafistoffverbrauchs Vorteilhafterweise dadurch möglich wird, dass bei stehenden Kolbenpaaren die Arbeitswelle zusammen mit der im Schwungrad 88 gespeicherten Energie sich frei weiterdrehen und der Motor unabhängig von der drehenden Arbeitswelle 58 wieder gestartet werden kann,
• eine Magnetscheibe 112 für jedes Kolbenpaar durch Hallsensoren bzw. Lagegeber 113, elektronisch kommutiert wird und eine Steuer- Regelelektronik die Winkelgenaue Drehrichtungsumkehr schaltet,
• für jedes Kolbenpaar eine Zündkerze 42 zur Verfügung steht und deren Zündung mit einem Hallrad mit mindestens zwei Nuten, einem Hallsensor und einer Einzelfunkenspule erfolgt und dass die Verstellung des Zündzeitpunktes über eine Unterdruckdose für beide Zündkerzen gleichzeitig erfolgen kann,
• das Motorkonzept eine Variabilität in der geometrischen Auslegung des Kolbenwinkels und der Kolbenzapfen und damit des Kolbenhubes bzw. Hubverhältnisses und des Verdichtungsraumes bzw. der Verdichtung innerhalb des konstanten Kreissegmentes im Zylinder des Motorgehäuses von 180° Kw ermöglicht,
• die Ausführung des inneren Gehäuse- und Kolbenquerschnittes in runder oder eckiger Form durch das neue Dichtelementkonzept möglich wird,
• mit einer kontinuierlichen in den Kolbenscheiben eingebauten Öldruckumlaufschmierung gleichzeitig eine Kühl- und Abdichtfunktion der Kolben zu den einzelnen Kammern und zum Gehäuseinnenraum erfolgen kann.

The object of the invention is achieved 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 at exactly the position of the TDC between the exhaust and intake ports after each rotation of a 135 ° / 120 ° / 108 ° Kw pair of pistons and the spark plugs are located between two pistons in the BDC ,
• by a new sealing element concept in which the piston pairs have a closed 90 ° crossing closed sealing boundary to the two piston discs and the housing wall, no valves and valve control are required,
• 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 27 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 there is a piston between the two openings,
• this valve is electrically controlled by means of a rotary potentiometer on the accelerator pedal or other actuators and thus the engine power can be additionally influenced by the variable compression,
• in the chamber 28, a further opening 31 is located, which is closed with a check valve 54 and at negative pressure (eg, during the starting process) opens this chamber,
• With the speed sensor 87, an engine management system is made possible that optimally adjusts the power consumption, consumption and CO ₂ emission via a lambda probe.
• a simple engine start-stop function (not only for hybrid drives) to save the Krafistoffverbrauchs Advantageously, it is possible that with standing piston pairs the working shaft together with the energy stored in the flywheel 88 continue to rotate freely and the engine regardless of the rotating shaft 58 to be restarted can
• a magnetic disk 112 is electronically commutated for each pair of pistons by Hall sensors or position encoders 113 and a control electronic control unit switches the angular direction reversal,
• for each pair of pistons, a spark plug 42 is available and the ignition takes place with a Hall wheel with at least two grooves, a Hall sensor and a single spark coil and that the adjustment of the ignition can be done simultaneously via a vacuum box for both spark plugs
• the engine concept allows a variability in the geometric design of the piston angle and the piston pin and thus the piston stroke and the compression space or the compression within the constant circular segment in the cylinder of the motor housing of 180 ° Kw ,
• the execution of the inner housing and piston cross-section in round or square shape is made possible by the new sealing element concept,
• a cooling and sealing function of the piston can be done to the individual chambers and to the housing interior with a continuous built-in the piston discs oil pressure circulation lubrication.

4th embodiment

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

• Fig. 1.1 eine schematische Seitenansicht vom Innenraum des Motors mit der wiederkehrenden Arbeitsposition der Kolbenpaare und der Aufteilung des Ringraumes in vier Kammern,
• Fis. 1.2 einen Teilquerschnitt durch das ringförmige Gehäuse mit den beiden Kolbenscheiben, den Kolben und deren Lagerung im Gehäuse,
• Fig. 2 . 1 einen Gesamtquerschnitt durch die am Motorprinzip beteiligten Komponenten, mit dem Schmierölverlauf an einem Kolbenpaar,
• Fig. 2.2 einen Teilschnitt durch die Zahnrad- Steuerscheibe mit Zahnkranz und Dämpferscheibe sowie die Ansicht der Vorrichtung zur Verriegelung und Positionierung der Kolben im OT und UT,
• Fis. 2.3.2.4 zeigt die Seitenansichten der Zahnrad- Steuerscheibe zur Steuerung der Startermotoren und der Verriegelung mit je zwei 180° Kw gegenüberliegenden Kreissegmenten und die Position der Sensoren im OT,
• Fil!. 2.5- 2.7 einen Teilquerschnitt und die isometrische Ansicht des internen ECM mit dem Rotor (Permanentmagnet), Stator (Elektromagnet) und der bürstenlosen Kommutierung der Magnetscheibe mittels Hallsensoren bzw. Lagegeber,
• Fig. 3.1- 3.10 die Darstellung des Arbeitsprinzips mit Sensorsteuerung über Kreissegmente, Positionsrad und Hallsensor, bei einer Umdrehung beider Kolbenpaare, am Beispiel eines Saugmotors,
• Fig. 3.11 ein Weg-Zeit-Diagramm (s/t-Diagramm) der beiden Kolbenpaare zur Verdeutlichung der abwechselnd gleichgerichteten Drehbewegung und der Übersetzung von 2:3 zur Arbeitswelle,
• Fig. 3.12 ein Arbeitsdiagramm (p/v-Diagramm) der sensorgesteuerten RKB als Saugmotor in Zusammenwirkung der in den einzelnen Kammern entstehenden Druckverlaufes über dem Hubvolumen (Kammervolumen),
• Fig. 4 einen Stromlaufplan, der die Motorsteuerung mit der Zündung, dem Hallsensor und Hallrad, der Verriegelungsvorrichtung mit Hubmagnete, sowie der externen Startermotoren über Kreissegmente durch Sensoren und einem Zündstartschalter aufzeigt,
• Fig. 4 . 1 einen Teilbereich des Stromlaufplanes, der die Motorsteuerung der konventionellen externen Starter mit der Polwendeschaltung für Drehrichtungsumkehr aufzeigt,
• Fig. 5.1-5.7 das Dichtungskonzept der einzelnen Kolben- und Kolbenscheiben mit Kolbenringsegmente und weiteren Dichtelementen für zwei alternative Kolben- bzw. Zylinderquerschnitte,
• Fig. 6 die isometrische Ansicht, der in den Kolbenscheiben integrierten Ölpumpenfunktion mit Pumpenscheiben,
• Fig. 6.1-6.6 die Schnitte und Unteransicht am Kolben mit den Bohrungen zur Schmierung und Kühlung derselben und der als Rückschlagventil eingesetzten Abdeckplatte,
• Fig. 7 die isometrische Ansicht, des Kühlmittelverlaufes in den Gehäuseteilen mit den Ölbohrungen, die in den Gehäuserippen integriert sind,
• Fig. 8 . 1 . 8 . 2 die Gesamtaußenansicht der sensorgesteuerten RKB von links und rechts,
• Fig. 9 die Gesamtaußenansicht der sensorgesteuerten RKB mit zwei internen ECM,
• Fig. 9 . 1 ein Blockschaubild mit der links und rechts von der RKB angeordneten internen ECM, in Funktion eines parallelen Hybridantriebes.

Show it:

• Fig. 1.1 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 in four chambers,
• Fis. 1.2 shows a partial cross section through the annular housing with the two piston discs, the piston and their mounting in the housing,
• Fig. 2 , 1 a total cross section through the components involved in the motor principle, with the lubricating oil flow on a pair of pistons,
• Fig. 2.2 a partial section through the gear control disc with sprocket and damper disc and the view of the device for locking and positioning of the pistons in TDC and UT,
• Fis. 2.3.2.4 shows the side views of the gear control disc for controlling the starter motors and the interlock with two 180 ° Kw opposite circle segments and the position of the sensors in the TDC,
• Fil !. 2.5- 2.7 a partial cross-section and the isometric view of the internal ECM with the rotor (permanent magnet), stator (electromagnet) and the brushless commutation of the magnetic disk by means of Hall sensors or position sensors,
• Fig. 3.1- 3.10 the representation of the working principle with sensor control over circle segments, position wheel and Hall sensor, with a rotation of both piston pairs, the example of a suction motor,
• Fig. 3.11 a path-time diagram (s / t-diagram) of the two piston pairs to illustrate the alternately rectified rotational movement and the translation of 2: 3 to the working shaft,
• Fig. 3.12 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 above the displacement (chamber volume),
• Fig. 4 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 a portion of the circuit diagram showing the motor control of the conventional external starter with the pole reversal reversing circuit,
• Fig. 5.1-5.7 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,
• Fig. 6 the isometric view, the oil pump function integrated in the piston disks with pump disks,
• Fig. 6.1-6.6 the cuts 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,
• Fig. 7 the isometric view of the coolant flow in the housing parts with the oil holes, which are integrated in the housing ribs,
• Fig. 8 , 1 , 8th , 2 the overall external view of the sensor-controlled RKB from left and right,
• Fig. 9 the overall external view of the sensor-controlled RKB with two internal ECM,
• Fig. 9 , 1 a block diagram with the left and right of the RKB arranged internal ECM, in function of a parallel hybrid drive.

According to an advantageous embodiment Fig. 1.1 and Fig. 1 , 2 The motor includes two pairs of 180 ° Kw opposite piston pairs with the piston 1, 2 (Kp a ) and 3, 4 (Kp b ), the interchangeable on each circular piston disk 5, 6 automatically axially at the same distance from the inner wall of the housing 17th , 18 can position. 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 pistons 1 - 4 to the piston disc 5, 6 by means of the piston screw 23 and a piston pin 24th 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 Fig. 5 , 6 and each piston can be supported to transmit 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 base in a base 10 Fig. 5 , 6 , These cross-sections are to four pistons 1 - 4 configured with pin 48 at the end faces. These pistons simultaneously perform a valve and sealing function to the multi-part closed housing 17, 18, 19, to the four chambers 26-29 and to the piston discs. The intake 35 and exhaust port 36 is at the periphery Fig. 1.1 the housing arranged so that a valve control for sealing the openings in the recurrent 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 this shaft is left and right with the claw-shaped teeth 66, 67 an inner clutch disc 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 key 82, the working shaft rotates in the direction of piston rotation.

In the further embodiment, a gear wheel control disc 83, 84 with a ring gear 85, 86, for driving the piston pairs during the starting process of the engine Fig. 2 , 1 , by means of external electric starters 139, 140, and in the internal ECM 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 cummed or detected by three Hall sensors or position encoders 113 distributed around the stator 103 and also attached to the housing cover Fig. 2.5- 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. In addition, on this page, the installation of a V-belt pulley 92 on the outer clutch disc 80 for driving the necessary attachments such as water pump, alternator, refrigerant compressor, etc. is provided.

The working shaft is fixed and centered by two corrugated spring washers or disc springs 90 by means of two nuts 91 (or other suitable fasteners) to the housing in such a way that the outer clutch disc 80, 81 to the inner clutch disc 69, 70 respectively 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 . About 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 pin guide 100, 101 with a locking pin 97 and two stops 105, 106, which are connected to a damper disc 110, 111 . The gear control disc is rotatably stopped relative to the damper disc, 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 are alternately stopped during startup by the backstop 21, 22 in the housing 17, 18 and the sprung Locking device with solenoids can be omitted.

1. a) Alleiniger Fahrzeugantrieb durch RKB (Stand- alone). ECM nur als Startermotor.
2. b) Antrieb mit RKB plus externer E-Motor (seriell, parallel, kombinierter Hybridantrieb)
3. c) Antrieb mit RKB plus wechselseitigen Antrieb durch die beiden internen ECM
   (paralleler Hybridantrieb, Drehmomentaddition).
4. d) Wechselseitiger Generatorantrieb der internen ECM durch die RKB nach dem Start.
5. e) Fahrzeugantrieb durch reinen Batteriebetrieb beider interner ECM.
6. f) Ein rückwirkender Antrieb des Schwungrades 88 durch Bremsenergie kann durch den
   Freilauf 75, 76, der die Arbeitswelle zu den Kolbenpaaren entkoppelt, erfolgen.

With an internal ECM arranged to the left and right of the RKB , the following drive variants are advantageously also present in a vehicle according to the invention Fig. 9, 9 , 1 possible:

1. a) Sole vehicle drive by RKB (stand-alone). ECM only as a starter motor.
2. b) Drive with RKB plus external electric motor (serial, parallel, combined hybrid drive)
3. c) Drive with RKB plus reciprocal drive through the two internal ECM
   (parallel hybrid drive, torque addition).
4. d) Alternate generator drive of the internal ECM by the RKB after the start.
5. e) Vehicle drive by pure battery operation of both internal ECM.
6. f) A retroactive drive of the flywheel 88 by braking energy can by the
   Freewheel 75, 76, which decouples the working shaft to the piston pairs done.

• Fig.3 . 1
  Aus einer beliebigen Position im Gehäuse der Kp a, b zueinander, werden diese vom externen Starter 139, 140 bzw. von der internen ECM nach rechts in die wiederkehrend Arbeitsposition des OT/UT gedreht.
• Fig. 3 . 2
  Das nachfolgende Kp b, a wird vom Kp a, b über Kreissegmente durch zwei Hubmagneten, die eine Verriegelung betätigen oder durch wechselnde Drehrichtungsumkehr der externen Starter Fig. 4, 4 . 1 bzw. der beiden internen ECM Fig. 2.5-2.7, in OT/UT sensitiv gesteuert, festgehalten.
• Fig. 3.3
  Starter 1 dreht Kp a um 90° Kw, erstes Ansaugen des frischen zündfähigen Kraftstoff-Luft-Gemisches, Kp b in OT frei. Druckausgleich durch regelbares Drosselventil 52 in Kammer 26, 27. Das Rückschlagventil 54 gleicht den Unterdruck in Kammer 28 aus.
• Fig. 3 . 4
  Starter 1 dreht beide Kp a, b direkt gegenüberstehend und an den Zapfen maximal berührend um 45° Kw auf die neue Arbeitsposition (gesamt 135° Kw), das Kp b wird im OT freigestellt, das Kp a bleibt stehen.
• Fig. 3 . 5
  Starter 2 dreht Kp b um 90° Kw weiter, das Kp a wird festgehalten, Ansaugen und erstes Verdichten des Kraftstoff-Luft-Gemisches mit Druckausgleich. Das Rückschlagventil 54 gleicht den Unterdruck in Kammer 28 aus.
• Fig. 3 . 6
  Starter 2 dreht Kp a, b um 45° Kw weiter auf die 135° Kw der Arbeitsposition. Es erfolgt die erste Zündung des Kraftstoff-Luft-Gemisches und der erste Arbeitstakt beginnt.
• Fig. 3 . 7
  Durch die Expansionskraft bleibt Kp b stehen, das Arbeitsspiel Ansaugen, Verdichten, Arbeiten und Ausschieben erfolgt durch die Drehung des Kp a um 90° Kw gleichzeitig.
• Fig. 3 . 8
  Beide Kolbenpaare drehen sich durch die Antriebskraft und dem Schwungmoment des Kp a um 45° Kw bis zur Arbeitsposition weiter, der zweite At erfolgt.
• Fig. 3 . 9
  Im zweiten At wird das Kp b um 90° Kw gedreht, die kinetische Energie überträgt sich auf das Kp a. Der Motor läuft selbsttätig.
• Fig. 3.10
  Kp a und b drehen um 45° Kw weiter und haben sich um eine volle Umdrehung aus der Position der Fig. 3.2 weiterbewegt. Die Arbeitsspiele wiederholen sich bis die Zündung abgeschaltet oder mehr Kraftstoff-Luft-Gemisch zugeführt wird.
  Wenn keine weitere Zündung nach Abschaltung des Motors erfolgt, wird der Druck in Kammer 26, 27 durch das geregelte Ventil 52 ausgeglichen und beide Kolbenpaare können sich bis zum Stillstand ungehindert auf der Arbeitswelle weiterdrehen.
• Fig. 3.11
  Das s/t-Diagramm zeigt das Zusammenspiel der intermittierend sich drehenden und angehaltenen Kp a, b im Verhältnis von 2:3 zur Arbeitswelle und die vier entstehenden At nach einer vollen Umdrehung beider Kolbenpaare.
• Fig. 3.12
  Im p/v- Diagramm sind die in den einzelnen Kammern erfolgten Arbeitsspiele Ansaugen, Verdichten, Arbeiten und Ausschieben mit dem Druckverlauf über den Kw von 90° (Kammervolumen VH = Vh+Vc) zusammengefasst.
  Alle in den Kammern befindlichen Gase werden mit dem entsprechenden thermischen Gaszustand (Überdruck, Unterdruck) beim Drehen über einen Kw von 45° gespeichert, bis die Arbeitsposition wieder ereicht wurde und das Arbeitsspiel von Neuem beginnt. Die Reihenfolge der Kammern beginnt wieder von vorne (Kammer 29 wird zur Kammer 26 usw.).

For controlling the ignition timing Fig. 2 , 1 a Hall sensor 130, 131 is provided for each pair of pistons, 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 Hall sensors, is in the Fig. 3.1- 3.10 shown and described below:

• Figure 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, 4th , 1 or the two internal ECMs 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 opposite and at the pin maximum touching 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 , 8th
  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 turn 45 ° Kw and have a full turn out of position Fig. 3.2 advanced. 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.).

• das Dichtungskonzept an Kolben, Kolbenscheiben und Gehäuse
• das Schmierkonzept und
• das Kühlkonzept des Motors

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 disks 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 in the right-angle piston variant Fig. 5.1-5.4 achieved 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. According to the invention, two corrugated springs 175 with three arcs, in a deeper groove in the piston, support the required contact pressure in all directions (see arrows a - h). Fig. 5 , 2 and Fig. 5.3 ) . In the middle 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, two flat oil stripping plates 208, 213 are laterally pressed by two cylindrical springs 209 against the housing wall (see arrows j, k), whereby the excess lubricating oil in the groove 188 via the piston disc through the holes 168, 169 back to the working shaft 58 and then out of the housing.

The circular arc piston variant Fig. 5.5- 5.7 and Fig. 6 , 1 . 6.6 According to the invention is represented by a cross section having a base 10 down. The piston groove 162 is continued horizontally in the socket. The horizontal groove 163 in the base Figure 6 , 3 serves, 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 radially to the adjacent piston disk, which corresponds approximately to that of the piston to the housing Fig. 5.6.

Due to the oil pressure in the main oil flow 199 , of the oil flowing into the bore 197 in the center of the piston, the oil stripping plates 208 , 213 of the oil scrape lubricating ring segments 153 and the oil scraper lubricating 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 also 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 large opening width, so that they overlap with the outer flat sealing elements 166,165, in order to avoid the leakage that might arise from manufacturing tolerances, due to thermal influences 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 bores 68 , the piston discs with the sealing rings 170, 171 are pressed against the inner wall of the housings 17, 18 and the pump discs 215, 216 against the piston disc inner surface, in order 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 backflow, against the forces acting on the oil centrifugal forces from the housing and to maintain the oil circuit, is advantageously an oil pump function Fig. 6 integrated in the piston discs 5, 6 .

• auf einer Seite der Arbeitswelle eine Öldrehdurchführung 89 Fig. 2 . 1 vorgesehen ist, die mit zwei Wellendichtringen 185 abgedichtet und mit zwei Kugellagern 187 auf der Arbeitswelle 58 gelagert wird,
• im Zentrum der Arbeitswelle eine Ölbohrung 190 vorgesehen wird, die bis zu den Kolbenscheiben führt und dass in dieser Bohrung ein Gewinde für die Aufnahme mindestens eines Rückschlagventils 192 (mit Durchfluss in Einschraubrichtung) vorgesehen und die Arbeitswelle an beiden Enden stirnseitig dichtend verschlossen wird,
• weitere Bohrungen 194, 195 radial Fig. 6 das Pumpennutsegment 210, 211 tangierend neben der Kolbenstange 8 aus den Kolbenscheiben 5, 6 herausgeführt werden,
• bei einer alternativen Schraubverbindung der Kolben 1 - 4 zu der Kolbenscheibe Fig. 2 . 5 das Öl über eine zentrale Ölbohrung 194 über das Rückschlagventil 191 (mit Durchflussrichtung entgegen der Einschraubrichtung) durch die Kolbenschraube 23 geführt wird.
• in jedem einzelnen Kolben 1 - 4 die Bohrungen 194, 195 Fig. 6.1- 6.6 mit einer V-förmigen Nut 196 zu einer zentralen, vertikalen Bohrung 197, die am oberen Ende des Kolbens austritt, zusammengeführt werden,
• unter dem Ölabstreif-Schmierringsegment 153 bzw. Schmierelement 160 das Öl in der Nut 198 des Kolbens auf einer Seite über zwei Bohrungen 201 zurück zum Zentrum des Gehäuses fliesen kann und dabei die Gehäuseoberfläche im Nebenstrom 200 geschmiert wird und das Öl im Hauptstrom 199 des Ölabstreif- und Schmierringes gleichzeitig eine zu den benachbarten Kolben abdichtende und kühlende Funktion übernimmt,
• bei der alternativen Schraubverbindung Fig. 2 . 5 der Kolben zur Kolbenscheibe das Öl über den Kolbenbolzen 24 zurück zu den Bohrungen 201 und zu den Öl- Abstreifplatten 208, 213 geführt wird und an dieser Stelle nur das zur Schmierung erforderliche ÖL austreten kann und der Hauptölstrom über die Bohrung 168, 169 zurück zur Arbeitswelle geführt wird,
• sich an jedem Ende des Ölabstreif- Schmierringsegmentes 153 bzw. Schmierelementes 160 eine in den Kolben eingefügte Öl-Abstreifplatte 208, 213 befindet, die auf beiden Seiten der Gehäusewand jeweils das überschüssige Öl im Kolben, durch den Druck der Federn 209 über die V-förmige Nut 203 und die Bohrungen 201, 202 sowie der Bohrung 168,169 Fig. 6 zurück zur Arbeitswelle 58 und aus dem Gehäuse leitet,
• die beiden Gehäuse 17, 18 Fig. 2 . 1 je zwei Bohrungen 204, 205 aufweisen, die es ermöglichen das Öl aus dem Gehäuse herauszuführen, um den Kreislauf zu einem Ölkühler zu schließen,
• die beiden Kolbenscheiben 5, 6 radial und axial mehrere Bohrungen 62 aufweisen, die eine Verbindung zu den axialen Bohrungen 64, 65 der inneren Kupplungsscheiben 69, 70 für die Schmierung der Lagerung zwischen der äußeren/inneren Kupplungsscheiben ermöglichen,
• mit all diesen Maßnahmen alle drehenden Lagerteile mit Öl versorgt werden können.

This is inventively achieved in that

• on one side of the working shaft, an oil rotary duct 89 Fig. 2 , 1 is provided, which is sealed with two shaft sealing rings 185 and stored 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 sealed frontally at both ends,
• further holes 194, 195 radially Fig. 6 the Pumpennutsegment 210, 211 tangentially out of the piston discs 5, 6 led out next to the piston rod 8 ,
• in an alternative screw the piston 1 - 4 to the piston disc Fig. 2 , 5 the oil is passed through the piston screw 23 via a central oil bore 194 via the check valve 191 (with the flow direction counter to the screwing-in direction).
• in each individual piston 1 - 4, the holes 194, 195th Fig. 6.1- 6.6 with a V-shaped groove 196 to a central, vertical bore 197, which emerges 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 simultaneously performs a sealing and cooling function to the adjacent piston,
• in the alternative screw connection Fig. 2 , 5 the piston to the piston disk the oil is passed through the piston pin 24 back to the holes 201 and the oil stripper plates 208, 213 and at this point only the oil required for lubrication can escape and the main oil flow through the bore 168, 169 back to the working shaft to be led,
• at each end of the Ölabstreif- lubricating ring segment 153 and lubricating element 160 is inserted into the piston oil stripper plate 208, 213 , on both sides of the housing wall in each case the excess oil in the piston, by the pressure of the springs 209 on the V-shaped Groove 203 and the holes 201, 202 and the bore 168.169 Fig. 6 back to working shaft 58 and out of the housing,
• the two housings 17, 18th Fig. 2 , 1 each have two bores 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 disks 5, 6 have a plurality of bores 62 radially and axially, which allow a connection to the axial bores 64, 65 of the inner clutch disks 69, 70 for the lubrication of the bearing between the outer / inner clutch disks,
• With all these measures all rotating bearing parts can be supplied with oil.

• die beiden Kolbenscheiben 5, 6 wie auch die Motorkolben relativ zur kontinuierlichen Drehung der Arbeitswelle sich immer nach 90°/60°/36° Kw abwechselnd einmal zu- bzw. auseinander drehen,
• an den beiden Kolbenscheiben radiale Ölbohrungen 186 vorgesehen sind, die in Verbindung zu den zwei Pumpennutsegmenten 210, 211 stehen,
• zwischen den Kolbenscheiben zwei Pumpenringe 215, 216 vorgesehen werden, die breiter sind als die kreisbogenförmigen Nuten und über den Innendurchmesser in einer Vertiefung 217 der Kolbenscheiben geführt werden, diese Pumpenringe mit jeweils zwei Nocken 218, 219 ausgestattet sind, die genau in den Pumpennutsegmenten 210, 211 an einer Seite der Nut anliegen und die so lang sind, dass sie die beiden Ölbohrungen 212 nach einer Drehung um 90°/60°/36° Kw am anderen Ende der Nut abdecken können,
• sich weiterhin an jedem Pumpenring mindestens zwei Mitnehmerbolzen 221, 222 am äußeren Durchmesser der Pumpenringe befinden, die sich übergreifend vom rechten Pumpenring in eine Nut 220 der linken Kolbenscheibe und umgekehrt einfügen und von dieser mitgedreht werden,
• das in den Pumpennutsegmenten 210, 211 befindliche Öl durch die relative Drehung der Pumpenringe und Nocken und durch das sich schließende Rückschlagventil 192, gleichzeitig in alle hierfür vorgesehenen Bohrungen 194 der Kolbenscheibe und der Motorkolben gepresst wird, durch die umgekehrte relative Drehung der Pumpenringe und Nocken eine Saugwirkung entsteht und der Rückfluss des Öles aus der zentralen Bohrung des Motorkolbens beim Ansaugvorgang dadurch verhindert wird, dass erfindungsgemäß für jeden Kolben ein Rückschlagventil 191 in der Bohrung 194 vorgesehen wird Fig. 2 . 5 oder unter jedem Kolben eine Abdichtplatte 224 so dimensioniert und befestigt ist, dass sie einmal die Nut 196, 203 Fig. 6.1, 6.3 im Kolben und mittels zweier kreisbogenförmiger durch Ausklinkung 227 entstehende, bewegliche Laschen 225, 226 beide Bohrungen 194, 195 neben der Kolbenstange 8 abdecken kann,
• die Förderleistung der Ölpumpe durch die Tiefe, Breite und Radius der Pumpennutsegmenten 210, 211 an die Erfordernisse angepasst werden kann.

An oil pump function Fig. 6 According to the invention Advantageously achieved in that

• the two piston disks 5, 6 as well as the engine pistons always alternately turn on and off at 90 ° / 60 ° / 36 ° Kw, relative to the continuous rotation of the working shaft ,
• radial oil bores 186 are provided on the two piston disks, which are connected 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 are guided over the inner diameter in a recess 217 of the piston discs, these pump rings are each equipped with two cams 218, 219, which 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 ° / 60 ° / 36 ° Kw at the other end of the groove,
• continue to be at each pump ring at least two driving pins 221, 222 are located on the outer diameter of the pump rings, which overlap from the right pump ring into a groove 220 of the left piston disc and vice versa and be rotated by this,
• the oil contained in the pump groove segments 210, 211 is forced through the relative rotation of the pump rings and cams and through the closing check valve 192 into all of the piston disc and engine piston bores 194 provided by the reverse relative rotation of the pump rings and cams Suction arises and the backflow of the oil from the central bore of the engine piston during the intake process is prevented by the invention for each piston a check valve 191 is provided in the bore 194 Fig. 2 , 5 or under each piston, a sealing plate 224 is dimensioned and fixed so that it once the groove 196, 203 Fig. 6.1, 6.3 in the piston and by means of two arcuate formed by notching 227 , movable tabs 225, 226 can cover both bores 194, 195 next to the piston rod 8 ,
• the delivery rate of the oil pump through 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 according to the invention Fig. 7 achieved in that both housings 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 seal the space for a flowing cooling medium 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 through three inlet openings 250, 251, 257 opposite to the piston rotation direction leads to the larger heat zone on the exhaust side. The exhaust ports 252, 253, 258 are located after a complete internal 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 partition wall 247 and an opposite rib 248 simultaneously serve to accommodate the required oil holes 204, 205. Each individual piston is advantageously cooled in addition to 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 entire engine concept in the exterior view 50, 60, 45 show the Fig. 8 , 1 . Fig. 8 , 2 and Fig. 9 In the selected installation position, for example, the sensor-controlled RKB according to the invention can be 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

digit description digit description digit description 1 47 93 polarity switch 2 piston 48 spigot 94 3 49 95 Housing cover li 4 50 Exterior left 96 Housing cover right 5 piston disc 51 97 bolt 6 52 adjustable valve 98 solenoid 7 piston pin 53 99 8th piston rod 54 check valve 100 bolt guide 9 sliding block 55 101 10 base 56 102 Rotor ECM 11 threaded hole 57 103 Stator ECM (E-magnet) 12 Set screw 58 working shaft 104 permanent magnet 13 59 105 attack 14 hub 60 Exterior right 106 15 ball-bearing 61 bearings 107 16 62 drilling 108 17 Housing left 63 cyl. feather 109 18 Housing re 64 axial bore 110 damper plate 19 cylinder 65 111 20 112 magnetic disk 21 Backstop, freewheel 67 66 dog clutch 113 Hall sensor, position sensor 22 68 drilling 114 23 piston screw 69 inner clutch disc 115 damper spring 24 Piston pin in the piston 70 116 25 adjusting spring 71 117 26 suction 72 ball-bearing 118 sensor 27 compression chamber 73 119 28 working chamber 74 120 sensor 29 expansion chamber 75 Backstop, freewheel 121 30 Opening 76 122 circular segment 31 77 ball-bearing 123 32 Compressed air line 78 124 33 79 125 sensor 34 80 outer clutch disc 126 35 suction 81 127 36 exhaust port 82 adjusting spring 128 circular segment 37 83 Gear or 129 38 84 control disc 130 Hall sensor 39 85 sprocket 131 40 threaded hole 86 132 carrier disc 41 87 sensor 133 42 spark 88 flywheel 134 43 Fuel injector 89 Oil rotary joint 135 Hall wheel, position wheel 44 90 Disc springs, spring washer 136 45 Exterior view with BGM 91 mother 137 46 92 Keitriemenscheibe 138 ignition switch 139 External starters 191 check valve 243 Partition, rib 140 192 244 O-ring 141 193 245 142 194 drilling 246 143 195 247 Partition, rib 144 Single spark coil, ignition coil 196 V-shaped groove 248 145 197 vertical bore 249 146 198 middle groove 250 inflow 147 battery 199 Oil main stream 251 148 200 Oil sidestream 252 outflow 149 Rod 201 drilling 253 150 Compression ring segment 202 254 151 203 V-shaped groove 255 housing wall 152 204 drilling 256 153 Olabstreif-Schmierringsegm. 205 257 outflow 154 206 258 155 thrust washer 207 259 156 208 Oil stripper 260 console 157 209 Cylindrical spring 261 158 sealing element 210 Pumpennutsegment 262 Exhaust pipe 159 211 263 160 Olabstreif-Schmierringsegm. 212 oil well 264 161 overlap 213 Ol-stripper 265 Frischgas- Stuzen 162 groove 214 266 163 outer horizontal, deeper groove 215 pump ring 267 164 Clearance radial 216 165 overlap 217 deepening Abbreviations 166 Sealing element with chamfer 218 cam RKB Rotary piston internal combustion engine 167 Sealing element, trapezoidal shape 219 168 drilling 220 groove ECM Internal electronically commutated electric motor 169 221 Driving pins 170 222 At strokes 171 seal 223 Aw Working wave directions 172 224 sealing Ah 173 overlapped bump 225 tabs b Kolb width 174 226 d Piston diameter 175 gewelly spring 227 notch dg equivalent diameter 176 228 d: Vh stroke ratio 177 middle groove 229 dg: Vh equivalent stroke ratio 178 straight push 230 seal H piston height 179 outer groove 231 axial sealing ring i. k directions 180 pen 232 n rotation speed 181 233 n / A At per turn 182 horizontal, deeper groove 234 O-rings Kp a Piston pair a 183 overlap 235 Kp b Piston pair b 184 236 kw crank angle 185 Shaft seal 237 OT Top Dead Center 186 radial oil hole 238 R crank radius 187 239 UT bottom dead center 188 Groove in the lubricating element 240 cavity Vc compression chamber 189 241 Vh capacity 190 oil well 242 cavity VH chamber volume

Claims (14)

1. Rotary piston internal combustion engine (RP-ICE) with two piston pairs (a, b), which are each mounted on a respective piston disc (5, 6) and rotate about a central axis in an annular cylinder (19) of a closed housing (17, 18) and in that case drive a working shaft (58), characterised in that the pistons (1 to 4) of the piston pairs (a, b) have a respective pin (48) at each end, that the pistons (1 to 4) as well as two internal electronically commutated starters, generators, motors (ECM) (102 to 104) in external pole mode of construction with a magnetic disc (112) are contactlessly controlled or regulated by sensors (87, 113, 118, 120, 125, 126, 130, 131), that a closed seal boundary crossing the piston discs (5, 6) at 90° is provided and with the help of wavy springs (175) as well as of right-angled sealing elements (158, 159), which are arranged around the circumference of the piston, and trapezium-shaped sealing elements (166, 167) forms, together with piston rings (170 to 172) in the piston discs (5, 6), chambers (26 to 29) - which execute the operating cycles of a four-stroke motor - within the annular cylinder (19) in a repeating working position, that the working shaft (58), together with a flywheel (88) and a gearwheel control disc (83, 84), is conjunctively rotated by the rotating piston pair (a or b) via an oppositely acting, reverse-motion blocking means (75, 76) concentrically mounted between an inner clutch disc (69, 70) and an outer clutch disc (80, 81), or that a rotor (102) of an ECM (102 to 104) with permanent magnets (104) and magnetic disc (112) is used instead of the control disc (83, 84), and that a stator, particularly in the form of an electromagnet (103), is fastened on the two sides of the housing cover (95, 96) concentrically with the working shaft and the rotor with permanent magnets is driven electrically or by the piston pair.
2. Rotary piston combustion engine according to claim 1, characterised in that by the pins an induction chamber is formed at the top dead centre (OT) and a working chamber at the bottom dead centre (UT) as chambers in the working position between the end surfaces of the pistons (1 to 4), that a compression chamber (27) and an expansion chamber (29) are formed at the piston rear side of the piston pairs (a, b) and that an induction port (35) for the supply of fresh fuel/air mixture is provided at the top dead centre (OT) and a spark plug (42) at the bottom dead centre (UT) in the housing (17, 18) and an exhaust gas port (36) is provided in the expansion chamber at a spacing of a piston angle from the top dead centre (OT).
3. Rotary piston combustion engine according to claim 1, characterised in that with a piston angle, i.e. an angular range 45°/60°/72° over which a piston with pin (48) extends, and with the piston stroke (crank angle), i.e. the angular range 90°/60°/36° (crank angle) over which a piston can move, the working position repeats after 135°/120°/108° (crank angle) and that the sum of degrees of angle from two pistons with pins (48) and the piston stroke is always 180° (crank angle).
4. Rotary piston combustion engine according to claim 1 to 3, characterised in that one piston pair (b or a) is moved alternately by the expansion force of the compressed fuel/air mixture ignited by the spark plug (42) at the bottom dead centre (UT) between two pistons in the working chamber (28), whilst the second piston pair (a or b) remains stationary, for at the most over the time period of the rotational movement of 90°/60°/36° (crank angle), due to a return motion blocking means (21, 22) supported in the housing (17, 18) and mounted concentrically on a hub (14) and between the ball bearings (15, 16) and the piston discs, and that in that case the working cycles of a four-stroke motor are executed in the chambers (26 to 29) and thereafter the two piston pairs rotate in common until a new working cycle begins.
5. Rotary piston combustion engine according to claim 2 to 4, characterised in that the two ports (30) are provided in the compression chamber (27) of the annular cylinder (29) and are connected by means of a compressed air duct (32), and that this compressed air duct (32) has an electrically regulable throttling and non-return valve (52) by which compensation can be provided for a pressure drop from the compression chamber (27) to the induction chamber (26) when a piston (1 to 4) is present between the two ports (30), and that a further port (31) is present in the expansion chamber (29), which further port is connected with a non-return valve (54) and opens when sub-atmospheric pressure prevails in this chamber.
6. Rotary piston combustion engine according to claim 1 to 5, characterised in that the control and regulation of the ignition spark for two spark plugs (42) is carried out contactlessly by way of a respective sensor (130, 131), which is mounted on a respective carrier disc (132, 133) connected with a rod (149), wherein the sensor (130, 131) is mounted to be rotatable about a central axis of the housing cover (95, 96) and the timing of the ignition is thereby settable.
7. Rotary piston combustion engine according to claim 1 to 6, characterised in that a rigid connection from a rim gear (85, 86) to the inner clutch disc (69, 70) and piston disc (5, 6) is produced by a mechanically positive axial clutch (66, 67) via the gearwheel control disc (83, 84), or in substitution a rotor (102) with permanent magnets (104) and a magnetic disc (112) of the ECM (102 to 104), and that thereby the piston pairs (a, b) are each electronically commutated, controlled and regulated by a respective external starter (139, 140), which contactlessly detects the piston pairs (a and b) by means of a sensor (118, 120) - which is secured to the housing cover (95, 96) at the top dead centre - by way of two symmetrically arranged outer arc segments (122, 123) or by a respective internal ECM (102 to 104), from a desired position within the annular cylinder (19), or by Hall sensors or position transmitters (113).
8. Rotary piston combustion engine according to claim 7, characterised in that a sensor (125, 126), which is secured to the housing cover (95, 96) at the top dead centre, is switchable by way of two symmetrically arranged inner arc segments (128, 129), wherein when the sensor (125) is switched the stroke magnet (98) or a pole reversing switch (93) of the piston pair (b) is activated, and wherein when the sensor (126) is switched the stroke magnet (99) or a further pole reversing switch (94) of the piston pair (a) is activated, and wherein the stroke magnets (98, 99) actuate two symmetrical locking means or the pole reversing switches (93, 94) or the electronically commutated, controlled and regulated rotor (102) of the ECM (102 to 104) reverses or reverse the rotational direction in alternation, whereby one of the piston pairs (a, b) is stopped.
9. Rotary piston combustion engine according to claim 1 to 8, characterised in that in the case of a piston variant of arcuate cross-section the pistons (1 to 4) have a base (10) and outer grooves (162) of the pistons (1 to 4) have at least two compression ring segments (150, 151) with an opening width corresponding with the width of the two piston discs (5 and 6), and that in the case of a piston variant of right-angled cross-section each of two right-angled sealing elements (158, 159) required for the compression form, in an outer groove (179), sealing boundaries with respect to the cylinder surface, wherein a centre groove (177, 198) for lubrication and assisting the sealing, an oil-stripper lubricating ring segment (153) or two right-angled oil-stripper lubricating elements (160), which overlap (183) with respect to the cylindrical housing (19) and which are components of an oil pressure circulating lubrication, are provided.
10. Rotary piston combustion engine according to claim 9, characterised in that a wavy spring (175) formed with three curves is arranged in the horizontally extending and deeper groove (163, 182, 177, 179) and is supported by the two outer curves in the deeper groove (163, 182, 177, 179), and that through the spring force of the middle curved shape the trapezium-shaped sealing element (167) is pressed and fixed by its end surface and flank surface and at the same time the middle trapezium-shaped sealing ring (172) and the two outer flat sealing elements (166) are pressed and fixed on the end surface of the piston discs (5, 6), and that the two ends of the wavy, horizontally compressed spring can be supported at 45° either directly on the sealing elements (166) or on the section edge or inner edge with respect to the right-angled sealing elements (158, 159) so that a sealing action is given in all directions (a to h; j, k) even at standstill of the piston pairs (a, b).
11. Rotary piston combustion engine according to claim 1 to 10, characterised in that the inner clutch disc (69, 70) together with the gearwheel control disc (83, 84) or the rotor (102) with permanent magnets (104) and magnetic disc (112) is mounted as a unit on the outer clutch disc (80, 81) in the ball bearings (72, 73 and 77, 78), wherein the unit is supported with respect to the housing (17, 18) by means of a slide bearing (61) or a needle bearing in the concentric bore of the piston discs (5, 6) together with the working shaft (58) with small axial play by way of a spring washer (90) and that the outer clutch disc (80, 81) is connected with the working shaft (58) and the flywheel (88) by way of a key (82) and when the piston pair (a and/or b) is stationary is rotatable in one direction relative to the inner clutch disc.
12. Rotary piston combustion engine according to claim 1 to 11, characterised in that as components an oil pressure circulatory lubrication and at least two over-engaging entrainer pins (221, 222) are provided, by means of which, through the movement of the piston discs (5, 6) and the piston pairs (a, b), pump rings (215, 216) arranged between the piston pairs are drivable, which are each equipped with two cams (218, 219) which in pump groove segments (210, 211) of the piston discs (5, 6) bear against an end face of the groove and which are of such a length that after a rotation through 90°/60°/36° of crank angle they cover oil bores (212) at the other end of the groove, and that the sealing function of the piston discs (5, 6) with respect to the housing (17, 18) and the pump discs (215 216) at the inner side of the piston discs is assisted by cylindrical springs (63) in the piston disc (5, 6).
13. Rotary piston combustion engine according to any one of claims 1 to 12, characterised in that for power increase a regulated exhaust-gas turbocharging is made possible by way of a connection from the exhaust gas duct (262) to the fresh gas duct (265) and that induction duct injection and/or compressor charging is or are ensured by way of the fresh gas duct (265) and/or that this motor has a start/stop function by which, when the piston pairs (a, b) are stationary, the working shaft (58) together with the energy stored in the flywheel (88) freely further rotates and the motor can be started again independently of the rotating working shaft (58) and/or that a fuel injection nozzle (43) is arranged in the housing (17, 18) between the spark plugs (42) in the working chamber (28).
14. Rotary piston combustion engine according to any one of claims 1 to 13, characterised in that an operating mode of the rotary piston combustion engine as a stand-alone drive is operable through an internal ECM, which is arranged to the left and right of the engine, with the function of starter, generator and EC motor and a serial, parallel or combined hybrid drive can be realised through an external electric motor, that a parallel hybrid drive can be realised through alternating connection of the two internal ECMs to the rotary piston combustion engine, that sole operation of the internal ECM can be realised when the rotary piston combustion engine is switched off and/or that a reaction drive of the flywheel (88) can be effected through brake energy by the freewheel (75, 76) which decouples the working shaft from the piston pairs.

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