EP1682749B1 - Rotary piston thermal engine device - Google Patents

Abstract

A rotary piston heat engine system is composed of two units. Each includes two pistons mounted for movement in opposite directions. Each piston is mounted for rotation in a cylinder. The longitudinal axes of the pistons and cylinder are collinear. The pistons are mounted for movement in opposite directions. Effective cylinder displacements are formed in each case between two radial boundary surfaces of the two respective pistons which execute an angular motion relative to each other when the engine is operating. At least one mechanism superimposes a circular motion on the angular motion of the two pistons, and each unit includes a shaft for driving a torque-producing device. The system also includes a heater, a heat storer and a cooler connected to a pipe system by which the inlet ports and outlet ports of the displacements of the cylinders of the units are connected to each other.

Description

The invention relates to a rotary piston heat engine device composed of two units, each with two mutually movably mounted pistons, which are rotatably mounted in each case a cylinder, wherein the longitudinal axes of the piston and the cylinder are collinear, and the pistons are mounted so that they are mutually movable, wherein a plurality of effective displacements between each two radial interfaces of the two respective pistons is formed, which perform during operation of the motor with respect to each other a swinging motion, wherein at least one means is provided which causes the swinging motion to a circular movement of both Flask is superimposed, each unit containing a respective rotational force output device driving shaft, and wherein a heater, a heat storage device and a cooling device in Connection are provided with a pipe system through which inlet slots and outlet slots of the cylinder displacements of the units are interconnected.

As rotary engines, for example Wankel engines are known. In these motors, a piston formed with a plurality of rounded surfaces is mounted in a cylinder whose inner wall is not circular, but has a plurality of concave recesses. The combustion chambers of this engine are in each case formed between the rounded surfaces of the piston and corresponding recesses of the cylinder. The disadvantage of the Wankel engine is mainly its complicated assembly, which requires a high production cost. Another problem is the sealing of the engine. Even very small leaks lead to a reduction in engine performance, an increase in the toxic components in the exhaust gases and increased fuel and oil consumption.

A rotary engine of the aforementioned type is known from DE 197 40 133.3-15. This rotary engine has a displacement which is increased over that of the Wankel engine and has the advantage that its combustion chambers are easily sealed, easily filled and emptied, and the expansion energy of the combustion gases or working gases to a high proportion of kinetic Energy is being transformed.

Furthermore, so-called Stirling engines are known in the prior art. These are heat engines in which at least one piston reciprocally mounted in a cylinder moves through gases is whose temperature is cyclically changed by a heater, a heat storage device and a cooling device. A disadvantage of such engines are heat losses due to the cyclic temperature changes of the gases in connection with difficult to produce sealability of the gases, due to the prevailing in the engines high pressures. The life of such engines is also very limited due to high load and associated rapid wear of the engine components. The efficiency of most previously known Stirling engines is also limited by the efficiency of the regenerator in a physical way.

The object of the invention is to develop a based on the principle of the Stirling engine rotary piston heat engine device of the type mentioned so that an adaptation to a plurality of different operating conditions such as different temperature and pressure conditions in the cylinders is possible, so that the applications of the Device are extended. This is equivalent to the task, a rotary piston heat engine device of the type mentioned in such a way that an increased efficiency is given at a predetermined operating condition, i. with the device according to the invention on the one hand a more effective operation over the known devices, on the other hand, but also an active control of engine performance is possible.

For a rotary engine of the aforementioned type, this object is achieved in that a compensation element is provided, which in a possible phase shift at the timing of the two units causes a position compensation of the respective pistons of the two units, thereby causing an optimized phase response.

Preferred embodiments of the invention are the subject of the dependent claims.

In the rotary piston heat engine device according to the invention is characterized in that a compensation element is provided which causes a positional compensation of the respective pistons of the two units at a possible phase shift in the timing of the two units, thereby causing an optimized phase response, that a Device is provided, in which a torque shift between the two units is possible via a phase shift of the timing of the two units concerned. The device according to the invention further has the important advantage over the prior art that in a predetermined manner an arbitrary rotational angle positioning of a respective piston of the units is made possible, so as to obtain an optimization of the efficiency or the performance of the motor device.

In the following, first, the construction and the function of the rotary piston heat engine device according to the invention will be explained, followed by an explanation of the structure and the function of the claimed compensating element followed.

In comparison to conventional Stirling engines, the engine according to the invention has a simpler structural design. To regulate the engine control, no Parts such as valves, camshaft or crankshaft needed. All the main parts of the engine have easy to sand cylindrical surfaces and can be manufactured with high precision at low cost. The sealing of the engine also presents no problems. With conventional sealing elements, a virtually absolute tightness can be achieved. This makes it possible to reduce the manufacturing costs considerably. Other advantages of the engine are its small dimensions, a particularly effective design of a regenerator, the gas flow and the optimization possibilities by Hubgeschwindigkeitsänderungen, and targeted flow disturbances.

The engine according to the invention is a rotary piston engine operating in a cyclic process, which can optionally be equipped with a plurality of work spaces.

According to a preferred embodiment of the rotary piston engine according to the invention, two units consisting of pistons, cylinders and cylinder end faces are connected to one another by a control device.

Preferably, two pistons each having two piston wings are provided in each unit of the engine according to the invention, wherein four working spaces are formed between the respective boundary surfaces of the total of four piston wings of each unit, and four double operations are provided in one revolution of the working shaft.

Preferably, in the engine according to the invention different masses of the piston by recesses and / or additional masses on the piston and / or the gears balanced. This increases the smooth running of the engine and reduces the load on the components.

Preferably, in the rotary piston engine according to the invention in each unit, the axis of the one piston is formed as a solid rod and the axis of the other piston formed as a hollow rod, whose clear diameter is dimensioned so that the solid rod of a piston is movably mounted in its collinear '. This ensures that a mutual mobility of the two pistons is made with collinear axes in a simple and at the same time robust.

The device for effecting a circular motion superimposed on the oscillating motion (approximately 60 °) of the pistons preferably has six oval gearwheels whose main axes are arranged in pairs perpendicular to one another. In this case, two oval gearwheels each perpendicular to one another are preferably each assigned to one cylinder, and the two other oval gears arranged perpendicular to one another are assigned to a working shaft for outputting the engine power. The four oval gears of the cylinders are in each case connected to corresponding, each standing perpendicular to them standing oval gears of the working shaft. It is particularly advantageous if the axis of the one piston is connected to a first oval gear and the axis of the other piston is connected to a second oval gear, said oval gears are collinear arranged behind one another and the main axes of these oval gears perpendicular to each other. In this case, preferably the first and second oval gear are connected to each other via a third and fourth oval gear, wherein the third and fourth oval gear are collinear arranged on an axis, wherein the major axes of the third and fourth oval gear perpendicular to each other.

Preferably, each unit is associated with a plurality of inlet and outlet slots.

Preferably, the two cylinders of the engine according to the invention on differently sized and differently arranged cylinder wall sections between the respective inlet and outlet openings. In a first cylinder of the engine according to the invention is preferably provided between a first inlet slot of a Einlaßschlitzpaares and a first adjacent outlet slot of Auslaßschlitzpaares a cylinder wall which spans only a few angular degrees, and provided between the same inlet slot of the Einlaßschlitzpaares and another Auslaßschlitz the Auslaßschlitzpaares a cylinder wall, the ca 60 degrees.

In a second cylinder of the engine according to the invention further preferably between a first inlet slot of a pair of inlet slits and a first adjacent outlet slot of Auslaßschlitzpaares a cylinder wall is provided which spans about 30 degrees, and provided between the same inlet slot of the Einlaßschlitzpaares and another outlet slot of the Auslaßschlitzpaares a cylinder wall, which also spans about 30 degrees.

The asymmetry between the inlet and outlet ports of the first cylinder and the second cylinder causes in the engine according to the invention a timely transport of the working gas from one cylinder to another. This process generates the power of the engine.

Preferably, the respective angular position of the slots is provided so that it coincides with the position of the respective combustion chamber, which is formed by the respective boundary surfaces of the respective sections of the piston wings, so that a timely filling or emptying of the working spaces is effected.

The boundary surfaces of the pistons are preferably likewise designed in a straight line, with equal distances being provided between adjacent parts of opposing boundary surfaces of the pistons.

With the straight-line design of the inlet slot and the outlet slot in conjunction with a straight-line formation of the boundary surfaces of the piston causes a vibration behavior of the piston within the cylinder, in which the respective working chambers expand so that first in a first cycle of the first piston by approx. Swinging 60 ° in the direction forward, and the second piston oscillates about 120 ° in the direction forward, whereupon in a second cycle, the first piston swings about 120 ° in the direction forward and the second piston by about 60 ° in the forward direction swings.

Accompanied with this vibration behavior is a formation of the respective first and second oval gear such that the ratio of the length of the longitudinal axis to the length of Broad axis of each gear is about 1.7: 1. Alternatively, it is possible to form a gear pair around, and in compensation to provide the other gear pair with a ratio of the length of the longitudinal axis to the length of the wide axis of about 3.5: 1.

For a desired change in Hubwinkelbereichs a change in the ovality of the gears must be made, and the inlet and outlet slots are adapted to the piston interfaces.

In the case of the motor according to the invention, the first and second oval gearwheels are preferably connected to one another via a third and fourth oval gearwheel, which are arranged colinearly one behind the other on an axis and whose main axes are perpendicular to one another.

In the engine according to the invention, the boundary surfaces of the pistons are preferably formed in a straight line such that in each case equal distances are predetermined between adjacent parts of opposing boundary surfaces of the pistons.

In the engine according to the invention, the respective angular position of the inlet openings is preferably provided so that they each coincide with the position of the respective displacement, which is formed by the respective boundary surfaces of the respective sections of the piston wings, so that a timely correct filling of the working chambers is effected.

In the engine according to the invention, the respective angular position of the outlet openings is preferably so provided that it corresponds in each case with the position of the respective displacement, which is formed by the respective boundary surfaces of the respective sections of the piston wings, so that a timely emptying of the working chambers is effected.

In the engine according to the invention, for example, the four mutually movably mounted pistons are preferably rotatably mounted in two different cylinders.

In the case of the engine according to the invention, for the purpose of an effective and rapid reduction in activity or increase in activity corresponding to a force reduction or force increase of the engine, it is advantageous to provide a bridging line between a hot line and a cold line of the motor according to the invention, which can be activated or deactivated via a valve device.

According to a further preferred embodiment of the engine according to the invention, a pipe connections between the displacements is designed as a two-circuit system.

The hot line and the cold line of the pipe system can be carried out separately in the engine according to the invention.

The engine according to the invention can have the structural design of a valve-controlled Stirling engine without additional components.

The working gas in the engine according to the invention preferably always assumes the same flow direction in a respective pipe section.

The motor according to the invention can be used with the supply of mechanical energy as a heat pump.

The motor according to the invention is also usable as a chiller with the supply of mechanical energy.

The motor according to the invention can also be used as a Vuilleumiermaschiene.

In the following structure and function of preferred embodiments of the compensating element according to the invention will be explained.

According to a first preferred embodiment of the device according to the invention it is provided that the compensation element is discretely adjustable. This has the advantage that a phase change of the respective pistons of the two units can be carried out with simple structural means. The compensating element can be formed, for example, by a toothed belt placed around the shafts of the two units, which toothed belt is mounted displaceably for one compensating operation by one or more teeth.

Preferably, the compensation element is in this case formed by a fixing device in which the respective driving a rotational force output device shafts of the units are mounted fixed in different positions, wherein in each of these positions a meshing of the gears of the torque output device is ensured with the respective gears of the waves. In this case, the fixing device is preferably of a gearbox or a holding plate is formed in which the respective driving the shaft of a torque output device of the units are mounted fixed in different positions, wherein in each of these positions a meshing of the gears of the torque output device is ensured with the respective gears of the waves.

The respective shafts of the units driving a torque output device are preferably arranged at a fixed angle of 135 ° or 125 ° to each other, each shaft being associated with a respective bore A, A 'or B, B' for each of these angular arrangements.

According to a second preferred embodiment of the device according to the invention it is provided that the compensation element is continuously adjustable. As a result, a very rapid phase change of the respective pistons of the two units and an associated change in performance of the device according to the invention is made possible. Furthermore, an engine braking is thereby made possible by a sufficiently large false phase shift is brought about by means of a controllable adjusting device.

In this embodiment, the compensating element is preferably formed as two displaceable rollers, which are arranged between the two rotational force output devices of the two units and drivingly connected via a toothed belt with the rotational force output means, wherein the displaceable rollers at mutually changeable distance in a direction perpendicular to the line connecting the rotational force output devices reciprocally are displaceable. The two sliding rollers can be designed in particular as eccentric rollers.

Preferably, it is provided that a first inlet slot of a diametrically opposed first inlet slot pair of a first cylinder and a first outlet slot of a diametrically opposed first Auslaßschlitzpaares the first cylinder 1 ° to 5 ° separated from each other and a second inlet slot of the diametrically opposed first inlet slot pair and a second outlet slot of the diametrically opposed first pair of outlet slots are separated at an angular distance of about 55 ° to 95 °. As a result, an energy-optimized operation of the device according to the invention is made possible.

In particular, preferably, a first inlet slot of the diametrically opposed first inlet slot pair and a first outlet slot of the diametrically opposed first outlet slot pair are separated by 4 °.

Also particularly preferably, a second inlet slot of the diametrically opposed first inlet slot pair and a second outlet slot of the diametrically opposed first outlet slot pair are separated from each other at an angular distance of about 77 °.

Preferably, it is also provided that a first inlet slot of a diametrically opposed second inlet slot pair of a second cylinder and a first outlet slot of a diametrically opposed second pair of outlet slots of the second cylinder are spaced apart angularly from about 25 ° to 45 ° and a second inlet slot of the diametrically opposed second inlet slot pair and a second outlet slot of the diametrically opposed second outlet slot pair are angularly spaced from about 30 ° to 60 ° apart from each other to allow energy-optimized operation of the device according to the invention.

More preferably, a first inlet slot of the diametrically opposed second inlet slot pair and a first outlet slot of the diametrically opposed second outlet slot pair are separated by an angular distance of about 34 °.

Also particularly preferably, a second inlet slot of the diametrically opposed second inlet slot pair and a second outlet slot of the diametrically opposed second outlet slot pair are separated by an angular distance of about 47 °.

According to an important preferred embodiment of the device according to the invention it is provided that all inlet slots and outlet slots are formed in the cylinder head of a respective cylinder.

According to a further preferred embodiment of the device according to the invention it is provided that the two units are arranged so that a part of the A device, from which the rotational force of the rotary piston engine is removable, operated by both units, and a heater, a heat storage device and a cooling device are provided in connection with a pipe system through which inlet slots and outlet slots of the displacements of the at least one cylinder of the units are interconnected ,

The rotary piston heat engine device according to the invention is particularly suitable for use as a heat pump or as a cooling machine with the supply of rotational energy to the torque output devices.

Fig. 1

eine bevorzugte Ausführungsform der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung einschließlich Wärmetauschern und Rohrverbindungen, in einer ersten Arbeitsstellung, in einer Querschnittsansicht;

Fig. 1a

die in Fig. 1 dargestellte Ausführungsform der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer anderen Arbeitsstellung, ebenfalls in einer Querschnittsansicht;

Fig.2

die Zylinder der in Fig. 1 dargestellten Kreiskolben-Wärmemotor-Vorrichtung in einer, teilweisen gebrochenen Ansicht von schräg oben;

Fig.2a

eine erste Kolbenhälfte eines Zylinders der in Fig. 1 dargestellten Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht von schräg unten;

Fig.2b

eine zweite Kolbenhälfte eines Zylinders der in Fig. 1 dargestellten Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht von schräg oben;

Fig.3

ein funktionales Blockdiagramm der in Fig. 1 dargestellten Kreiskolben-Wärmemotor-Vorrichtung;

Fig.4

eine weitere bevorzugte Ausführungsform der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer ersten Arbeitsstellung, in einer Querschnittsansicht;

Fig.4a

die in Figur 4 dargestellte erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer anderen Arbeitsstellung, in einer Querschnittsansicht;

Fig.5

die beiden Zylinder einer erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung gemäß Fig. 1 oder Fig. 4, in einer Querschnittsansicht, aus der die relative Lage der Kolbenwellen und der Drehkraftabgabeeinrichtung erkennbar ist;

Fig.6

eine Tabelle mit Anlagen 1 bis 4, aus der die Zustandsänderungen des Arbeitsgases während eines Schwingzyklusses der Motorvorrichtung ersichtlich sind;

Fig.7

eine erste Anlage zur in Figur 6 dargestellten Tabelle zur Verdeutlichung der Taktung eines Arbeitsgases;

Fig.8

eine weitere Anlage zur in Figur 6 dargestellten Tabelle zur Verdeutlichung der Taktung eines Arbeitsgases;

Fig.9

eine weitere Anlage zur in Figur 6 dargestellten Tabelle zur Verdeutlichung der Taktung eines Arbeitsgases;

Fig.10

eine weitere Anlage zur in Figur 6 dargestellten Tabelle zur Verdeutlichung der Taktung eines Arbeitsgases;

Fig. 11

eine erste bevorzugte Ausführungsform einer diskreten Verstelleinrichtung der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht von hinten;

Fig.12

eine zweite bevorzugte Ausführungsform einer diskreten Verstelleinrichtung der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht von schräg vorne; observiere dabei Welle 5

Fig. 12A

die Wellen der in Figur 12 dargestellten bevorzugten Ausführungsform der diskreten Verstelleinrichtung der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht von hinten; observiere dabei Welle 5

Fig.13

eine erste bevorzugte Ausführungsform einer kontinuierlichen Verstelleinrichtung der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht von hinten;

Fig.14

die Zylinderköpfe einschließlich Einlassschlitzen und Auslassschlitzen eines ersten Zylinders der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht in Richtung des Pfeils P in Figur 13;

Fig. 14A

die Zylinderköpfe einschließlich Einlassschlitzen und Auslassschlitzen des ersten Zylinders der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Querschnittsansicht;

Fig. 14B

die Zylinderköpfe einschließlich Einlassschlitzen und Auslassschlitzen des ersten Zylinders der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht in Richtung des Pfeils P' in Figur 13;

Fig.15

die Zylinderköpfe einschließlich Einlassschlitzen und Auslassschlitzen eines zweiten Zylinders der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht in Richtung des Pfeils P in Figur 13;

Fig.15A

die Zylinderköpfe einschließlich Einlassschlitzen und Auslassschlitzen des zweiten Zylinders der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Querschnittsansicht;

Fig. 15B

die Zylinderköpfe einschließlich Einlassschlitzen und Auslassschlitzen des zweiten Zylinders der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht in Richtung des Pfeils P' in Figur 13;

Fig.16

eine Temperatur-Einheit TA der in Figur 11 dargestellten bevorzugten Ausführungsform einer diskreten Verstelleinrichtung der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Querschnittsansicht;

Fig. 17

die Einheiten I und II einschließlich Ausgleichselement (Riemen 120 einschließlich Riemenräder 32, 32') der in Figur 11 dargestellten bevorzugten Ausführungsform einer diskreten Verstelleinrichtung der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht von schräg hinten;

Fig.18

die Einheiten I und II mit ihren jeweiligen miteinander thermisch gekoppelten Temperatur-Einheit TA und TB der in Figur 11 dargestellten bevorzugten Ausführungsform einer diskreten Verstelleinrichtung der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht von vorne;

Fig. 18a

die Einheiten I und II mit ihren jeweiligen miteinander thermisch gekoppelten Temperatur-Einheit TA und TB der in Figur 11 dargestellten bevorzugten Ausführungsform einer diskreten Verstelleinrichtung der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht von oben;

Fig. 18b

die Einheiten I und II mit ihren jeweiligen miteinander thermisch gekoppelten Temperatur-Einheit TA und TB der in Figur 11 dargestellten bevorzugten Ausführungsform einer diskreten Verstelleinrichtung der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Seitenansicht;

Fig.19

eine Einheit II der Temperatur-Einheit TB einer diskreten Verstelleinrichtung der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Explosionsansicht;

Fig.20

eine Einheit I einer Temperatur-Einheit TA einer diskreten Verstelleinrichtung der erfindungsgemäßen Kreiskolben-Wärmemotor-Vorrichtung in einer Ansicht von schräg oben;

The rotary piston heat engine device according to the invention will be explained below with reference to preferred embodiments, which are illustrated in the figures of the drawing. Show:

Fig. 1

a preferred embodiment of the rotary piston heat engine device according to the invention including heat exchangers and pipe joints, in a first working position, in a cross-sectional view;

Fig. 1a

the embodiment of the rotary piston heat engine device according to the invention shown in Figure 1 in another working position, also in a cross-sectional view.

Fig.2

the cylinders of the rotary piston heat engine apparatus shown in Figure 1 in a, partially broken view obliquely from above.

2a

a first piston half of a cylinder of the rotary piston heat engine device shown in Figure 1 in a view obliquely from below.

2b

a second piston half of a cylinder of the rotary piston heat engine device shown in Figure 1 in a view obliquely from above.

Figure 3

a functional block diagram of the illustrated in Figure 1 rotary piston heat engine apparatus.

Figure 4

a further preferred embodiment of the rotary piston heat engine device according to the invention in a first working position, in a cross-sectional view;

4a

the illustrated in Figure 4 according to the invention rotary piston heat engine device in another working position, in a cross-sectional view;

Figure 5

the two cylinders of a rotary piston heat engine device according to the invention according to FIG. 1 or FIG. 4, in a cross-sectional view, from which the relative position of the piston shafts and the torque output device can be seen;

Figure 6

a table with Appendices 1 to 4, from which the changes in state of the working gas during a swing cycle of the engine device can be seen;

Figure 7

a first system for the table shown in Figure 6 to illustrate the timing of a working gas;

Figure 8

a further Appendix to the table shown in Figure 6 to illustrate the timing of a working gas;

Figure 9

a further Appendix to the table shown in Figure 6 to illustrate the timing of a working gas;

Figure 10

a further Appendix to the table shown in Figure 6 to illustrate the timing of a working gas;

Fig. 11

a first preferred embodiment of a discrete adjustment of the rotary piston heat engine device according to the invention in a view from behind;

Figure 12

a second preferred embodiment of a discrete adjustment of the rotary piston heat engine device according to the invention in a view obliquely from the front; observe wave 5

Fig. 12A

the waves of the illustrated in Figure 12 the preferred embodiment of the discrete adjusting device of the rotary piston heat engine device according to the invention in a view from behind; observe wave 5

Figure 13

a first preferred embodiment of a continuous adjustment of the rotary piston heat engine device according to the invention in a view from behind;

Figure 14

the cylinder heads including inlet slots and outlet slots of a first cylinder of the rotary piston heat engine device according to the invention in a view in the direction of arrow P in Figure 13;

Fig. 14A

the cylinder heads including inlet slots and outlet slots of the first cylinder of the rotary piston heat engine device according to the invention in a cross-sectional view;

Fig. 14B

the cylinder heads including inlet slots and outlet slots of the first cylinder of the rotary piston heat engine device according to the invention in a view in the direction of the arrow P 'in Figure 13;

Figure 15

the cylinder heads including inlet slots and outlet slots of a second cylinder a rotary piston heat engine device according to the invention in a view in the direction of arrow P in Figure 13;

15A

the cylinder heads including inlet slots and outlet slots of the second cylinder of the rotary piston heat engine device according to the invention in a cross-sectional view;

Fig. 15B

the cylinder heads including inlet slots and outlet slots of the second cylinder of the rotary piston heat engine device according to the invention in a view in the direction of the arrow P 'in Figure 13;

Figure 16

a temperature unit TA of the preferred embodiment shown in Figure 11 a discrete adjustment of the rotary piston heat engine device according to the invention in a cross-sectional view;

Fig. 17

the units I and II including compensation element (belt 120 including pulleys 32, 32 ') of the illustrated in Figure 11 the preferred embodiment of a discrete adjustment of the rotary piston heat engine device according to the invention in a view obliquely from behind;

Figure 18

the units I and II with their respective thermally coupled temperature unit TA and TB of the illustrated in Figure 11 the preferred embodiment of a discrete adjustment of the rotary piston heat engine device according to the invention in a view from the front;

Fig. 18a

the units I and II with their respective mutually thermally coupled temperature unit TA and TB that shown in Figure 11 preferred embodiment of a discrete adjustment of the rotary piston heat engine device according to the invention in a view from above;

Fig. 18b

the units I and II with their respective mutually thermally coupled temperature unit TA and TB of the illustrated in Figure 11 the preferred embodiment of a discrete adjustment of the rotary piston heat engine device according to the invention in a side view;

Figure 19

a unit II of the temperature unit TB of a discrete adjusting device of the rotary piston heat engine device according to the invention in an exploded view;

fig.20

a unit I of a temperature unit TA of a discrete adjusting device of the rotary piston heat engine device according to the invention in a view obliquely from above;

In the rotary piston heat engine device 100 according to the invention shown in Figures 1 to 10 are two pistons 1, 2 rotatably mounted in a cylinder 3, wherein the axes of symmetry 14, 15 of the piston 1, the piston 2 and the cylinder 3 are aligned collinear. The axis 6 of a piston 1 is formed as a solid rod 6, and the axis 7 of the other piston 2 is formed as a hollow rod, whose clear diameter is dimensioned so that the solid rod 6 is rotatably mounted in the hollow rod 7. The pistons 1, 2 each have boundary surfaces 10, 20, wherein between adjacent parts of opposing boundary surfaces 10, 20 are each predetermined equal distances. Between the respective Boundaries 10, 20, a plurality of effective displacement chambers 8, 9, 11, 12 is formed, which are bounded on the outside by the cylinder 3, and at the ends by the cylinder head 33 and the cover plate 30.

Furthermore, in the rotary piston heat engine device 100 according to the invention shown in FIGS. 1 to 6, two pistons 1 ', 2' are rotatably mounted in a cylinder 3 ', the axes of symmetry 14', 15 'of the piston 1', of the piston 2 '. and the cylinder 3 'are collinearly aligned. The axis 6 'of the one piston 1' is formed as a solid rod 6 ', and the axis 7' of the other piston 2 'is formed as a hollow rod whose diameter is dimensioned so that the solid rod 6' rotatable in the hollow rod. 7 'is stored. The pistons 1 ', 2' each have boundary surfaces 10 ', 20', wherein between adjacent parts of opposing boundary surfaces 10 ', 20' respectively equal distances are given. Between the respective boundary surfaces 10 ', 20' is a plurality of effective displacement chambers 8 ', 9', 11 ', 12' is formed, which outwardly through the cylinder 3 ', and at the ends by the cylinder head 33' and the cover plate 30 ' are limited.

The two cylinders of the engine device according to the invention have differently dimensioned and differently arranged cylinder wall sections between the respective intake and exhaust ports. In a first cylinder of the engine according to the invention, a cylinder wall is provided between a first inlet slot of a Einlaßschlitzpaares and a first adjacent outlet slot of Auslaßschlitzpaares, which spans only a few angular degrees, and between the same inlet slot Einlaßschlitzpaares and another outlet slot of Auslaßschlitzpaares a cylinder wall provided, which spans about 60 degrees of angle.

In a second cylinder of the engine device according to the invention, a cylinder wall is provided between a first inlet slot of a Einlaßschlitzpaares and a first adjacent outlet slot of Auslaßschlitzpaares, which spans only about 30 degrees, and provided between the same inlet slot of the Einlaßschlitzpaares and another outlet slot of the Auslaßschlitzpaares a cylinder wall, the also spans about 30 angular degrees.

The asymmetry between the inlet and outlet ports of the first cylinder and the second cylinder cause a timely transport of the working gas from one cylinder to another such that the engine is able to provide a working power.

A device 110 shown in Figure 2 causes in the rotary piston heat engine device 100 according to the invention, that the oscillatory movement of the pistons 1 and 2, and the piston 1 'and 2', a circular motion is superimposed.

The device 110 has six oval gears 101, 102, 103, 104, 101 'and 104', whose major axes 111, 112, 113, 114, 111 'and 114' are arranged in pairs perpendicular to each other. In the device 110, the axis 7 of the other piston 2 is connected to a first oval gear 101, and the axis 6 of the one piston 1 is connected to a second oval gear 104, wherein these oval gears 101, 104 are arranged in collinear succession and the main axes 111, 114 of these oval gears 101, 104 are arranged perpendicular to each other. The first oval gear 101 and the second oval gear 104 are connected to each other via a third oval gear 102 and a fourth oval gear 103, wherein the gears 102 and 103 are arranged in collinear succession on a shaft 5, wherein the respective main axes 112, 113 the gears 102, 103 are arranged perpendicular to each other.

Furthermore, in the device 110, the axis 7 'of the other piston 2' is connected to a first oval gear 101 ', and the axis 6' of the one piston 1 'is connected to a second oval gear 104', these oval gears 101 ', 104 'are arranged collinear one behind the other and the main axes 111', 114 'of these oval gears 101', 104 'are arranged perpendicular to each other. The first oval gear 101 'and the second oval gear 104' are connected to each other via a third oval gear 102 and a fourth oval gear 103, wherein the gears 102 and 103 are arranged in collinear succession on a shaft 5, wherein the respective main axes 112 , 113 of the gears 102, 103 are arranged perpendicular to each other.

With such an arrangement, the gears 102 and 103 and the shafts 5 ', 5 "of the two units (cylinders 3, and 3') are operated, the shaft 5 described above being shown in two separate units of temperature, and therefore in one first temperature unit as a shaft 5 'and designated in a second temperature unit as a shaft 5 ".

Such an arrangement applies for example to an assembly, as shown in Figures 3, 12 and 12a.

Another type of assembly is shown in Figures 11, 13 and 16 to 18b. Be Hirbei 8 as Ovalzahnräder ausgefürte non-circular gears (101, 102, 103, 104, 101 ', 102', 103 ', 104') on the shafts 5 'and 5 ", as well as a link (clutch, timing belt, chain o. Ä.) Linked together

The oval gears 101 to 104 and 101 'and 104' have a ratio of 1.7 / 1 with respect to the length of their longitudinal axes to that of their transverse axes.

During operation of the rotary piston heat engine device 100 according to the invention causes an expansion of a heated working gas, for example, in the displacement of the cylinder 3 3, a movement of the pistons 1, 2 in the direction away from each other. The connected to the axis 7 of the piston 2 oval gear 101 moves in the direction of that arrow, which is shown in Fig. 2 on its surface. In the starting position shown in Fig. 2 causes a rotation of the gear 104 by a small angular deflection a relatively large angular deflection of the arranged on the shaft 5 gear 103. The also arranged on the shaft 5 gear 102 transmits this movement to that with a further increase in the Angle deflection of the axis 7 of the piston 2 connected gear 101st

The different, changing local power transmission of the gears 101 rsp. 104 causes in that the oscillation movement of the pistons 1, 2 is superimposed by a circular movement. The working shaft 5 rotates at the average rotational speed of the two pistons 1 and 2. At the extension of the working shaft 5 or 5 'or 5 ", the rotational energy of the motor with constant angular velocity is removable Removable per revolution four times changing angular velocity, as is desirable for example for operating compressors.

The same applies to the unit of the cylinder 3 '.

Fig. 1 and 1a show an embodiment of the engine device according to the invention, in which two cylinders 3, 3 'with respective piston pairs 1, 2 or 1', 2 'via eih corresponding pipe system 201, 201', 202, 202 ', 203, 203rd 'and 204, 204' via a heater 300, a radiator 400 and a regenerator or heat exchanger 200 are coupled together.

At the beginning of a working cycle, working gas heated by the heater 300 flows via the pipe system 202, 202 'into the inlet openings 130, 130' of the cylinder 3. The hot working gas subsequently flows into the intermediate space between the pistons 1, 2, whereby these pistons are forced apart. Thereby, the gap between the piston surfaces of the pistons 1, 2, which are located in the vicinity of the outlet openings 140, 140 'of the cylinder 3, compressed, so that the working gas located there through the pipe system 203, 203' escapes. About the pipe system 203, 203 ', the leaked from the cylinder 3 working gas via a heat exchanger 200, arrives it gives off its heat, via a cooler 400, where it is further cooled, in the pipe system 204, 204 'of the cylinder 3'.

From the pipe system 204, 204 'passes the now cooled working gas through the inlet ports 131, 131' of the cylinder 3 'in the vicinity of these inlet openings located between the pistons 1' and 2 ', these piston interspaces are increased, and the spaces , which are adjacent to the respective opposite piston surfaces of the piston 1 ', 2', are reduced, so that the working gas located there is pressed through the outlet ports 141, 141 'from the cylinder 3' in the pipe system 201, 201 '. Via the pipe system 201, 201 ', this working gas continues to flow through the regenerator or heat exchanger 200, where it absorbs heat from the working gas which flows from the pipe system 203, 203' through the heat exchanger 200.

After exiting the heat exchanger 200, the now heated working gas originating from the pipe system 201, 201 'continues to flow through a heater 300, in which it is further heated. From there it flows into the pipe system 202, 202 ', from where the cycle repeats itself.

In the Stirling engine according to the invention shown in FIGS. 4 and 4a, two cylinders 3, 3 'are coupled to one another via a corresponding pipe system via two heaters 300 or 300', two regenerators or heat exchangers 200, 200 'and two coolers 400 or 400' ,

At the beginning of a rotation cycle of this engine, working gas heated by the respective heaters 300, 300 'flows via the respective tubes 202, 202 'in the inlet openings 130, 130' of the cylinder 3. About the inlet ports 130, 130 'enters the hot working gas in the underlying spaces between the pistons 1, 2, and pushes these pistons apart. As a result, the spaces between the pistons 1, 2 formed by the respective opposite piston surfaces 10, 20 are compressed, and the working gas located there is via the outlet openings 140, 140 'in the respective. Tubes 203, 203 'pressed.

The working gas forced into the pipe 203 passes in sequence through the regenerator 200 and the radiator 400 into the pipe 204 which opens into the inlet port 131 of the cylinder 3 ', and the working gas forced into the pipe 203' passes through the regenerator 200 'and the radiator 400 'in the tube 204', which opens into the inlet opening 131 '. The entering into the inlet port 131 of the cylinder 3 'working gas has thus given off a portion of its heat to the regenerator 200 and is then further cooled by the radiator 400, so that it is present at the inlet port 131 with respect to the tube 203 greatly lowered temperature.

The applied at the inlet port 131 'working gas has given a large part of its heat to the regenerator 200' and is then further cooled by the radiator 400 'so that it at the inlet port 131' of the cylinder 3 'opposite the tube 203' in strong cooled form is present. Through the inlet ports 131, 131 'of the cylinder 3' thus enters cold working gas in the located below these inlet openings spaces between the piston 1 'and 2', wherein the spaces between This piston can be increased and the respectively by the opposite piston surfaces 10 ', 20' of the piston 1 ', 2' formed intermediate spaces, which are located below the outlet openings 141, 141 'of the cylinder 3', be reduced. By compressing these piston interstices, the working gases therein are forced through the outlet ports 141, 141 'into the tube 201 and into the tube 201', respectively.

The working gas in the tube 201 is first preheated by the regenerator 200 and then heated by the heater 300, from where it enters the tube 202. The working gas in the pipe 201 'is preheated by the regenerator 200' and then heated by the heater 300 'from where it enters the pipe 202'. As a result, the cycle described above is repeated.

The operation takes place in the motor devices according to the invention shown in Fig. 1 and 1a and Fig. 4 and 4a in an identical manner. In principle, the working gas in the pipe system and the cylinders passes through four changes of state which are predetermined by corresponding working cycles of the pistons of the cylinders 3, 3 '.

In a first working cycle of the engine according to the invention, working gas is compressed in the respective interspaces between the pistons 1, 2, 1 ', 2' of the cylinders 3, 3 'by a movement of the respective pistons towards one another.

In a second cycle of the engine according to the invention, the thus heated working gas, via the outlet opening 141 of the cylinder 3 'has been pressed into the tube 201 or via the outlet opening 141' of the cylinder 3 'in the tube 201' further heated by the regenerators 200 'and 200 and the heaters 300' and 300, respectively in the working gas prevailing pressure is further increased. In the tube 202 behind the heater 300 and in the tube 202 'behind the heater 300', therefore, there is a total of maximum pressure of the working gas in the entire pipe system.

Through the inlet ports 130, 130 'therefore occurs under high pressure working gas in the cylinder 3 and passes between corresponding spaces between the pistons 1, 2 and pushes these pistons apart at high pressure. This corresponds to a third cycle of the engine according to the invention. The heat energy of the working gas is converted in this working cycle of the engine according to the invention by a pushing apart of the spaces between the pistons 1, 2 of the cylinder 3 in rotational energy of these pistons. The working gas cools down in a third state change.

In a fourth cycle of operation of the engine according to the invention, the working gas thus relaxed is forced out of the cylinder 3 via the outlet ports 140, 140 'by compressing the respective spaces between the pistons 1, 2 due to expansion of the spaces between these pistons in the direction of rotation of the engine , The working gas then undergoes a fourth state change by being further cooled by the regenerators 200 and 200 'and the coolers 400 and 400', so that it is in a highly cooled state in the tubes 204 and 204 '.

With the time of entry into the inlet openings 204 'and 204 and after entering the inlet openings 204' and 204, the working gas is compressed again.

The state of the working gas, defined by its pressure and its temperature, is summarized summarized in Table 1 summary.

For a rapid reduction in activity or increase in activity in accordance with a force reduction or force increase of the engine according to the invention, it is possible to activate or inactivate a bypass line via a valve between a hot line and a cold line of the engine according to the invention.

Fig. 2 and Fig. 5 show a schematic representation of the spatial arrangement of the shafts 6, 7 and 6 ', 7' or axes of the cylinder 3, 3 'and the working shaft 105 of the motor according to the invention. In order to achieve a timely transport of the working gas from one cylinder to another, in which the engine according to the invention provides a working power, the axes of the two cylinders are arranged so that they with the axis of the working shaft, from which the engine power is removable, an isosceles triangle form, wherein the angle between the catheters is about 135 ° and the angle of the hypotenuse to a catheter is about 22.5 °.

In the figures 11 to 20, the structure and function of the compensating element according to the invention is shown.

In the preferred embodiment of the device according to the invention shown in Figures 11 to 12A, the compensation element is discretely adjustable.

As shown in FIGS. 1 and 1A, the compensating element is formed by a toothed belt placed around the shafts of the two units, which toothed belt is displaceably mounted around one or more teeth for a compensating process.

As shown in FIG. 2, the compensating member is constituted by a fixing device in which the respective shafts of the units driving a rotational force output device are fixedly fixed in different positions, and in each of these positions, meshing of the gears of the rotational force output device with the respective gears of the shafts is ensured ,

The fixing device, in turn, is formed by a gear box in which the respective shafts of the units driving a torque output device are mounted fixed in different positions, wherein in each of these positions a meshing of the gears of the torque output device with the respective gears of the shafts is ensured.

As shown in FIGS. 12 and 12A, the respective shafts of the units driving a torque output device are arranged at a fixed angle of 135 ° to each other, each shaft being associated with a respective bore A, A 'for each of these angular arrangements. The bores B, B 'relate to a different angle of 120 ° in this case.

In the illustrated in Figures 13 to 15A preferred embodiment of the device according to the invention, the compensation element is continuously adjustable.

The compensating element is designed as two displaceable rollers which are arranged between the two torque output devices of the two units and drivingly connected via a toothed belt with the torque output devices, wherein the displaceable rollers are reciprocally displaceable at mutually changeable distance in a direction perpendicular to the connecting line of the rotary power output devices ,

As shown in Figure 14, a first inlet slot of a diametrically opposed first inlet slot pair of a first cylinder and a first outlet slot of a diametrically opposed first outlet slot pair of the first cylinder are separated 4 °, and a second inlet slot of the diametrically opposed first inlet slot pair and a second outlet slot of the diametrically opposed first Auslassschlitzpaares are separated at an angular distance of about 77 °.

As shown in Figure 14A, a first inlet slot of a diametrically opposed second inlet slot pair of a second cylinder and a first outlet slot of a diametrically opposed second outlet slot pair of the second cylinder are spaced apart at an angular distance of about 35 °, and a second inlet slot of diametral opposite second inlet slot pair and a second outlet slot of the diametrically opposed second outlet slot pair are separated by an angular distance of about 47 °.

All inlet slots and outlet slots are formed in the cylinder head of each cylinder.

The two units are arranged so that a part of the device from which the rotational force of the rotary engine is detachable is operated by both units, and a heater, heat storage and cooling means are provided in communication with a pipe system through the intake ports and exhaust ports the displacements of the at least one cylinder of the units are interconnected.

FIG. 16 shows a temperature unit TA of the preferred embodiment of a discrete adjusting device of the rotary piston heat engine device according to the invention shown in FIG. 11 and having two corresponding temperature units TA, TB in a cross-sectional view. This unit has four oval gears, namely the intermeshing oval gears 103, 104 and the intermeshing oval gears 101, 102. The shaft 6 is formed integrally with the piston 1. The oval gears 102 and 103 are arranged on a shaft 5 '. The oval gear 101 is rotatably connected to the piston 2, and the oval gear 104 is rotatably connected to the piston 1 via the shaft 6. The respective pistons are shown in detail in Figures 2a and 2b. The transmission gears 101, 102, 103 and 104 are housed in a gear box 28 such that these Cogs mesh with each other, and also the transmission gears 101 ', 102', 103 'and 104' are housed in a gear box 28 'such that these gears mesh with each other.

The workflow is in accordance with that, as shown in Figures 1 to 10 with the exception of Figure 2.

17 shows the units I and II including the compensating element formed as belt 120, including pulleys 32, 32 'of the preferred embodiment of the discrete adjusting device of the rotary piston heat engine device according to the invention shown in FIG. 11 in an oblique rear view, and FIG shows the units I and II with their respective mutually thermally coupled temperature unit TA and TB in a front view.

Fig. 18 shows the units I and II with their respective thermally coupled temperature units TA and TB in a front view, Fig. 18a shows the same units I and II in a top view, and Fig. 18b shows the same units I and II in a side view. In the region of the opening slots 131, 131 '; 141, 141 'of a cylinder cover 33 and the opening slots 130, 130'; 140, 140 'of a cylinder cover 33' are connected to one another via gas communication connections 300, 400.

19 shows a unit II of the temperature unit TB of a discrete adjusting device of the rotary piston heat engine device according to the invention in an exploded view and FIG. 20 shows a unit I of a temperature unit TA of a discrete adjusting device of the rotary piston heat engine device according to the invention in an oblique view from above.

The above-described embodiments of the invention are only for the purpose of better understanding of the teaching defined by the claims according to the invention, which is not limited as such by the embodiments.

Claims (17)

1. A rotary piston heat engine system (100) composed of two units (I, II) each comprising two pistons (1, 2) mounted for movement in opposite directions, the pistons being each mounted for rotation in a cylinder (3, 3'), wherein the longitudinal axes (4, 4') of the pistons (1, 2) and cylinders (3, 3') are collinear, and the pistons (1, 2) are mounted for movement in opposite directions, and a plurality of effective cylinder displacements (8, 9, 11, 12) is formed in each case between two radial boundary surfaces (10, 20) of the two respective pistons (1, 2), which execute an angular motion relative to each other when the engine (100) is operating, and at least one mechanism (110) is provided that superimposes a circular motion on the angular motion of the two pistons (1, 2), and each unit comprises a shaft (6, 6') for driving a torque-producing device (5 or 5', 5"), and wherein heating means and cooling means connected to a pipe system are provided, by means of which the inlet ports (130, 130' ; 131, 131') and outlet ports (140, 140'; 141, 141') of the displacements of the cylinders (3, 3') of the units (I, II) are interconnected, characterized in that a compensating device is provided that balances the positions of the respective pistons in the two units (I, II) in the event of a possible phase shift in the synchronization of the two units (I, II), in order to effect an optimal phase response, and the compensating device (120) is discretely adjustable and is in the form of a toothed belt disposed around the shafts of the two units (I, II) embodied as torque-producing devices (5', 5"), which belt is mounted for displacement by one or more teeth to effect compensation.
2. A rotary piston heat engine system as defined in claim 1, characterized in that the compensating device is embodied as an anchoring system (122), in which the respective shafts (6, 6') of the units (I, II) adapted to drive a torque-producing device (5,) are stably mounted in different positions, and in each of these positions meshing of the gear wheels of the torque-producing device with the respective gear wheels on said shafts is guaranteed.
3. A rotary piston heat engine system as defined in claim 2, characterized in that said anchoring system is embodied as a gearbox in which the respective shafts (6, 6') of the units adapted to drive a torque-producing device (5; 5', 5") are stably mounted in different positions and in each of these positions meshing of the gear wheels of the torque-producing device with the respective gear wheels on said shafts is guaranteed.
4. A rotary piston heat engine system (100) composed of two units (I, II) each comprising two pistons (1, 2) mounted for movement in opposite directions, the pistons being each mounted for rotation in a cylinder (3, 3'), wherein the longitudinal axes (4, 4') of the pistons (1, 2) and cylinder (3, 3') are collinear, and the pistons (1, 2) are mounted for movement in opposite directions, and a plurality of effective cylinder displacements (8, 9, 11, 12) is formed in each case between two radial boundary surfaces (10, 20) of the two respective pistons (1, 2), which execute an angular motion relative to each other when the engine (100) is operating, and at least one mechanism (110) is provided that superimposes a circular motion on the angular motion of the two pistons (1, 2), and each unit comprises a shaft (6, 6') for driving a torque-producing device (5 or 5', 5"), and wherein heating means and cooling means connected to a pipe system are provided, by means of which the inlet ports (130, 130'; 131, 131') and outlet ports (140, 140'; 141, 141') of the displacements of the cylinders (3, 3') of the units (I, II) are interconnected, characterized in that a compensating device is provided that balances the positions of the respective pistons in the two units (I, II) in the event of a possible phase shift in the synchronization of the two units (I, II), in order to effect an optimal phase response, and the compensating device is continuously adjustable and is in the form of two displaceable rollers (240, 241) disposed between the two torque-producing devices (5', 5") of the two units (I, II) and are drivingly connected to the torque-producing devices (5', 5") via a toothed belt, which displaceable rollers (240, 241) are reciprocately displaceable over a mutually variable distance in a direction perpendicular to the connecting line between the torque-producing devices (5', 5'').
5. A rotary piston heat engine system as defined in claim 3 or claim 4, characterized in that the respective shafts (6, 6') of the units adapted to drive a torque-producing device (5; 5', 5") are disposed relative to each other at a fixed angle of 135 ° or 125 °, there being assigned to each shaft (6, 6') a respective bore A, A' and B, B', respectively, for each of these angular configurations. (Fig. 12, Fig. 12A)
6. A rotary piston heat engine system as defined in claim 4, characterized in that the two displaceable rollers (240, 241) are in the form of eccentric rollers.
7. A rotary piston heat engine system as defined in any one of claims 1 to 6, characterized in that a first inlet port (130) of a diametrically opposed first pair of inlet ports (130, 130') of a first cylinder (3) and a first outlet port (140) of a diametrically opposed first pair of outlet ports (140, 140') of the first cylinder (3) are separated from each other by 0.5 ° to 8 ° and a second inlet port (130') of the diametrically opposed first pair of inlet ports (130, 130') and a second outlet port (140') of the diametrically opposed first pair of outlet ports (140, 140') are separated from each other by an angular distance of approximately 55 ° to 95°.
8. A rotary piston heat engine system as defined in claim 7, characterized in that a first inlet port (130) of the diametrically opposed first pair of inlet ports (130, 130') and a first outlet port (140) of the diametrically opposed first pair of outlet ports (140, 140') are separated from each other by 4 °.
9. A rotary piston heat engine system as defined in claim 7 or claim 8, characterized in that a second inlet port (130) of the diametrically opposed first pair of inlet ports (130, 130) and a second outlet port (140) of the diametrically opposed first pair of outlet ports (140, 140) are separated from each other by an angular distance of approximately 77 °.
10. A rotary piston heat engine system as defined in any one of claims 1 to 9, characterized in that a first inlet port (131) of a diametrically opposed second pair of inlet ports (131, 131') of a second cylinder (3') and a first outlet port (141) of a diametrically opposed second pair of outlet ports (141, 141') of the second cylinder (3') are separated from each other by an angular distance of approximately 25 ° to 45 ° and a second inlet port (131') of the diametrically opposed second pair of inlet ports (131, 131') and a second outlet port (141') of the diametrically opposed second pair of outlet ports (141, 141') are separated from each other by an angular distance of approximately 30 ° to 60 °.
11. A rotary piston heat engine system as defined in claim 10, characterized in that a first inlet port (131) of the diametrically opposed second pair of inlet ports (131, 131') and a first outlet port (141) of the diametrically opposed second pair of outlet ports (141, 141') are separated from each other by an angular distance of approximately 34 °.
12. A rotary piston heat engine system as defined in claim 10 or claim 11, characterized in that a second inlet port (131') of the diametrically opposed second pair of inlet ports (131, 131' and a second outlet port (141') of the diametrically opposed second pair of outlet ports (141, 141') are separated from each other by an angular distance of approximately 47 °.
13. A rotary piston heat engine system as defined in any one of claims 7 to 12, characterized in that all inlet ports and outlet ports are formed in the cylinder head (33; 33') of the a respective cylinder (3; 3').
14. A rotary piston heat engine system as defined in any one or more of the previous claims, characterized in that additionally heat storage means are provided which are connected to the heating means and the cooling means.
15. A rotary piston heat engine system as defined in any one or more of the previous claims, characterized in that the two units are such that that part of the system (5, 102, 103) from which the torque of the rotary piston engine (100) can be outputted is driven by both units (I, II), and heating means, heat storage means, and cooling means connected to a piping system are provided, which piping system connects the inlet ports and outlet ports of the piston displacements of the at least one cylinder (3) of the units (I, II) to each other.
16. Use of a rotary piston heat engine system as defined in any one of the previous claims as a heat pump by supplying rotational energy to the torque-producing devices (5; 5', 5").
17. Use of a rotary piston heat engine system as defined in any one of the previous claims as a refrigerating machine by supplying rotational energy to the torque-producing devices (5; 5', 5").

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