EP2356317B1 - Rotary piston engine, unit with control system and method for the cycle-controlled operation of a rotary piston engine - Google Patents

Description

The invention relates to a rotary engine, an arrangement of a control system and a rotary piston engine and a method for the clock-controlled operation of a rotary piston engine.

From the prior art motors with rotating pistons in a variety of designs are known. In contrast to rotary-piston engines, rotary-piston engines have the property that all rotating components of the engine move in circular paths around a single point.

In contrast to combustion engines with lifting cylinders, which convert a resulting from explosion of a fuel-air mixture lifting movement by means of a crankshaft in a rotary motion, rotary motion is generated directly in rotary engines. For this reason, these engines are characterized by a better displacement-power ratio compared to reciprocating engines.

However, various problems arise especially in rotary engines, which have previously prevented greater market penetration of the same. These are in particular sealing problems inside the combustion chamber and high manufacturing costs due to a complicated mechanical engine structure.

From the GB377380 A a rotary piston engine assembly comprising at least one counter and rotary piston is known, in which the counter-piston is pressed by means of a drive mechanism comprising a spring and an associated rod system directly to the rotary piston in order to achieve the required sealing of the combustion chamber. From the GB151124A and the WO 85/03549 A1 are also already known similar rotary piston engines.

Based on the stated prior art, the present invention based on the object to provide a rotary piston engine with the simplest possible structure and an arrangement of a control system and such a rotary engine and method for the clock-controlled operation of the rotary piston engine, which ensures high efficiency.

The object is achieved by a rotary engine according to claim 1, an arrangement of a control system and a rotary engine according to claim 13and a method according to claim 17 and 19.

The essential aspect of the rotary piston according to the invention is to be seen in that the rotary piston engine consists of a motor housing with a housing interior with inlet and outlet, in which a cylindrical rotor is received in a predetermined direction of rotation rotatable about a rotation axis in a concentric to the axis of rotation cylindrical running surface with the lateral surface of the rotor and lateral webs includes at least one annular in cross-section cylinder, and in which at least one rotary piston is arranged on the lateral surface of the rotor. Furthermore, at least one counter-piston is at least partially accommodated in the motor housing and at least the at least one counter-piston in the motor housing or the at least one rotary piston is movably mounted on the rotor, wherein each counter-piston is assigned at least one inlet with inlet valve and at least one outlet. The at least one outlet is hereby arranged in the direction of rotation immediately before the opposing piston and the at least one inlet in the direction of rotation at the latter, wherein the at least one counter-piston is driven by the rotor via a mechanical control system. It is particularly advantageous that the at least one counter-piston is driven by the rotor via the mechanical control system in such a way that the counter-piston follows the contour of the rotary piston projecting from the rotor in contactlessly with a minimum distance, while the rotor is advantageously designed in one piece. Further, at least two cylinders are provided, wherein in each case a cylinder is formed by the one-piece rotor and a part of the motor housing. The rotary piston and the protruding into the cylinder Part of the counter-piston are approximately identical in shape and the at least one rotary piston and the at least one counter-piston is approximately trapezoidal.

In an advantageous embodiment, the rotary piston and the part of the opposing piston protruding into the cylinder in certain rotary piston positions are approximately identical in form and arranged in the engine such that the remaining space between the rotary piston and the opposed piston is minimized immediately before passing through the rotary piston through the region of the opposing piston.

In a particularly preferred embodiment, the rotary engine has at least two cylinders, wherein the first cylinder is designed as a pressure cylinder for compressing air and the other cylinder as a working cylinder. The pressure cylinder leads compressed air to an accumulator device which has at least two pressure or ignition chambers. In the pressure and ignition chambers, a fuel-air mixture is generated and caused to explode, wherein the pressure resulting from the explosion via a connecting channel between the pressure and ignition chambers and working cylinder is supplied to the same and generates a rotational movement by the pressure in the working cylinder becomes.

According to a further aspect of the invention, an arrangement of a control system and a rotary engine is provided, wherein the preferably mechanical control system for controlling at least one guided in a Gegenkolbengehäuseabschnitt counter-piston of a rotary piston engine is provided, via which the counter-piston is lifted out of the cylinder such that the deck - or side surfaces of the counter-piston protruding from the rotor contour of the rotary piston in its passage contactless with a distance less than 0.5mm, follow, wherein the rotary piston and projecting into the cylinder part of the counter-piston are approximately identical in shape and the at least one rotary piston and the at least an opposing piston are approximately trapezoidal in shape.

Also forms the subject of the invention, a method for the clock-controlled operation of a rotary piston engine consisting of a motor housing with a housing interior. The essential aspect of this method is the fact that by rotating the rotary piston, starting from the counter-piston in the direction of rotation via the inlet into the first cylinder chamber, a fuel-air mixture is sucked in and at the same time the exhaust gas located in the second cylinder chamber from the Vortakt is discharged through the outlet and that during the passage of the rotary piston of the counter-piston is lifted synchronously to the rotary piston from the cylinder and returned to the passage back into the cylinder, in such a way that the radial movement of the counter-piston follows almost exactly the shape of the rotary piston, so that the passage of at least a rotary piston through the region of the at least one counter-piston takes place without contact with a minimum distance.

Another object of the invention is an alternative method for the clock-controlled operation of a rotary piston engine consisting of at least one pressure cylinder and a working cylinder, each comprising at least one motor housing with a housing interior. The essential aspect of the alternative method is to suck in and compress air via the impression cylinder, supply the compressed air to an accumulator device and form fuel-air mixture in the accumulator device of the compressed air, and then supply the fuel in the accumulator device Air mixture is ignited, wherein the resulting by the explosion pressure is supplied to the working cylinder. Here, the pressure storage device is provided separately from the pressure and working cylinder, which has at least two pressure or ignition chambers in which alternately the fuel-air mixture is made to explode.

Further advantageous embodiments of the subject invention can be found in the dependent claims. In addition, developments, advantages and possible applications of the invention also result from the following description of embodiments and from the figures. All described and / or illustrated features are alone or in any combination in principle subject of the invention, regardless of their summary in the claims or their dependency. Also, the content of the claims is made an integral part of the description.

Fig. 1

beispielhaft eine perspektivische Ansicht eines einstückigen Rotors des Drehkolbenmotors mit jeweils zwei gegenüberliegenden Drehkolben und Gegenkolben;

Fig. 2

beispielhaft eine perspektivische Ansicht eines Motorgehäuseteils;

Fig. 2.1

beispielhaft eine perspektivische Schnittdarstellung eines Motorgehäuseteils gemäß Fig. 2;

Fig. 3

beispielhaft eine stirnseitige Draufsicht auf den im Motorgehäuseteil gemäß Fig. 2 aufgenommenen, einstückigen Rotor mit Drehkolben und Gegenkolben;

Fig. 3.1

beispielhaft eine perspektivische Ansicht von zwei aneinander gefügten Motorgehäuseteilen mit eingeschobenem Rotor

Fig. 4.1 bis 4.6

beispielhaft sechs stirnseitige Draufsichten gemäß Figur 2 jeweils bei unterschiedlichen Drehpositionen des Rotors im Motorgehäuse;

Fig. 5

beispielhaft eine schematische Blockzeichnung des Drehkolbenmotors mit Druck- und Arbeitszylinder und einer Druckspeichervorrichtung;

Fig. 6

beispielhaft eine dreidimensionale Schnittdarstellung des Rotor mit an dessen Mantelfläche befestigten Drehkolben und Dichtringen;

Fig. 7

beispielhaft eine dreidimensionalen Ansicht des Rotors mit an der Mantelfläche befestigten Drehkolben und Dichtringen gemäß Fig. 6;

Fig. 8

beispielhaft eine dreidimensionale Darstellung einer Nocke;

Fig. 9

beispielhaft eine dreidimensionale Darstellung einer Nockenschale;

Fig. 10.1 bis 10.6

beispielhaft sechs Teildarstellungen unterschiedlicher Drehzustände der zusammenwirkenden Nocke und Nockenschale;

Fig. 11

beispielhaft eine dreidimensionale Darstellung einer Steuerungseinheit zur Ansteuerung des Gegenkolbens;

Fig. 12

beispielhaft eine perspektivische Darstellung eines Kegelzahnradantriebsmechanismus zum Antrieb des Gegenkolbens über die Steuerungseinheit und

Fig. 13

beispielhaft eine perspektivische Darstellung der Ansteuerung der Einlassventile durch einen Zahnrad-Zahnriemen-Antrieb.

Fig. 14.1, 14.2

beispielhaft eine Vorder- und Rückansicht eines erfindungsgemäßen Drehkolbenmotors in einer perspektivischen Gesamtdarstellung

Fig. 15.1, 15.2

beispielhaft eine Vorder- und Rückansicht eines erfindungsgemäßen Drehkolbenmotors mit Druckspeichereinrichtung in einer perspektivischen Gesamtdarstellung

The invention will be described in more detail with reference to several embodiments and several figures. Show it:

Fig. 1

For example, a perspective view of a one-piece rotor of the rotary piston engine with two opposing rotary pistons and opposed pistons;

Fig. 2

an example of a perspective view of a motor housing part;

Fig. 2.1

by way of example a perspective sectional view of a motor housing part according to Fig. 2 ;

Fig. 3

by way of example a frontal plan view of the in the motor housing part according to Fig. 2 accommodated, one-piece rotor with rotary piston and counter-piston;

Fig. 3.1

an example of a perspective view of two mutually joined motor housing parts with inserted rotor

Fig. 4.1 to 4.6

exemplified six frontal plan views according to FIG. 2 each at different rotational positions of the rotor in the motor housing;

Fig. 5

by way of example a schematic block diagram of the rotary piston engine with pressure and working cylinder and a pressure storage device;

Fig. 6

Example, a three-dimensional sectional view of the rotor with attached to the lateral surface of the rotary piston and sealing rings;

Fig. 7

by way of example a three-dimensional view of the rotor with attached to the lateral surface of the rotary piston and sealing rings according to Fig. 6 ;

Fig. 8

an example of a three-dimensional representation of a cam;

Fig. 9

exemplified a three-dimensional representation of a cam shell;

Fig. 10.1 to 10.6

for example, six partial representations of different rotational states of the cooperating cam and cam shell;

Fig. 11

for example, a three-dimensional representation of a control unit for controlling the counter-piston;

Fig. 12

by way of example a perspective view of a bevel gear drive mechanism for driving the counter-piston via the control unit and

Fig. 13

exemplified a perspective view of the control of the intake valves by a gear-toothed belt drive.

Fig. 14.1, 14.2

by way of example a front and rear view of a rotary piston engine according to the invention in a perspective overall view

Fig. 15.1, 15.2

by way of example a front and rear view of a rotary piston engine according to the invention with pressure storage device in a perspective overall view

FIG. 1 shows a perspective view of a tubular, one-piece rotor 3 with preferably two on the outer surface 3.1 of the rotor 3 firmly screwed rotary pistons 4, 4 'and one with these rotary pistons 4, 4' cooperating opposed pistons 7, 7 'of a rotary piston engine 1 according to the invention. For a better illustration of the construction and the interaction of said components of the rotary piston engine 1 according to the invention, these are shown without the motor housing 2, which surrounds them, preferably multi-part design. The rotor 3 is in this case arranged concentrically to the axis of rotation RA and rotatably mounted in the motor housing 2 in a predetermined rotational direction DR.

Both the two rotary pistons 4, 4 'and the opposed pistons 7, 7' are offset by 180 ° from each other and arranged concentrically about the axis of rotation RA. As a result of this offset, in each case the rotary pistons 4, 4 'or the opposing pistons 7, 7' are located symmetrically with respect to the axis of rotation RA. This reduces the imbalance of the rotor 3 and a low-vibration running of the rotary piston engine 1 is ensured.

FIG. 2 and FIG. 2.1 show at least a portion of the motor housing 2 in a perspective overall or sectional view, said part of the motor housing 2 together with the rotor 3 rotatably mounted therein forms a preferably annular in cross-section cylinder 5. To form a plurality of such preferably circular cross-section in the cylinder 5, a plurality of identical parts of the motor housing 2 may be arranged in series.

The part of the motor housing 2 comprises a circular in cross-section, stepped housing interior 2.1 with a cylindrical, concentric with the axis of rotation RA arranged tread 6 with lateral, circumferential ridges 5.3, which project radially inwardly over the tread 6, so that gradations arise.

The webs 5.3 in turn have at least one side surface 5.3.1 and 5.3.2 an upper side, wherein the side surface 5.3.1 is approximately perpendicular to the tread 6 and the top 5.3.2 is formed circular and concentric with the axis of rotation RA. The part of the motor housing 2 has for receiving and guiding a Opposite piston 7, 7 'at least one opposed piston housing section 12 with a piston guide channel 12.1. In this case, the piston guide channel 12.1 is designed for the radial guidance of the counter-piston 7, 7 'in the counter-piston housing section 12.

FIG. 3 shows a section through the rotary piston engine 1 according to the invention along a plane perpendicular to the axis of rotation RA cutting plane, namely an end view of the arranged in the motor housing 2 rotor 3 with rotary piston 4 and piston 7, which are accommodated in a piston guide channel 12.1 of the piston housing section 12. The in FIG. 1 shown rotor 3 is provided to form two annular in cross-section cylinder 5, that is, a series arrangement of two in FIG. 2 shown parts of the motor housing 2, which, as in Figure 3.1 shown connected to each other at the end face and connected to each other liquid-tight, preferably screwed, are, so that the respective running surfaces 6 come to lie concentrically to the axis of rotation RA.

The rotor 3 is integrally formed and mounted concentrically in the two housing inner spaces 2.1 rotatable about the axis of rotation RA. This results in the housing interior 2.1 each have an annular in cross-section cylinder 5, which is limited in the radial direction by the lateral surface 3.1 of the rotor 3, the tread 6 and in the direction parallel to the rotation axis RA through the mutually facing side surfaces 5.3.1 of the webs 5.3.

In a preferred embodiment, in each case one rotary piston 4, 4 'is provided per cylinder 5, which is moved on a path running concentrically about the axis of rotation RA. In this case, the rotary piston 4, 4 'is running contactless with its free end complied with by the lateral surface 3.1, preferably with a minimum distance on the cylindrical running surface 6. The rotary piston 4, 4' closes by means of seals the cylinder 5 both to the tread 6 and to the rotor 3 and to the side surfaces 5.3.1 of the webs 5.3 liquid and / or airtight, ie the height of the rotary piston 4, 4 'corresponds approximately to the distance between the lateral surface 3.1 of the rotor 3 and the running surface 6 of the motor housing 2 and the depth of the rotary piston 4, 4 ' corresponds approximately to the distance of the opposite side surfaces 5.3.1 two webs 5.3 a cylinder. 5

At least one inlet 2.2 and at least one outlet 2.3 are assigned to the opposing piston housing section 12 provided for receiving the opposing piston 7, 7 ', wherein the at least one outlet 2.3 in the direction of rotation DR immediately before the opposing piston 7, 7' and the at least one inlet 2.2 thereto are arranged. Furthermore, a Zündvorrichtungsöffnung 2.4 may be provided for receiving an ignition device in the motor housing 2, wherein this preferably comes to rest in the direction of rotation DR on the at least one counter-piston 7, 7 'following 120 ° -Sector. In a preferred embodiment, the at least one inlet 2.2 is provided within a 90 ° sector downstream of the counter-piston 7, 7 'in the direction of rotation DR, preferably directly following the counter-piston 7, 7'.

In a preferred embodiment, the rotary pistons 4, 4 'and the part of the counter-piston 7, 7' protruding into the cylinder 5 are approximately identical in shape. The rotary piston 4, 4 'consists of a base surface 4.1 adjoining the lateral surface 3.1 of the rotor 3, a contact surface 4.2 adjoining the running surface 6 with minimal distance and two side surfaces 4.3, 4.4 connecting the base surface 4.1 and the cover surface 4.2. Preferably, the side surfaces 4.3, 4.4 and the base 4.1 include an acute angle. The counter-piston 7, 7 'has due to its approximate uniformity of shape to the rotary piston 4, 4' a top surface 7.1 and two side surfaces 7.2, 7.3, wherein the enclosed by the side surfaces 7.2, 7.3 and the top surface 7.1 angles are each obtuse. This leads both in the case of the counter-piston 7, 7 'and the rotary piston 4, 4' to an approximately trapezoidal cross-section.

Upon rotation of the rotor 3 in the direction of rotation DR, the counter-piston 7, 7 'is lifted out of the cylinder 5 in such a way that a non-contact passage of the rotary piston 4, 4' takes place in the fastening region of the counter-piston 7, 7 '. Preferably, the counter-piston 7, 7 'is lifted out of the cylinder 5 such that the cover 7.1 or

Side surfaces 7.2, 7.3 of the counter-piston 7, 7 'of the protruding from the rotor 3 contour of the rotary piston 4, 4' in its passage contactless and with a minimum distance, preferably a distance less than 0.5mm, follow.

For additional reduction of the distance, in an advantageous embodiment, at least the side surface 4.3, 4.4 of the rotary piston 4, 4 'approaching through the rotation can be slightly convexly curved. In addition, optionally, the at least one side surface 7.2, 7.3 of the counter-piston 7, 7 ', which approaches the rotary piston 4, 4' by its movement, be slightly concave. After passing through the rotary piston 4, 4 ', the opposing piston 7, 7' with its cover surface 7.1 nestles with a minimum distance against the lateral surface 3.1 of the rotor 3. In the case of a closed counter-piston 7, 7 ', ie that the top surface 7.1 is minimally spaced from the lateral surface 3.1 of the rotor 3, the rotary piston 4, 4' divides the annular cylinder 5 together with the counter-piston 7, 7 'in two cylinder chambers. 5 a, 5.b, wherein both rotary pistons 4, 4 'and counter-piston 7, 7' are formed such that the separation by means of the rotary piston 4, 4 'and the opposed piston 7, 7' provided seals preferably liquid and / or airtight he follows. For the sealing of the cylinder 5 on the lateral surface 3.1 of the rotor 3 are attached to this sealing rings 17 (see FIG. 6 and FIG. 7 ) are provided, which fit precisely on the tops 5.3.2 of the webs 5.3.

Based on Figures 4.1 to 4.6 the mode of operation of the rotary piston engine 1 will be described below, with different rotational positions of the rotor 3 in the cylinder 5 being illustrated in six partial images 4.1 to 4.6.

In Figure 4.1 is generated by the rotating in the direction of rotation DR rotary piston 4 in the first cylinder chamber 5.a a suction effect, so that air is sucked through the inlet 2.2. As a result of the rotation of the rotary piston 4, the second cylinder space 5.b decreases at the same time, which results in the exhaustion of a burned exhaust gas located in the second cylinder space 5.b via the outlet 2.3. After a defined rotation angle, the inlet valve is closed at the inlet 2.2, via the fuel supply 9 fuel into the cylinder chamber 5.a fed and brought the fuel-air mixture in the first cylinder chamber 5.a by means of the ignition device to the explosion (see Figure 4.2 ).

Due to the explosion of the fuel-air mixture, a force in the direction of rotation DR is exerted on the rotary piston 4 when the opposing piston 7 is closed and causes a rotation of the rotor 3 in the direction of rotation DR. Immediately before touching the counter-piston 7, 7 'by the rotary piston 4, the volume in the remaining second cylinder chamber is minimal 5.b, ie the burned flue gas from the Vortakt was almost completely pushed through the outlet 2.3 (see Figure 4.3 ). The above-described shape of the side surfaces 4.3, 4.4 and 7.2, 7.3 of the rotary piston 4 and the counter-piston 7 in this case enables a minimization of the volume of the second cylinder subspace 5.b. In order to avoid contact of the rotary piston 4 and the counter-piston 7, the counter-piston 7 is raised approximately synchronously with the rotary piston 4 guided past the cylinder 5 and returned to the cylinder 5 after the passage (see FIGS. 4.4 to 4.6 ). The radial movement of the counter-piston 7 in this case follows almost exactly the shape of the rotary piston 4. This ensures that even when returning the counter-piston 7 into the cylinder 5, the distance between the rotary piston 4 and counter-piston 7 is minimal, with the result that the proportion At burned flue gas in the first cylinder chamber 5.a is also minimal.

As in FIG. 1 and Figure 3.1 already indicated, the rotary engine 1 according to the invention may have a plurality of cylinders 5 arranged in series, with one cylinder per cylinder 5 in each case FIG. 2 illustrated portion of the motor housing 2 is provided and the cylindrical running surfaces 6 are each formed concentrically to the axis of rotation RA. On the rotor 3, a plurality of rotary pistons 4, 4 'are provided depending on the desired number of cylinders, wherein the rotary pistons 4, 4' are offset from each other along the axis of rotation RA and at least one respective rotary piston 4, 4 'is received in a cylinder 5. In order to allow a low-vibration running of the motor, the juxtaposed rotary pistons 4, 4 'alternately rotated by 180 ° to each other on the rotor 3 are arranged. In addition, each rotary piston 4, 4 'associated with an opposed piston 7, 7', wherein also the opposing pistons 7, 7 'offset from each other along the axis of rotation and rotated alternately to each other by 180 °. The ignition of the individual cylinders 5 can take place simultaneously or else offset in time.

In a preferred embodiment, the rotary piston engine 1 according to the invention comprises at least two cylinders 5, wherein one of the at least two cylinders 5 is designed as a pressure cylinder 5.1 for compressing air and the at least one further cylinder 5 as a working cylinder 5.2. Such a rotary engine 1 has separate from the pressure and working cylinders 5.1, 5.2 at least one pressure storage device 10, which includes at least a first and second pressure or ignition chamber 11.1, 11.2.

FIG. 5 shows a schematic block diagram for explaining the operation of a rotary piston engine 1 with pressure and working cylinders 5.1, 5.2 and associated pressure storage device 10. The outlet 2.3 of the pressure cylinder 5.1 is connected via a connecting line 18 to the pressure storage device 10, wherein the connecting line 18 via a check valve 19 on Outlet 2.3 of the printing cylinder 5.1 is connected. The pressure storage device 10 in turn consists of at least a first and second pressure or ignition chamber 11.1, 11.2, which are each coupled via an associated first and second valve 20.1, 20.2 and a common valve 21 to the connecting line 18. The first and second pressure or ignition chambers 11.1, 11.2 have a first and second device for fuel supply 23.1, 23.2 in the first and second pressure or ignition chamber 11.1, 11.2 and in each case a first and second ignition device 24.1, 24.2. On the output side, the first and second pressure or ignition chamber 11.1, 11.2 each with a further valve 22.1, 22.2 coupled to the working cylinder 5.2.

The following is based on FIG. 5 the operation of the rotary piston engine 1 with additional pressure storage device 10 explained in more detail. For better illustration, in FIG. 5 the impression cylinder 5.1 and the cylinder 5.2 shown side by side. The realization of the rotary piston engine 1, however, takes place, as in FIG. 1 shown by a common rotor 3. The position of the rotary pistons 4, 4 'and counter-piston 7, 7' in the pressure cylinder 5.1 and in the working cylinder 5.2 are each offset by 180 ° to each other. During the starting process of the rotary piston engine 1, the rotor 3 is set in rotary motion by a starter, not shown, known from the prior art, wherein in the pressure cylinder 5.1 through the inlet 2.2 air is sucked into the first cylinder chamber 5.a of the pressure cylinder 5.1. As a result of the rotation, the volume in the second cylinder space 5.b of the pressure cylinder 5.1 is compressed and fed via the outlet 2.3 through the connecting line 18 to the pressure storage device 10. When a predefined pressure is reached, the common valve 21 opens and the pressure can reach the respectively downstream first and second pressure or ignition chambers 11.1, 11.2 when the first or second valve 20.1, 20.2 is opened. Subsequently, the first or second valve 20.1, 20.2 is closed again. The first and second valves 20.1, 20.2 are alternately opened, namely each valve 20.1, 20.2 once every two revolutions, so that every other revolution of the first and second valve 20.1, 20.2 associated first and second pressure or Ignition chamber 11.1, 11.2 is pressurized.

After supplying fuel into the first and second pressure or ignition chamber 11.1, 11.2 via a first and second fuel supply 23.1, 23.2, the fuel-air mixture within the first and second pressure or ignition chamber 11.1, 11.2 on the respective first or second ignition device 24.1, 24.2 ignited and at the same time the first or second additional valve 22.1, 22.2 belonging to this pressure or ignition chamber 11.1, 11.2 is opened. At this time, the rotary piston 4 is in the working cylinder 5.2 seen in the direction of rotation DR after the counter-piston 7, said counter-piston 7 is closed, i. with its top surface 7.1 is minimally spaced from the lateral surface 3.1 of the rotor 3.

The resulting in the pressure or ignition chamber 11.1, 11.2 by the explosion pressure is supplied via the connecting channel 25 to the working cylinder 5.2, via its inlet 2.2. As a result, a force in the direction of rotation DR is exerted on the rotary piston 4 in the working cylinder 5.2. At this time, the starter can be switched off. Due to the one-piece design of the rotor 3 also learns the Rotary piston 4 'in the pressure cylinder 5.1 a force in the direction of rotation DR and also generates pressure, which is via the connecting line 18 and an open first and second valve 20.1, 20.2, that of the first or second pressure or ignition chamber not used in the previous cycle 11.1, 11.2 is assigned, in ebendiese pressure or ignition chamber 11.1, 11.2 can spread. After passing through the two rotary pistons 4, 4 'through the region of the counter-piston 7, 7' can in one of the first and second pressure or ignition chamber 11.1, 11.2 by supplying fuel and the subsequent ignition by the first and second ignition device 24.1, 24.2 the fuel-air mixture is exploded again. In the second cylinder subspace 5.b of the working cylinder 5.2 is at this time from the previous cycle resulting, burned flue gas, which is ejected by the rotation of the rotary piston 4 through the outlet 2.3 of the working cylinder 5.2.

The processes described above are periodically recurring, wherein the period of the processes of the rotational speed of the rotor 3 is dependent. In addition, the fuel-air mixture is alternately brought into explosion in one of the first and second pressure or ignition chambers 11.1, 11.2, so that in one of the two pressure or ignition chamber 11.1, 11.2 only every second revolution of the rotor. 3 an explosion occurred. By separating the working cylinder 5.2 from the pressure storage device 10 and the use of two pressure or ignition chambers 11.1, 11.2, the fuel-air mixture can interact with each other for a longer period of time, resulting in better mixing and thus higher efficiency or efficiency the combustion of the rotary piston engine 1 pulls. In addition, such a structured rotary piston engine 1 with gasoline, diesel or gas is operable.

The FIGS. 6 and 7 show in each case the rotor 3 with attached to the lateral surface 3.1 rotary pistons 4, 4 'and sealing rings 17, in a three-dimensional sectional view and a perspective overall view, with the front sides of the rotor 3 preferably circular cover 8 are flanged with paddle wheel-like recesses 8.1. In each case at the cross-sectional center of each cover 8, a shaft 27 is attached, along the axis of rotation RA of the rotor. 3 protrudes, wherein the axis of rotation RA coincides with the wavelength axis. The shafts 27 serve, on the one hand, for the rotatable mounting of the rotor 3 in the motor housing 2 and, on the other hand, for the dissipation of the kinetic energy transmitted to the rotor 3 by the combustion, for example by means of toothed wheels, belts or chains. In addition, by means of these shafts 27 all necessary for the operation of the engine, movable assemblies, such as inlet valve 13, opposed piston 7, 7 ', etc. driven.

Inside the rotor 3, a pipe 26 concentric with the axis of rotation RA is received. This tube 26 is held by the screwed onto both end faces of the rotor 3 cover 8, in the grooves 8.3 provided therein, in its position, the end faces of the rotor 3 are added thereto in the grooves 8.3. By inserting the tube 26 into the rotor 3 results in the interior of the rotor 3, a division into two rotor chambers 28, 29, wherein the first rotor chamber 28 is formed between the rotor inner side and the outer circumferential surface of the tube 26 and the second rotor chamber 29 through the inner The lateral surface of the tube 26 is enclosed. Both the first rotor chamber 28 and the second rotor chamber 29 are bounded laterally by the two covers 8. The construction of lids 8 and a tube 26 arranged inside the rotor serves to create a volume-reduced cooling space adjacent to the heat produced by the combustion, namely the first rotor chamber 28 in order to flow through it with a liquid or viscous medium and thus to cool the rotary engine 1. For this reason, the connection of the cover 8 with the rotor 3 and the connection of the tube 26 with just these lids 8 is made liquid-tight. The second rotor chamber 29 is sealed off from the first rotor chamber 28 and does not come into contact with the cooling medium.

A cooling medium located in the motor housing 2 in front of the cover 8 is supplied with the bores 8.2 on rotation of the rotor 3 via the blade wheel-like recesses 8.1 and introduced into the first rotor chamber 28 through these bores 8.2. The second cover 8 operates in opposite action, ie creates a suction effect on the located in the first rotor chamber 28 cooling medium and conveys the cooling medium through the holes 8.2 and blade-like recesses 8.1 out of the first rotor chamber 28 out. Preferably, the holes 8.2 are inserted obliquely into the cover 8, so that the introduction of the cooling medium is simplified by the blade-like recesses 8.1 through the holes 8.2 in the first rotor chamber 28. The mounted on the lateral surface 3.1 of the rotor 3 rotary pistons 4, 4 'also have cooling channels, said cooling channels have a connection to the first rotor chamber 28, for example via provided with an internal bore screws, for fastening the rotary piston 4, 4' on the rotor 3 are provided. The cooling medium flowing through the first rotor chamber 28 can thus also flow through the rotary pistons 4, 4 'and ensure cooling of the latter, the replacement of the cooling medium being actively supported by the centrifugal force. The cooling medium emerging through the suction effect on the opposite cover 8 can flow back to the first cover 8 via return channels integrated in the motor housing 2. Thus, the motor housing 2, which is acted upon by the combustion process with heat, effectively cooled. In order to avoid overheating of the cooling medium, a well-known from the prior art cooling device is introduced into the cooling circuit, which extracts heat, for example, by a greatly enlarged effective cooling surface of the cooling medium. In addition, this heat can be used for other purposes, such as for heating the fuel or for heating the interior of motor vehicles.

The following is based on the Figures 8-12 a control system according to the invention for controlling at least one guided in the opposed piston housing portion 12 opposed piston 7, 7 'of a rotary piston engine 1 described.

By means of the control system, the above-described radial movement of the counter-piston 7, 7 'is controlled such that during the passage of a rotary piston 4, 4' through the Gegenkolbengehäuseabschnitt 12 of the counter-piston 7, 7 'is lifted out of the cylinder 5, that at a minimum distance from each other a contact of the rotary piston 4, 4 'and the counter-piston 7, 7' is avoided. For this purpose, each counter-piston 7, 7 'of the rotary piston engine 1, a control unit 40, 40' assigned, which are driven by rotating shafts 41, with these Waves 41 each at least one cam 42 and at least one, preferably two cam shells 43 are mechanically connected. The shaft 41 is driven by a mechanical operative connection from the rotor 3 and thus sets both cam 42 and cam shells 43 in rotation.

The in the FIGS. 10.1 to 10.6 each cam 42 shown in the installed state and cam shells 43 are in FIG. 8 respectively. FIG. 9 shown in a perspective view. The cam 42 has a substantially circular outer contour 42.1 with a bulge 42.2, wherein the cam 42 is scanned continuously on its outer surface by a bolt 44, that is, the bolt 44 follows the shape of the cam 42. The bulge 42.2 here is asymmetrical and has a flat or a steep flank.

In the FIG. 9 shown cam shell 43 has a front side milling on, this milled direction predetermines a circumferential path for a bolt 45 and this way, except for a radially outwardly projecting bulge region 50, is approximately circular. The width of the milled recess of the cam shell 43 is matched to the diameter of the bolt 45, so that it is made to fit in the milled recess. In a preferred embodiment, the bolt 45 is guided between two uniform camshells 43, wherein the front-side milled recesses of the cam shells 43 and the cam shells 43 are mutually congruent and spaced from each other.

Upon rotation of the shaft 41 and thus the cam shells 43 in FIG. 11 the bolt 45 moves from the inner and outer contour 43.1, 43.2 of the cam shell 43 from. In the bulge region 50 of the inner or outer contour 43.1, 43.2, a lever mechanism 48 is raised against the spring force of the first spring unit 46, with the lever mechanism 48, an opposing piston 7, 7 'is coupled and this is thus also lifted from the cylinder 5 , In the event that exactly one rotary piston 4, 4 'is arranged in a cylinder 5 of the rotary piston engine 1, the rotor 3 and the shaft 41 have the same rotational speed, ie the transmission ratio between rotor 3 and shaft 41 is 1: 1. This will be the Opposite piston 7, 7 'lifted by the control unit 40, 40' exactly once per revolution of the rotor 3 from the cylinder 5. The cam 42 is coupled to the lever mechanism 48 indirectly via a second spring unit 47.

In the six partial views 10.1 - 10.6 different rotational states of the cam 42 and cam shell 43 are shown, wherein the relative position of the cam 42 to the cam shell 43 is in each case unchanged. In the Figures 10.1 - 10.6 is the cam 42 and the outer surface extending bolt 44 shown by solid lines, the inner contour 43.1 and 43.2 outer contour of the cam shell 43 and the guided between the inner contour 43.1 and outer contour 43.2 bolt 45 are drawn in dashed lines. The rotation of the shaft 41, the cam 42 and the cam shell 43 is clockwise. The cam 42 and the congruent camshells 43 are slightly offset from each other in their bulges 42.2, 50, ie the bulge 42.2 of the cam 42 is in the direction of rotation slightly ahead of the bulge region 50 of the cam shells 43.

In FIG. 10.1 represents the initial situation in which the first and second spring unit 46, 47 are relaxed. In Figure 10.2 is the bolt 45 in the direction of rotation before passing through the bulge portion 50 of the cam shells 43. To facilitate the passage through the bulge region 50, the bolt 44 is raised by the flat edge of the bulge 42.2 of the cam 42 before this pass, so that the second Spring unit 47 is biased. However, the force exerted by the second spring unit 47 on the lever mechanism 48 force still leads to no lifting out of the opposed piston 7, since the outer contour 43.2 of the cam shell 43 effectively prevents this. Upon further rotation of the cam 42 and the cam shells 43, the second spring unit 47 is further biased ( FIG. 10.3 ). Now runs the bolt 45 in the cam shell 43 in the bulge region 50 ( Figure 10.4 ), the already biased second spring unit 47 allows the easier inlet of the bolt 45 in the same, since the lever mechanism 48 is lifted by the prestressed second spring unit 47. This leads to a lifting out of the counter-piston 7, 7 'from the cylinder 5 and indeed one Lifting out as given by the contour of the inner and outer surface 43.1, 43.2 of the cam shell 43 in the respective rotational position.

After the entry of the bolt 45 into the bulge region 50, the bolt 44 passes through the sharply falling flank of the bulge 42. 2 of the cam 42 (FIG. Figure 10.5 ). As a result, the second spring unit 47 relaxes. At the end of the bulge region 50, the bolt 45 is guided out of the bulge region 50 by the spring unit 46 which is preloaded during lifting, and thus the opposing piston 7, 7 'is returned to the cylinder 5 via the lever mechanism 48 (FIG. Figure 10.6 ). The interaction of the cam 42 with the cam shell 43 ensures a gentle material overcoming areas of greater slope, especially when entering the bulge region 50, in which the counter-piston 7, 7 'must be quickly lifted from the cylinder 5 to the shape of the rotary piston. 4 4 'to follow with minimal distance. In addition, the lever mechanism 48 has a gear ratio generated by different lever arm lengths, which converts a small stroke movement caused by the cam shell 43 into an enlarged stroke movement on the opposing piston 7, 7 '.

Figures 12 and 13 show the rotary engine 1 according to the invention in a front and rear view. In FIG. 12 the valve control is omitted for better illustration.

FIG. 12 shows the drive of the control unit 40, 40 'for opposed pistons 7, 7' via a bevel gear mechanism. A fixed to the shaft 27 first bevel gear 60 drives second bevel gears 61 which are articulated at first ends of connecting shafts 64, wherein longitudinal axes of these connecting shafts 64 are perpendicular to the axis of rotation RA. At the second ends of the connecting shafts 64 are mounted third bevel gears 62 which mesh with fourth bevel gears 63 which are connected to and drive the shafts 41. By this arrangement, the shafts 41 are set in a rotational movement by the rotation of the rotor 3, wherein the axes of the shafts 41 are approximately parallel to the axis of rotation RA and spaced therefrom. The direction of rotation of the shafts 41 is the direction of rotation DR of the shaft 27 opposite. By using bevel gears 60-63 with different diameters, the gear ratio can be suitably selected, in particular the preferred gear ratio 1: 1, ie one revolution of the rotor 3 leads to a rotation of the shafts 41st

FIG. 13 shows the control of the intake valves 13 by a toothed belt drive toothed belt. The drive takes place on the opposite side of the bevel gear mechanism of the rotary piston engine 1. On the shaft 27, a gear 51 is fixed in the two other gears 52 engage. At these gears 52 pulleys are mounted frontally, which drive a toothed belt 54. By means of this toothed belt 54 further pulleys 53 are driven, which drive the intake valves 13 via shafts 55 and cams 56. Depending on the number of rotary pistons 4, 4 'used in a cylinder 5, the gear ratio between the rotational speed of the rotor 3 and the rotational speed of the shaft 55 must be suitably selected. When using a rotary piston 4, 4 'per cylinder 5, the speed ratio between the shaft 27 and shaft 55 is also 1: 1.

FIGS. 14.1, 14.2 and FIGS. 15.1, 15.2 each show a rotary engine 1 according to the invention in a front and rear view in the assembled state. Both rotary piston engines 1 have, for example, two cylinders 5, wherein the two cylinders 5 of the rotary piston engine 1 in the FIGS. 14.1, 14.2 a combustion process takes place. The rotary engine 1 in FIGS. 15.1, 15.2 has in contrast to a pressure cylinder 5.1 and a working cylinder 5.2 and an accumulator device 10 and is therefore also suitable for the combustion of diesel fuel.

The rotary engine 1, for example, to drive machines, motor vehicles o.ä. serve. For this purpose, the shaft 27 is coupled via a mechanical operative connection with the drive mechanism of a machine or a motor vehicle, wherein the mechanical operative connection can be made directly or indirectly via a transmission with fixed or variable ratio. As materials for the production of the engine, all commonly used in engine construction materials use Find. The motor can be made mostly of aluminum, in particular all housing parts, the rotor 3 and the lid. 8

LIST OF REFERENCE NUMBERS

1

Rotary engine

2

motor housing

2.1

Housing interior

2.2

inlet

2.3

outlet

2.4

Ignition device opening

3

rotor

3.1

Lateral surface of the rotor

4, 4 '

rotary pistons

4.1

Base of the rotary piston

4.2

Top surface of the rotary piston

4.3, 4.4

Side surface of the rotary piston

5

cylinder

5.a

first cylinder space

5.b

second cylinder space

5.1

pressure cylinder

5.2

working cylinder

5.3

web

5.3.1

Side surface of the bridge

5.3.2

Top of the dock

6

tread

7, 7 '

opposed piston

7.1

Top surface of the opposing piston

7.2, 7.3

Side surface of the opposing piston

8th

cover

8.1

blade-like recess

8.2

drilling

8.3

groove

9

fuel supply

10

Pressure storage device

11.1

first pressure or ignition chamber

11.2

second pressure or ignition chamber

12

Opposed piston housing section

12.1

Piston guide channel

13

intake valve

17

seal

18

connecting line

19

check valve

20.1, 20.2

first and second valve

21

common valve

22.1, 22.2

more valves

23.1, 23.2

fuel supply

24.1, 24.2

first and second ignition device

25

connecting channel

26

pipe

27

wave

28

First rotor chamber

29

Second rotor chamber

40, 40 '

control unit

41

wave

42

cam

42.1

circular outer contour of the cam

42.2

Bulge of the cam

43

cam shell

43.1

Inner contour of the cam shell

43.2

Outer contour of the cam shell

44

bolt

45

bolt

46

First spring unit

47

Second spring unit

48

lever mechanism

49

hanger

50

Auswölbungsbereich

51

gear

52

Gear with front pulley

53

pulley

54

toothed belt

55

wave

56

cam

60

First bevel gear

61

Second bevel gear

62

Third bevel gear

63

Fourth bevel gear

64

connecting shaft

RA

axis of rotation

DR

direction of rotation

Claims (19)

1. A rotary piston engine consisting of an engine housing (2) with a housing interior (2.1) with at least one inlet (2.2) and at least one outlet (2.3), in which in a specified rotation direction (DR) rotatably about a rotation axis (RA) a cylindrical rotor (3) is received in a cylindrical running surface (6) running concentrically to the rotation axis (RA), which running surface encloses with the lateral surface (3.1) of the rotor (3) and lateral webs (5.3) at least one cylinder (5) which has the shape of a circular ring in cross-section, in which at least one rotary piston (4, 4') is arranged on the lateral surface (3.1) of the rotor (3), wherein at least one counter piston (7, 7') is received at least partially in the engine housing (2), at least the at least one counter piston (7, 7') is movably mounted in the engine housing (2) or the at least one rotary piston (4, 4') is movably mounted on the rotor (3), and at least one inlet (2.3) with inlet valve (13) and at least one outlet (2.3) are associated with each counter piston (7, 7' , in which the at least one outlet (2.3) is arranged in rotation direction (DR) immediately in front of the counter piston (7, 7') and following the latter the at least one inlet (2.2) is arranged in rotation direction (DR), wherein the at least one counter piston (7, 7') is driven via a mechanical control system by the rotor (3), characterized in that the at least one counter piston (7, 7') is driven via the mechanical control system by the rotor (3) such that the counter piston (7, 7') follows the contour of the rotary piston (4, 4'), projecting from the rotor (3), in a contactless manner during its passage with minimal distance, that the rotor (3) is constructed in one piece and at least two cylinders (5) are provided, wherein respectively a cylinder (5) is formed by the single-piece rotor (3) and a part of the engine housing (2), that the rotary piston (4, 4') and the part of the counter piston (7, 7') projecting into the cylinder (5) are approximately identical in shape, and that the at least one rotary piston (4, 4') and the at least one counter piston (7, 7') are constructed approximately in a trapezoidal shape.
2. The rotary piston engine according to Claim 1, characterized in that the at least one inlet (2.2) is arranged within a 90° sector in connection with the counter piston (7, 7') directly after the counter piston (7, 7'), and/or that the counter piston (7, 7') or the rotary piston (4, 4') are movable radially to the cylindrical running surface (6).
3. The rotary piston engine according to Claim 1, characterized in that the at least one rotary piston (4, 4') is securely connected to the rotor (3) and has a base surface (4.1) adjoining the rotor (3), a cover surface (4.2) adjoining the running surface (6), and two lateral surfaces (4.3, 4.4) connecting the base surface (4.1) or respectively the cover surface (4.2), wherein respectively one lateral surface (4.3, 4.4) forms with the base surface (4.1) an acute angle and/or that the at least one counter piston (7, 7') has a cover surface (7.1) adjoining the rotor (3) and two lateral surfaces (7.2, 7.3) adjoining the cover surface, wherein the angles formed respectively by a lateral surface (7.2, 7.3) and the cover surface (7.1) are obtuse.
4. The rotary piston engine according to one of the preceding claims, characterized in that the at least one counter piston (7, 7') forms an almost tight separation in particular positions of the rotary piston (4, 4') in the space delimited between the lateral surface (3.1) of the rotor (3), the cylindrical running surface (6) and the webs (5.3).
5. The rotary piston engine according to Claim 3 or 4, characterized in that at least one lateral surface (4.3, 4.4) is curved in a convex manner, wherein the lateral surfaces (7.2, 7.3) of the at least one counter piston (7, 7') are curved in a concave manner.
6. The rotary piston engine according to one of the preceding claims, characterized in that at least two cylinders (5) and on the one-piece rotor (3) at least two rotary pistons (4, 4') are provided, wherein the rotary pistons (4, 4') are offset to one another along the rotation axis (RA), at least in each case one rotary piston (4, 4') is received in a cylinder (5) and the cylinders (5) have a common symmetry axis, which lies in the rotation axis (RA), wherein the at least two rotary pistons (4, 4') lying adjacent to one another are arranged rotated through 180° to one another.
7. The rotary piston engine according to Claim 6, characterized in that at least two cylinders lying adjacent to one another have at least in each case one rotary piston (4, 4') and at least in each case one counter piston (7, 7'), wherein both the rotary pistons (4, 4') and also the counter pistons (7, 7') are offset to one another along the rotation axis (RA) and are rotated through 180° to one another.
8. The rotary piston engine according to one of the preceding claims, characterized in that in the engine housing (2) an ignition device, acting in the at least one cylinder (5), is provided, at namely in the 120° sector following the at least one counter piston (7, 7') in rotation direction of the rotor (3).
9. The rotary piston engine according to Claim 6, characterized in that at least two cylinders (5) are provided, wherein one of the at least two cylinders (5) is constructed as a pressure cylinder (5.1) for the compressing of air and the at least one further cylinder (5) is constructed as a working cylinder (5.2).
10. The rotary piston engine according to Claim 9, characterized in that separate from pressure cylinder (5.1) and working cylinder (5.2) at least one pressure storage device (10) is provided, which has at least two pressure- or respectively ignition chambers (11.1, 11.2), wherein the pressure cylinder (5.1) supplies air alternately to one of the at least two pressure- or respectively ignition chambers (11.1, 11.2).
11. The rotary piston engine according to Claim 10, characterized in that suitable arrangements are provided at the at least two pressure- or respectively ignition chambers (11.1, 11.2), which at particular positions of the at least one rotary piston (4, 4') supply liquid and/or gaseous fuel alternately to one of the at least two pressure- or respectively ignition chambers (11.1, 11.2), and ignite this if applicable, wherein a connecting duct (25), closable by further valves (22.1, 22.2), is provided between the at least two pressure- or respectively ignition chambers (11.1, 11.2) and the working cylinder (5.2), which diverts into the working cylinder (5.2) the pressure occurring in a pressure- or respectively ignition chamber (11) by explosion of the fuel/air mixture.
12. The rotary piston engine according to one of the preceding claims, characterized in that at the two end faces of the rotor (3) covers (8) with impeller-like recesses (8.1) and bores (8.2) are provided, which exert a pumping effect on a liquid or viscous fluid, serving for cooling, and transport the medium through provided ducts into all regions of the rotary piston engine (1) which are to be cooled.
13. An arrangement of a control system and of a rotary piston engine (1) according to one of the preceding claims, wherein the control system is constructed for the activation at least of one counter piston (7, 7'), guided in a counter piston housing section (12), of the rotary piston engine (1), characterized in that the counter piston (7, 7') is lifted out from the cylinder (5) such that the cover- (7.1) or respectively lateral (7.2, 7.3) surfaces of the counter piston (7, 7') follow the contour, projecting from the rotor (3), of the rotary piston (4, 4') on its passage in a contactless manner with a distance less than 0.5 mm, wherein the rotary piston (4, 4') and the part of the counter piston (7, 7') projecting into the cylinder (5), are approximately identical in shape and the at least one rotary piston (4, 4') and the at least one counter piston (7, 7') are constructed approximately in a trapezoidal shape.
14. The arrangement according to Claim 13, characterized in that the activation of the counter piston (7, 7') is realized exclusively through mechanical assemblies and/or that the counter piston (7, 7') is lifted out from the cylinder (5) by the action at least of one cam bowl (43) and at least one cam (42) on a lever mechanism (48) connected to the counter piston (7, 7').
15. The arrangement according to Claim 14, characterized in that the at least one cam bowl (43) acts directly, the at least one cam (42) acts via at least one spring arrangement (47) indirectly via a common lever mechanism (48) on the counter piston (7, 7') and/or that exclusively the inner or respectively outer contour (43.1, 43.2) of the cam bowl (43) determines the stroke movement of the counter piston (7, 7') and/or that the at least one cam (42) supports the stroke movement of the counter piston (7, 7') determined by the at least one cam bowl (43), and namely at locations of great incline of the inner contour (43.1) of the at least one cam bowl (43).
16. The arrangement according to Claim 14 or 15, characterized in that the lever mechanism (48) increases the stroke movement, generated by the at least one cam bowl (43), by means of a transmission ratio.
17. A method for the synchronous operation of a rotary piston engine (1) according to one of Claims 1 to 12, in which for division of the cylinder (5), which has the shape of a circular ring in cross-section, into a first and a second cylinder chamber (5.a, 5.b), the counter piston (7, 7') is introduced radially into the cylinder (5), in which by rotating of the rotary piston (4, 4') starting from the counter piston (7, 7') in rotation direction (DR) via the inlet (2.3) into the first cylinder chamber (5.a) a fuel/air mixture is drawn in and at the same time the exhaust gas, situated in the second cylinder chamber (5.b) from the pre-cycle is ejected via the outlet (2.3) and that during the passage of the rotary piston (4, 4') the counter piston (7, 7') is lifted synchronously to the rotary piston (4, 4') out from the cylinder (5, 5'), and after the passage is directed back into the cylinder (5) again, and namely such that the radial movement of the counter piston (7, 7) follows almost exactly the shape of the rotary piston (4, 4'), so that the passage of the at least one rotary piston (4, 4') through the region of the at least one counter piston (7, 7') takes place in a contactless manner with minimal distance.
18. The method according to Claim 17, characterized in that after reaching a predetermined rotation angle, the fuel/air mixture situated in the first cylinder chamber (5.a) is brought to explosion by an ignition device.
19. The method for the synchronous operating of a rotary piston engine (1) according to one of Claims 1 to 12, consisting of at least one pressure cylinder (5.1) and a working cylinder (5.2), in which air is drawn in and compressed via the pressure cylinder (5.1), in which the compressed air is delivered to a pressure storage device (10), in which for the formation of a fuel/air mixture in the pressure storage device (10) fuel is delivered to the compressed air and subsequently in the pressure storage device (10) the fuel/air mixture is ignited and in which the pressure occurring through the explosion is delivered to the working cylinder (5.2), wherein the pressure storage device (10) is provided separate from pressure cylinder (5.1) and working cylinder (5.2), which has at least two pressure or respectively ignition chambers (11.1, 11.2), in which the fuel/air mixture is alternately brought to explosion.

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