WO1987005964A1 - Rotating and alternating piston machine - Google Patents

Abstract

The rotating and alternating piston machine is an alternating or free piston machine in which the pistons effect a rotating and alternating movement. Main characteristics: 1) the use of rotation or alternation/rotation, for example in order to control the ports provided in the cylinder walls of two- and four-stroke engines, pumps and compressors; 2) simple conversion of rotating and alternating movement by mechanical or electrical means. The rotating and alternating piston machine offers the possibility of: pumps, including the electric drive, in which there is only one rotating part; direct conversion of the alternating movement of the piston into electrical energy; control of the gas movement by the piston; operation of other ports having specific functions (for example, introducing additional compressed gas, discharge ports operating in succession etc.); free selection of the number of piston strokes per rotation; choice of piston stroke kinematics; powerful rotation or swirling of charge; easily designed compact and inexpensive machines; possible integration of a compressor without having to provide for an additional volume and virtually without any weight increase. In the two-stroke combustion engine, in which the gas exchange is controlled by the pistons (2 and 5), the useful power is available at the central shaft (14), which carries the rotating and alternating piston (2) in a longitudinally-slidable but rotationally-fixed manner. Movement is converted by the oscillating shaft (35) and transmission element (38). The engine is provided with four working chambers and has a 100% mass balance.

Description

 TURNING LIFTING PISTON MACHINE

The key points of the rotary reciprocating piston machine are the simple conversion of the reciprocating movement of the piston into a rotary movement, which results in a rotary / reciprocating movement. In addition, the use of this piston movement for the direct control of the gas exchange by the piston: valves become superfluous, not only with 2-stroke but also with 4-stroke engines and pumps and compressors.

According to the same principle of movement, the lifting movement can also be converted electrically instead of mechanically and directly generate electrical energy (or vice versa). With just one cylinder and two reciprocating pistons, you get a machine with four working spaces (corresponding to a conventional four-cylinder machine) and a 100% mass balance. (Example picture 1). With additional inner work spaces, another four work spaces are added to the same machine.

Several different solutions are listed for converting the piston movement (see Fig. 1, 6..8, 9..13). In addition to the compactness and simplicity of the machine, a very high level of performance and efficiency can be expected due to the very generous openings for changing loads. Other things, swirling of the charge in internal combustion engines, etc., will be discussed below.

To give the name: The "rotary piston machine" is a reciprocating piston machine or a free piston machine, with additional rotary movement of the piston. If the stroke is mechanically limited, it is a reciprocating piston machine, otherwise (for example, for electrical generation of the piston movement according to claim 4) it is by definition a free-piston machine. However, since the typical main feature of the machine is the rotary stroke movement of the piston, the name "rotary piston machine" is chosen. The course of the description is arranged according to the order of the claims. The numbers at the beginning of the following sections refer to the corresponding claims. Dependent claims that relate specifically to only one claim are dealt with in context.

Control of the gas exchange

1. The efficiency of every piston machine depends crucially on the quality of the gas exchange. Conventional valves leave only a relatively small cross section free and have to be opened and closed with great difficulty.

The task was therefore a piston machine with direct control of openings in the cylinder wall by the piston. (Often called "slot control"). The solution should be suitable for all known working methods and applications, that is also for machines which compress the working medium in the cylinder. This requirement requires that the working space at the top dead center of the stroke can be reduced to an arbitrarily small final volume.

The rotary reciprocating machine according to claim 1 fulfills this task. The piston rotation plays an important role here: the piston surface facing the working space is designed as geometrically defined in claim 1. Figure 5 shows illustrative examples.

With such shapes, the openings in the cylinder wall are covered and covered not only by the stroke movement, but above all also by the piston rotation. (This is in contrast to the conventional slot-controlled 2-stroke engine, in which only the stroke movement of the piston controls the openings). See pictures 3 and 4.

Thus, not only is the charge change in the slot-controlled 2-stroke engine significantly more efficient (asymmetrical control times possible), it is now also possible to build 4-stroke engines and pumps and compressors in this way. - 3 -

Achieving the small final volume (often also called "final compression volume"):

The working space is limited on one side by the rotary piston and on the other side also by a piston that rotates synchronously but does not need to perform a lifting movement. In the upper dead center of the surface shape fits a ^* piston in the formed as a negative mold surface of the other Kol¬ bens. This second piston, which only rotates, can also control openings for the gas exchange. (Picture 1, 13 and 5) Second variant:

The working space is delimited by two end faces: on the one side by the piston, which makes a rotating or rotating stroke movement, on the other side by a non-rotating end face. This can be a non-rotating piston or the cylinder head. In order to achieve a small final volume, these surfaces must also fit into one another as described above. So that these two end faces do not collide with each other at the top dead center, the following measures are taken:

In this position, no or only a slight rotational movement may take place as the distance between the two end faces and the shape of the end faces allow. This is achieved by discontinuous piston rotation, by several stroke cycles per revolution and / or by appropriate shaping of the end faces.

Radial forces due to the pressure in the work space are described below together with claim 2.

On the subject of piston movement: nothing is mentioned in this claim about the generation of the rotary stroke movement. Simple, compact solutions for this are the content of further independent patent claims.

Theoretically, there are almost infinite possibilities for generating the rotary stroke movement. Many are known or can easily be derived from the prior art of the following: - 4 -

produces an oscillating stroke movement in a known manner and adds any rotational movement to the piston with another known device. Example:

Large marine diesel engines are mostly built today as cross-head reciprocating engines. An additional piston rotation can be generated in various ways. For example, the piston rod can be rotatably connected (axial bearing) to the crosshead and the piston rod and piston can be rotated from the outside, or the piston can be rotated by a built-in auxiliary drive (electric motor etc.) etc. etc. Figure 2 shows a schematic example of this . The rotary movement can be matched to the stroke movement as desired. (See also claims 9, 10, 18, 19). The rotary movement of the piston preferably takes place as a continuous rotation, because of the inertia. However, a rotational movement is back with periodically and herwechselnder ^'Dreh¬ directional sense which very large openings allowed. Lubrication: See point 26.

Sealing: With piston rings, which are adapted to the shape of the control edge, for rather subordinate purposes with conventional piston rings or with a labyrinth seal (grooves). Ideal: without a piston ring thanks to a piston made of ceramic or another material that has only a small thermal expansion. The piston then runs with a minimal fit in the cylinder and no longer requires any further sealing elements.

2. Task: A piston machine with slot control by the piston, which works with low friction even with high pressure of the working medium. It should be simple and suitable for all applications which do not require a small final volume.

Solution: A rotary piston machine in which the piston rotates and controls the openings, whereby the piston geometry has two typical features: - 5 -

First, the piston face is shaped in such a way that the openings in the cylinder wall are controlled not only by the stroke movement, but above all also by the rotary movement of the rotary piston.

Secondly, low friction is achieved if the piston is also shaped in such a way that the pressure of the working medium on the piston end only causes a resulting axial force on the piston. Due to the special shape, the radial shear force components cancel each other out. Examples: Figure 5: Piston shapes a and b do not have the second characteristic, the other pistons in Figure 5 are "free of lateral forces" and meet the requirements. The second feature does not necessarily require symmetry of the piston face.

3rd and 8th integrated piston machine inside the rotary-stroke piston, integrated pre-compressor

Possibilities of pre-compression (charging) in the rotary piston machine: a) by means of a turbo or compressor b) with a mechanical pre-compressor integrated in the rotary piston machine.

Function of the integrated pre-compressor: see example diagram in Figure 16 and the detailed diagram

Description on the next page.

General advantages of the integrated pre-compressor:

- Space requirements are zero: the pre-compressor is fully integrated in the rotary piston machine. The rotary reciprocating machine does not get bigger as a result.

- Hardly any additional weight: Almost all parts are already available. The pre-compressor piston attached to the shaft is actually the only additional component. - 6 -

- Simple and cheap.

- The gas cushion in the pre-compressor improves the smooth running of the machine under certain conditions.

- The outlet control by the rotary piston enables different systems to be fed with different pressure levels. (See also claim 16).

Applications

- Two-stage compressors.

- Pumping or compressing different media with a single, compact machine, etc.

Discussion: Use in (rotary reciprocating) internal combustion engines

1) Use as a mechanical loader.

Same function as an external mechanical compressor.

2) Support for gas exchange in two-stroke engines. - In analogy to the known pre-compression of the intake mixture in the crankcase of today's two-stroke small engines.

3) Turbulence, stratified charge, lean engine:

(N.B: Claim 8 is the integration of the inner piston machine (integrated precompressor) into a rotary reciprocating piston machine with control of the gas exchange according to claim 1 or 2.)

Only part of the intake air is fed to the pre-compressor. After leaving the pre-compressor, this relatively strongly compressed "additional air" reaches the rotary piston engine in the following way:

After the normal suction process is completed, it is blown through a slot that is separate from the suction slot. Effect: - Strong turbulence

- Improve the filling. The time of blowing in can be optimized. Fuel injection into the blowing air makes sense. Now imagine the following: - 7 -

The cylinder is filled with pure air. Shortly before ignition, a "cloud" of rich, easily ignitable gasoline-air mixture is blown against the spark plug. The inclined reader knows what this means:

- Stratified charge in the highest degree and thus

good burning of an overall extremely lean person,

- correspondingly extremely low consumption and exhaust gas values.

4) Lean engine charged with pre-compressor:

For actual charging, it is recommended to pre-compress all of the intake air. The precompressor additionally compresses a small part of the air to the higher injection pressure. (Combination of 1) 3) and 16)).

5) For high charging (for diesel engines) it is best to use exhaust gas turbo or pressure wave superchargers. Advantage: utilization of the exhaust gas energy. The integrated pre-compressor then compresses part of the charge air to the higher injection pressure.

6) Other applications:

- Feeding servo units with compressed air.

- Use as an integrated pump instead of a compressor

(e.g. as an oil pump, hydraulic pump, etc.).

Constructive

- Check valves in the pre-compressor piston for the type with suction through hollow shaft: These are adapted to the type of work or the working medium. Execution as ball, flap or spring lip valves etc.

- The shape of the piston face of the pre-compressor piston can be selected. Very high compressions can be achieved.

- The entire concept is ideally suited for the use of exotic materials such as ceramics, hard materials, etc. - 8th -

Rotary piston machine with integrated pre-compressor

(Description of the schematic diagram Fig. 16) The rotary reciprocating piston (item 2) rotates together with the through shaft (14) and the rotating piston (item 5). The only rotating pistons (5) are firmly connected to the shaft (14). However, the rotating rotary piston is forced by the cam track (item 3) to make an additional longitudinal (stroke) movement. (For generation of the rotary stroke movement, see claim 7 or the other claims 5 and 6). The rotary piston is therefore longitudinally displaceable on a shaft; but it can still transmit a torque to the shaft (not visible in the picture, treated in claims 21, 22, 23).

The integrated pre-compressor mainly consists of the rotating pre-compressor piston (item 31).

This is located in the inner cavity of the rotary piston (2). It is firmly connected to the shaft (14), so it does not make any lifting movement. The oscillating stroke movement of the rotary piston (2) therefore causes the working medium located there to be compressed to the left and right of the pre-compressor piston.

Flow course:

Outlet: through slits in the lateral surfaces of the rotary piston and the cylinder. - The movement of the rotary piston relative to the cylinder automatically controls the slots. (The principle is known from slide controls).

Inlet: a) Inflow through the lateral surface according to the same principle as for the outlet. b) Inflow through the hollow shaft and the pre-compression piston. Advantage: cooling the shaft.

Check valves take over the control of the inlet. (Schematic sketch in Fig. 16 Item 32) c) Combination of a) and b). Of course, it would also be possible to pass the outlet through the hollow shaft instead of the inlet. - 9 -

Generation of the rotary stroke movement

4th and 9th "Electric" rotary reciprocating machine

Claims 4 and 9: These claims show how the desired rotary stroke movement can be generated directly with electrical energy. This machine can also directly convert the rotary stroke movement into electrical energy.

In conventional machines, for example, a shaft is first set in rotation with an electric motor. This wave rotation drives e.g. a pump. In the pump, the shaft rotation must be mechanical, e.g. can be converted into a lifting movement by means of a crank mechanism. This moves the piston. In the rotary reciprocating machine with motion generation according to claim 4 or 9, all this happens with only one machine, an "electric rotary reciprocating pump". Examples of use:

- As a motor: The electric current directly generates a rotary stroke movement. In this way, for example, a pump with slot control of the inlets and outlets with the rotary reciprocating piston (for example according to claim 2) can be built with only one moving part: the rotary reciprocating piston! I.

- Generator: The rotary reciprocating machine works, for example, as an internal combustion engine. The lifting forces on the pistons generate electrical energy. At the same time, the rotary motion is superimposed on the piston by the magnetic forces. Control of the gas exchange according to claim 1 or 2 is thus also possible.

Constructive, characteristic properties:

The anchor is specially shaped, see examples 20 and

22. This is the important, characteristic peculiarity.

We differentiate between two armature types: a) The armature is provided with fixed magnetic poles. - 10 -

This means that the armature either contains windings, is provided with permanent magnets or is permanently magnetized. b) Although the anchor can be agnetized, it is not permanent magnetic. That means it consists of a material with low magnetic remanence. Function: a) Anchor with fixed magnetic poles:

In principle, the rotary movement can be generated in exactly the same way as with conventional electric motors (this also applies analogously to electrical generators). All known types with direct current, alternating current, three-phase current, single-pole, multi-pole or types as stepper motors, etc. can be used.

Due to the shape of the armature, the rotary movement also results in the stroke movement of the piston: the stator guides the adjacent surface of the armature at one or more points by magnetic forces. See example in Figure 17: The top of the stator is where it guides the outer surface of the armature. At the bottom, the field of the stator is much wider axially. The axial movement of the outer surface of the armature is permitted there. In addition, the possible axial force on the armature can be increased as follows: The stator acts not only with axial forces on the outer surface of the armature where it guides the armature. It also supports the relative axial movement of the armature outer surface to the stator at other points by driving forces. These driving forces oscillate in accordance with the movement of the outer surface of the armature. As a result, they not only cause greater possible axial forces, they can also support the rotary movement. b) Anchors made of magnetizable but not permanently magnetic material, without coils on the anchor:

Advantages: Very cheap to manufacture.

No power supply to the rotating anchor. With a conventional, rotationally symmetrical anchor shape, it would not be possible to produce a rotary movement in this way. The armature can be magnetized by the stator, but they migrate - 11 -

with magnetic poles on the anchor.

Due to the special shape of the armature according to claim 4, such electric oters can be realized. See Figures 18 to 21. At least one point, the stator acts with a strong field on the armature and magnetizes the armature. This creates a whole number of magnetic pole pairs on the armature, i.e. an even number of magnetic poles. The driving forces now do not act in a purely tangential direction, as with a conventional electric motor. (N.B: The radial force component between the stator pole and armature is taken for granted and is therefore not mentioned here.). The driving forces of the stator act primarily in the axial direction. However, a tangential force component is also required to generate the rotary movement. This tangential force component is created automatically by the shape of the armature, unless the armature lies in a dead center of movement. For this reason, the machine in Figure 18 has, for example, an auxiliary winding (46) for starting the machine. The machine in Figure 19 has a guide pole (44) and three points on the stator that drive the armature. The driving poles are controlled so that the armature continuously follows the attractive forces of the driving magnetic fields. As shown in Figures 20 and 21, two lifting cycles per revolution occur. The shape of the anchor is shown in perspective in Figure 22. In Figure 20 we have two guide poles (44). The relative movement of the outer surface of the armature relative to the stator has "nodes" at these points. This machine also needs a starting device (not shown) for starting from the position shown.

Such machines with several (ideally at least 3) magnetic poles on the stator, which attract the armature with magnetic forces, can also be easily used to guide the armature in the radial direction: The distance between armature and stator becomes Eg electronically controlled and kept constant by varying the magnetic forces. As a result, this device also serves as a magnetic, practically frictionless magnet. - 12 -

camp. With two such devices, the shaft or the piston is stored cleanly.

In Figure 21 we again have two guide poles, but three positions on the stator, which have a driving effect on the armature. In such machines, it must be ensured that the driving poles (45) do not suddenly change their polarity at the same time and repel the armature. Since they are in the majority, they can otherwise magnetize the armature. With multi-phase alternating current, the machine runs as shown in Figure 21 so that all poles always attract each other. As a result, the armature can exert or withstand high axial forces. If the driving magnetic stator forces always have an attractive effect on the armature, the driving poles actually also assume axial guiding tasks. According to this principle, machines can also be realized which no longer have actual, stationary guide poles on the stator, but only moving, driving fields which guide the armature around in the correct position. The stroke length and the form of movement can be varied by detaching the anchor from a guide point or by changing guide points. (This also applies to variant a with coils in the armature). By adjusting the stroke length of the piston, the delivery rate can be adjusted for pumps, for example. (See also claim 20). The operation of the electric rotary reciprocating piston machine in the most common designs with the different types of current can be found in claim 9.

Alternative design: The stator on the outside has the described functions and features of the armature. Similarly, the armature has the descriptive functions and features of the stator. This can be imagined as follows: If you exchange the words "stator" and "anchor" with each other, you get an analog but different design. The outer surface of the armature is then to be understood analogously as the inner surface of the stator. Example: The external stator has the oblique or curved shape as described above for the armature. The anchor guides and drives with its magnet. graze the stator, so that the stator makes a rotary-stroke movement relative to the armature, etc. In most cases, this is the less favorable design: Most of the time the external stator is stationary relative to the surroundings. This makes it easier to supply power to the stator than to the rotating armature. - And this is a big advantage of this system with an anchor without coils.

"Mechanical" rotary reciprocating machines:

5., 10., 11. Exact geometric definition see claim 5. Descriptive definition based on an embodiment (see picture 1 and 6):

In this rotary reciprocating machine, the stroke movement is converted into a rotary movement (or vice versa) as follows: The swashplate-like shaft (Figure 1, item 35 or Figure 6, item 37) is or is firmly connected to the piston a component of the piston. When the piston rotates, this shaft makes a wobbling motion. After half a turn, the position changes as shown in Figure 1 on the left to a position as shown on the right. These two positions form the two extreme stroke positions (stroke movement dead centers). The transmission element (38) transmits the forces from the piston to the cylinder. A swashplate-like shaft and transmission element result in a torque from the lifting force or vice versa. So that the piston, the swashplate-like shaft and the guide element are not hindered in their movements, the connection between the transmission element and the cylinder is articulated. The exact geometric requirements are described in claim 5. The examples in pictures 1 and 6 show three examples of many possibilities.

The example in Figure 1 works without a ball joint with two interlocking joints. The inner joint transmits only radial forces and is axially displaceable. The outer joint with the axis of rotation perpendicular to the plane of the drawing also transfers axial forces. (NB: Central shaft (14) see claims 21 and 22). , ,

- 14 -

In the example shown in Figure 6, the swashplate-like shaft is molded into the piston. The joint is designed as a ball joint. Figures 6 a and b differ only in the different types of compensation for the longitudinal displacement of the articulation point. In the positions shown, the pivot point is closest to the cylinder axis. After a quarter turn, the pivot point has moved a little away from the cylinder axis. Applications: Motors:

The joint in Figure 1 is intentionally drawn very large. On the one hand, this makes the function easier to see. On the other hand, it is intended to illustrate that this device can be dimensioned very firmly and is therefore also suitable for large engines, e.g. for ships. (Items 37 and 38 can also be dimensioned as large as desired). The slim design is also ideal for deep installation lengthways in the keel. The slim design and the low weight are also interesting for aircraft engines and vehicle engines, etc. In addition, there are the further advantages of the rotary piston engine, e.g. easy control of the gas exchange. Rest:

Simplicity and compactness and the possibility of easy control of the gas exchange make this machine interesting for almost all applications. The slim design is e.g. ideal for oil pumps. Variants:.

- Two such devices per rotary reciprocating piston, the joints being diametrically opposite. This compensates for the eccentricity of the axial force acting on the piston.

- Swashplate-like shaft and transmission element together form an electric motor or electric generator. (Claim 11). - 15 -

6., 12. This rotary reciprocating machine serves the same purpose as that previously discussed. Function:

Exact geometric definition see claim 6. Illustrative definition based on the examples Figures 7 and 8: The "hollow shaft" (item 40) is rotatably mounted in the cylinder (1). If you follow a point on the hollow shaft, e.g. the articulation point (item 42), you can immediately see the following: With the rotation of this hollow shaft, this point also performs an axial movement relative to the cylinder. The piston is set in a rotary stroke movement. Conversely, the stroke movement of the piston rotates the hollow shaft. The design of the joint is defined in claim 6 analogously to that of claim 5. Figures 7 and 8 again show two of many possible examples. Applications: as in claim 5. Differences from claim 5:

- The axial space requirement in the cylinder is less here. This allows the rotary piston to be made shorter.

- The structural application of force to the piston is different

- The joint rotates around the cylinder axis. Variants:

Likewise, the arrangement of two such devices per rotary reciprocating piston is also possible here. As a result, the eccentric application of force to the piston can be compensated.

- The cylinder part surrounding the hollow shaft and the hollow shaft are designed as an electric motor or an electric generator. (Claim 12)

- The rotation of the hollow shaft can be transmitted directly to the outside by, for example, the hollow shaft carrying a ring gear which is in engagement with another gear or a gear. - 16 -

7., 13. A spatial cam track is responsible for the piston movement (Fig. 9..11, item 3), e.g. in the form of a cam or a circumferential groove, which is supported on guides (4), such as rollers or sliders. The spatial cam track (item 3) is normally directly connected to the piston (2) and reproduces the stroke kinematics "program" stored in its cam shape with every turn. Of course, the reverse arrangement is also conceivable, namely the guides on the piston and the cam track attached to the cylinder.

In theory, any integer number of lifting cycles per full revolution is possible - and any kinematics of the movement. If there are several lifting cycles per revolution, several guides can be installed on the circumference. This prevents an eccentric force attack on the piston.

Claim 13 solves the following problem: Figure 13 clearly shows that the cam tapered and thickened again. This is due to a fixed attachment of the guide rollers. With a rocker (Fig. 12) the thickness of the cam remains constant over the entire circumference.

14. Combinations: Of course, the mentioned claims for generating the rotary-stroke movement fit ideally together with the control of the charge exchange according to claim 1 or 2 and / or also with the integrated piston machine (integrated precompressor) according to claim 3 and / or 8.

15. Coordinating the slot control, piston shape and movement a) The decisive factor is the gas exchange and the piston shape: With 2-stroke engines, pumps and compressors, a working cycle (consisting of two strokes) is completed after a reciprocating movement of the piston.

With the 4-stroke engine, an entire working cycle (consisting of the 4 strokes of intake, compression, combustion and exhaust) requires 2 reciprocating movements of the piston, ie two working cycles. - 17 -

Since the rotation of the pistons decisively determines the control of the charge change, and since the "program" for the control of the charge change comprises a whole working cycle as a period, it is best if the (asymmetrical) pistons make one revolution per working cycle do. See pictures 3 and 4.

Exceptions: For piston shapes in which the position of the control edge repeats after half a turn, half a turn is adjusted per working cycle. (Analogously, with a corresponding piston shape, a third, a quarter, etc.). For examples see Figure 5 c, d, e.

Most "shear-free" pistons are such exceptions. Second exception: the 2-stroke internal combustion engine, in which only the rotary piston controls the openings: the entire gas change takes place only in the lower half of the stroke. At this time, a rapid rotation of the piston is desirable. Afterwards in the upper half of the stroke, the rotary position of the piston no longer has any influence on the control. There, the piston can easily make an "idle" rotation. This means that the piston should make two revolutions per stroke cycle (half a stroke cycle per revolution). Or that you can choose a "non-overhung" piston shape in which the position of the control edge repeats itself after half a turn. Then one stroke cycle per revolution is correct. So you normally choose (depending on the piston shape):

- Rotary piston machine with one stroke cycle per full (or half, ..) revolution for all pumps and compressors and for 2-stroke engines.

- Two stroke cycles per full (or half, ..) revolution for 4-stroke engines.

With rotary reciprocating machines, for example according to claim 4, 7, 9, 13, any number of lifting cycles per revolution can be achieved. According to claim 5, 6, 10, 11, 12 one is limited to one stroke cycle per revolution. - 18 -

b) (Welcome) effects on the number of revolutions: For a given stroke frequency, the number of revolutions per revolution determines the number of revolutions of the shaft, or vice versa. For pumps and compressors e.g. the stroke frequency can be increased for a given number of tours.

For propeller drives in aircraft and for propeller drives, a slow shaft speed is desired because of the propeller or screw efficiency. Slow-running motors, however, have a poor power-to-weight ratio; high-speed motors would require a gearbox.

In comparison to the reciprocating piston engine with crank drive, a 4-stroke rotary reciprocating piston engine with slot control rotates exactly at half the shaft speed at the same stroke frequency; or even only a quarter of the shaft speed, depending on the piston shape. The following also speaks specifically for use in aircraft:

- The very slim, cylindrical motor contour with a central (propeller) shaft, which can be integrated into the wings in an aerodynamically favorable manner. (In the case of the rotary reciprocating piston engine, 4, 6, 8 or more combustion chambers and a corresponding number of pistons can be installed in succession in a cylinder).

- The extremely low weight of the rotary piston engine.

16. Use of slot control for special purposes

a) Example: Internal combustion engine with exhaust gas turbocharger:

The combustion of the air-fuel mixture has led to a sharp increase in pressure and temperature. When the outlet opens, the pressure in the cylinder is many times higher than in the exhaust gas pipe in front of the turbocharger. The exhaust gas flows out at the speed of sound and is expanded to the pressure level of the exhaust gas collection pipe. As a result, a lot of useful energy is lost.

It is better if the pressure in the exhaust gas collection pipe is relatively high in this first phase. This gives the exhaust gas turbocharger - 19 -

more energy. If the pressure in the exhaust gas collection pipe does not exceed approximately half the cylinder internal pressure, the speed of sound is nevertheless achieved. This means that the emptying of the cylinder is not slowed down, the engine does not "feel" the higher back pressure yet.

In the second phase, after bottom dead center, when the pressure in the cylinder has dropped, the situation is different: Now the high back pressure makes the piston stroke stroke more difficult. Therefore we now open the second outlet channel with the piston and close the first high-pressure outlet (either with the piston or with a check valve). There is a low gas pressure in the second outlet duct. In the simplest case, it leads directly to the outside via a silencer. Because of the higher exploitation of the exhaust gas energy in the first phase, the turbo receives enough energy and therefore does not require the total amount of exhaust gas.

The internal cylinder pressure is now significantly higher when sucking in the charged air than when exhausting. Therefore, the four-stroke engine generates a noticeable additional power even during the gas change.

The two-stroke engine achieves an extremely fast and effective gas exchange1.

With appropriate effort (large engines), entropy can be reduced even further by arranging more than two outlet channels and grading the pressure more finely. The first outlet goes to a high pressure stage of the turbocharger, the second to a medium pressure stage, etc.

The principle mentioned above also provides a clear advantage for the "cooperation" between engine and turbo and for the engine characteristics:

Let us take the following example: The first outlet is designed in such a way that the exhaust gas flows out at the speed of sound at full load and relatively low speed during the opening time of the first outlet. Now we increase the speed: The absolute duration of the opening time of the first outlet is reduced - 20 -

become linear with the speed. For this, the number of openings per unit of time increases linearly. Consequently, the amount of exhaust gas and energy from the first outlet for the turbocharger remains constant. (Assuming the same load and combustion conditions). On the compressor side, there is an increased air requirement at higher engine speeds, - the supercharging pressure drops. The torque of the engine increases with decreasing speed - exactly the desired opposite of a typical turbo engine characteristic.

By designing the first outlet, the designer can determine the performance characteristics of the turbocharged engine. There is no need to control or regulate the turbo (blow off, etc.). b) The same principle, namely the "sorting" of the working medium according to its content of internal energy, can also be applied to

Realize compressors: A compressor can supply different "consumers" with differently compressed gas. Function and examples were explained in connection with the integrated pre-compressor. (See description of 3 and 8). The system also works for the supply of different hydraulic systems with different pressures. c) Example gasoline engine: To be able to reduce the cylinder charge and thereby the power (partial load), one uses today

Throttle valves in the intake duct. The negative pressure created by the throttling during suction results in efficiency losses. In the case of the rotary reciprocating piston engine, one can suck in without throttling and reduce the filling as follows: At the beginning of the compression cycle, the sucked-in medium is let out again through slots which can be closed with throttle valves. In fact, this shortens the effective stroke, i.e. varies the effective displacement. (This principle can also be used to vary the delivery rate of pumps and compressors. D) Since you can open and close any slots in the cylinder wall very quickly with the rotary piston, you can: - Blowing in of pre-compressed additional air during compression (see description for 3 and 8, integrated pre-compressor)

- blowing in additional air during the combustion process. Purpose: To act as a thermoreactor to minimize the formation of nitrogen oxides. (NOx) e) The ability of the rotary piston to cover openings or surfaces in the cylinder wall can also be used to valves, nozzles, igniters, sensors etc. in front of the high combustion temperatures or the high ones To protect press.

17. Enhancing the rotation of the medium The rotation of the medium supports the flow processes when changing charges. Further application examples: a) In the case of the internal combustion engine, the rapid spread of combustion and the willingness to ignite, especially in the case of lean mixtures, are significantly increased if the working medium is vigorously swirled. See picture 14.

One can even strive for the inertial forces (centrifugal effect) to create a stratification of the load, i.e. that on the periphery near the spark plug the mixture is richer and therefore more ignitable than in the center of the work area. b) With pumps and compressors you can by stirring for certain purposes

- prevent segregation of the pump medium or sedimentation

- Effectively centricize the medium at high peripheral speeds.

- Prevent cross-linking processes in the pump medium during pumping

- prevent the medium from sticking or freezing to the cylinder walls - In the case of viscous pumping media, radial ejection is also facilitated by an end volume which increases conically towards the cylinder wall at the top dead center.

18. The classic crank mechanism in the reciprocating piston machine drives the piston in a temporally sinusoidal stroke movement with superimposed harmonics. The piston thus remains somewhat longer in the area of bottom dead center than in the area of top dead center. In many applications, the piston motion would be different, i.e. another lifting kinematics, desirable.

The stroke kinematics of the rotary reciprocating machine according to claims 4, 9, 7 and 13 can be chosen completely freely and matched to the intended use. In the other claims relating to the generation of the piston movement, the lifting kinematics can also be selected within a certain range. Claim 18 mentions the geometrical variables with which the lifting kinematics of these systems are influenced. Application examples are also listed.

19. The change in the synchronization between piston rotation and the lifting movement can have the following purposes, for example:

- Adaptation of the control times to the operating point of the machine (speed, load etc.)

- Switching the control times to reverse running for engines without reversing gear (e.g. large marine diesel).

20. Stroke adjustment: Devices for adjusting the stroke length are normally used to change the delivery volume of a pump or the swallowing volume of a (hydraulic) motor, for example in the case of hydrostatic transmissions. - 23 -

Transmission of the piston rotation to the outside

21. We have seen that the piston rotates and lifts. The transmission of the rotation of the piston from the inside of the machine to the outside is the subject of this point: Imagine a central shaft which passes through the machine on the central axis of the cylinder and at one end of the machine (or at both ends) on the end face leads to the outside. The piston is attached to this shaft in such a way that it can move longitudinally on the shaft but cannot twist with respect to the shaft. This means that the piston can transmit torque to the shaft and still execute the lifting movement. (This can be implemented in a constructive manner with a form fit, for example with a keyway and wedge, or with a construction according to claim 22 or 23).

Or you can let the shaft take part in the stroke movement of the piston and then compensate the stroke movement of the shaft at another point, e.g. at the front of the machine.

The shaft is easily sealed e.g. with rod seals (analogous to the piston rings on the reciprocating piston engine, but with an inner seal!).

22. As we saw at point 21, the torque is transmitted between the rotary piston and the central shaft. At the same time, the piston must be able to move longitudinally on the shaft in order to carry out the lifting movement.

With rolling elements (rollers etc.) this torque transmission can be designed in such a way that the stroke movement also runs with little friction. Such a construction would, for example, be designed similarly to the constant velocity universal joints that are known from car front wheel drive. This construction also compensates for misalignments. - 24 -

23. Diaphragms or bellows (see Fig. 15 a and b) can also transmit the torque with their torsional stiffness (and strength). They take up the stroke movement with their high elasticity in the axial direction.

These designs are very cheap and practically frictionless.

24. In claims 21 to 23, the transmission of the piston rotation from the inside of the machine to the outside was treated by means of a central shaft. Another possibility is to transmit the rotation over the lateral surface of one of the rotating parts.

In this way, the entire power can be transmitted (for example, positively via gears), or auxiliary units can be driven in this way. The conversion of the piston movement by one of the only rotating parts into electrical energy also makes sense, e.g. by fixing the armature of a conventional electric motor or generator directly to the rotating part.

In the case of the machine according to claim 4, the rotary movement can in any case be transmitted directly to the outside via the outer surface of the rotary piston and converted into electrical energy (or vice versa).

A motion transmission, especially for the rotary reciprocating machine according to claim 6, is dealt with in claim 12.

25. The transmission of the torque from piston to piston can instead of a shaft also be carried out in a simply positive manner through the piston surfaces, which are shaped in the sense of a "dog clutch". Piston shapes according to Figure 5 c.e are suitable for this, for example.

The piston shape and stroke length must be coordinated so that the pistons remain in engagement with each other at every stroke position.

In order to reduce friction, the force can be transmitted indirectly via rolling elements instead of directly via sliding surfaces - 25 -

lie between the two piston surfaces.

26. Lubrication

The rotation of the piston on the cylinder wall can be used to achieve a hydrodynamic lubrication state (floating on the lubrication film). Mixed friction normally occurs in the conventional reciprocating piston engine. In addition, this increases the ability to absorb any lateral forces that may be present. - The conventional crank mechanism generates a lateral force on the piston, which changes in amount and direction with the crankshaft rotation (cause of the piston tipping). With the rotary reciprocating machine, it depends on the design whether lateral forces occur at all:

Shear forces are present in the machines with only one stroke cycle per revolution and only one device for generating movement per piston (exception: certain types of claim 4). The eccentric force application creates a moment on the piston, which manifests itself as a pair of transverse forces. These transverse forces on the (double-acting) rotary piston are roughly comparable to those of the reciprocating piston machine and can therefore be absorbed by the rotary piston, as well as possible transverse forces due to the medium pressures, easily and with little friction.

There are normally no lateral forces on the rotary reciprocating machines with at least two lifting cycles per revolution. And the medium pressures also do not generate any transverse forces if the piston face is designed accordingly (e.g. point-symmetrical) (Fig. 5 c.e).

Back to lubrication: In order to prevent the lubricant from getting into the work area or into the outlet openings, a scraper ring is installed in the cylinder.

27. The simple conversion of the stroke movement into a rotary movement according to one of the claims 4..7, 9..13 also has advantages if the piston rotation is not desired and is therefore canceled. A typical application example is the diaphragm pump. - 26 -

Figure 1: Schematic drawing of the legend of a 2-stroke rotary piston 1-cylinder engine with four working spaces, la, b, c cylinder parts. Charge change according to claim 1, 2 rotary pistons (makes generation of the piston movement after rotary stroke movement) 5. (See also Fig. 13) 3 cam track

4 tours

Figure 2: Illustration of the control 5 pistons, only rotating the gas exchange with the pistons. 6 piston rings The piston movement is generated with a 7 working space conventional cross-head crank 7 ditto, maximum volume drive. In addition, 7b ditto, final volume or a rotary movement is superimposed. Final compression volume

8 inlet duct

Fig. 3: Scheme of the charge change 9 outlet channel for a pump. At the same time, a stroke cycle takes place. 11 Outlet flow Every half stroke length is drawn. 12 spark plugs

13 injector (diesel)

Fig. 4: Scheme of the 4 cycles of a 14 continuous, central combustion engine (2 lifting cycles). wave

15 radial shaft seal

Fig. 5: Piston shape - examples: 16 rocker a, b: asymmetrical piston, 17 rocker bearing c, d, e: "shear-free" piston 18 membrane (for torque (here point-symmetrical) transmission) Fig. 6: Mechanical conversion 19 bellows (for torque ¬ the stroke in a rotary motion after transmission) claim 5. Compare also Figure 1. 20 anchors a and b show as examples two 21 stator different types of Längenaus¬ 22 drive to generate the same. the piston rotation

23 piston rod

7 and 8: Generation of the rotary 24 axial bearing stroke movement of the piston according to claim 25 crosshead 6. Schematic examples. 26 crosshead slideway 27 -

Figure 9: Mechanical conversion 27 connecting rod of the stroke into a rotary motion 28 crankshaft according to claim 7. Example with 29 valve disk-like cam track, 30 suction channel via hollow one stroke cycle per revolution. wave

31 rotating, inner

Picture 10: like picture 9, but with pre-compression piston two stroke cycles per revolution. 32 Check valve

33 outlet duct of the ver¬

Fig. 11: like Fig. 9, but with compressed medium curve path as a circumferential groove. from the rotary piston.

34 inlet channel of the front

Figure 12: Connection of the guide-compressed medium with rockers (claim 13) in the working space of the cylinder

Fig. 13: Schematic example of a swashplate-type 35 swash-plate rotary piston shaft, disk-shaped engine with four working spaces, sunk in the piston. shown swashplate-like different by half a shaft rotation 36. Shaft, movement conversion in piston reduced according to An¬. saying 7. See also Figure 1. 37 geometric center axis of the tau elschei-

Figure 14: Example of a combustion chamber-like shaft design for a diesel transmission element with generation of a 39 articulation point between turbulence in the toroidal vortex chamber (43). ment and the cylinder above: cuts through both 40 hollow shaft pistons at the top dead center of the stroke. 41 geometric middle - bottom: view of the front axis of the hollow shaft side of the lower piston. (intersects the cylinder axis)

Fig. 15: Torque transmission 42 Joint point between the central shaft and the piston, the piston and the one with diaphragm (a), with bellows (b). Hollow shaft - 28 -

Figure 16: Integrated precompression 43 toroidal vortex according to claim 3, 8, 14 and 16 space with an inner, rotating piston in the 44 magnetic pole, which guides the rotary piston, schematic anchor example. 45 magnetic pole, which drives the armature

Figure 17: Rotary reciprocating machine designation as an example: with electrical generation of the "N" = north pole rotary stroke movement according to claim 4. "S" = south pole On the left, the control of the auxiliary winding for starting change is conventionally shown with valves , right hand according to claim 1. The outer surface of the armature is axially guided through the concentrated magnetic field of the stator.

Figure 18: Generation of the rotary stroke movement according to claim 4 and 9. Example of non-permanently magnetic, but magnetizable anchors. One stroke cycle per revolution. The auxiliary winding (46) is only used to start the machine.

Image 19: as image, but as a difference with two additional places where driver poles (45) are arranged. The driver poles are shifted in time from one another (out of phase). Auxiliary windings for the start are not necessary.

Figure 20: Generation of the rotary stroke movement according to claim 4 and 9. The armature is not permanently magnetic, but can be magnetized. Two lifting cycles per revolution. Two guide poles (44) and two locations on the stator where the stator drives the armature (45).

Picture 21: like picture 20, but with 4 places that drive the anchor. Example with multi-phase alternating current (three-phase current).

Figure 22: Shape of the anchor of Figures 20 and 21. Note the analogy to the shape of the cam track according to claim 7, Figure 2 b.

Claims

 - 29 -

PATENT CLAIMS

Piston machine, with one or more working spaces per cylinder, usable as power or working machine, characterized in that pistons rotating synchronously with one another about the cylinder central axis delimit the working space or the working spaces on both sides, at least one of the two pistons delimiting a working space also in addition to the rotary movement executes an oscillating stroke movement parallel to the cylinder axis, and that at least one of these two pistons controls one or more openings in the cylinder wall by covering or uncovering openings with its outer surface during each working cycle, the end faces of both pistons being shaped in this way, that the edge line which delimits the piston end face facing the working space and at the same time also the piston skirt surface and therefore acts as a control edge, is not in a plane perpendicular to the cylinder central axis, and that the end faces of the two pistons refer to their shape and their position in relation to one another, in the top dead center of the stroke, fit into one another in such a way that an arbitrarily small final volume is reached depending on the intended use of the machine, or that the working space is limited only on one end face by a piston described above, which is a Performs rotary movement or rotary-stroke movement and controls the openings in the cylinder jacket surface, and that the working space on the other end face is limited by an end face which does not rotate synchronously, the two end faces delimiting a working space with respect to their shape and their Position in relation to each other, in the top dead center of the stroke, so that a small final volume is reached. However, in order to avoid butt between the rotating and the non-rotating end face, the rotating piston in the area of the top dead center of the hub performs no or only as little rotary movement as the distance between the two end faces and the shape of the end faces allows, all of them Variants, the piston face is either shaped so that the static pressure of the working medium on the piston face causes a resultant force with axial and radial components, or so that the radial force components cancel each other out, so that only an axial force results on the piston .

Piston machine, with one or more working spaces per cylinder, usable as a power or working machine, characterized in that the piston carries out an oscillating stroke movement parallel to the cylinder axis and a rotary movement around the cylinder axis and controls one or more openings in the cylinder wall, by it covers or releases openings with its outer surface during each work cycle, the edge line which delimits the piston end face facing the work space and at the same time also the piston outer surface and therefore acts as a control edge, is not in one plane, but is also placed at the same time that the radial force components from the pressure of the working medium on the piston face cancel each other out, so that only an axial force results on the piston.

Piston machine with several working spaces per cylinder, usable as a working or power machine, characterized in that at least one piston, which carries out an oscillating stroke movement and a rotary movement about the cylinder axis, serves with its inner surfaces as a cylinder for an additional inner piston enclosed therein which on - 31 -

a central shaft or axis extending into the rotary piston or passing through the rotary piston is attached and therefore makes an oscillating lifting movement relative to the rotating piston surrounding it, as a result of which this internal system also acts as a working or power machine.

Device for converting an oscillating lifting movement into a rotary movement - or vice versa -, or for generating a lifting, rotating or rotating lifting movement by means of electrical energy or for generating electrical energy from the movements mentioned, in particular when used for the rotating lifting movement of the Piston in piston machines, characterized in that these functions are caused by an electric motor or electric generator, the armature of which rotates relative to the stator and at the same time performs an oscillating stroke movement, this rotational stroke movement being achieved in that the armature is shaped in this way is that the two edge lines, which axially delimit the lateral surface of the armature, are not in a plane perpendicular to the axis of rotation, so that the armature is arranged obliquely to the axis of rotation or has waves in the axial direction, and that a) the armature is stationary with it Magnetic poles or windings is u nd the outer surface of the armature is guided axially by concentrated magnetic force at one or more, usually stationary, locations of the stator, whereas at the locations of the stator where the outer surface of the armature executes an axial movement relative to the stator, this axial Movement is supported by the stator by means of an oscillating magnetic force effect acting axially or axially tangentially, or is not impeded by the stator field there not being centered or zero with respect to the axial width, or - 32 -

b) that the armature is made of magnetizable but not permanently magnetic material and has an approximately constant axial width on its outer surface, and that the stator acts on the armature with magnetic forces at at least two points on its circumference, namely as follows, that the stator magnetizes the armature by means of at least one concentrated magnetic field and thereby generates a whole number of pole pairs on the armature, and that at least one point on the stator where the outer surface of the armature moves relative to the stator and where the Armature due to the stator field has a pole, the stator acts by axially or axially tangentially acting oscillating magnetic force on the armature, or that, as an alternative to the variants mentioned, the externally arranged stator has the described functions and features of the armature and analogously to Anchor has the described functions and features of the stator.

Piston machine, in which the oscillating stroke movement of the piston relative to the cylinder is converted into a rotary movement about the cylinder central axis - or vice versa - whereby a rotary stroke movement occurs, characterized in that at least one swashplate-like shaft, the central axis of which Cylinder axis intersects at an intersection, is formed in the rotary piston or is connected to the rotary piston, that on this swashplate-like shaft a transmission element is rotatably mounted about the shaft axis, but otherwise without relative degrees of freedom of movement, and that this transmission element is also attached to the cylinder, in such a way that the transmission element is permitted pivoting movements about all three coordinate axes or at least about those two coordinate axes which lie in a plane perpendicular to the axis of the swashplate-like shaft, and - 33 -

that this articulated bearing point can be displaced in a geometrically guided manner approximately in the direction radially to the cylinder axis, or that the transmission element permits a change in length with regard to the distance between its mounting on the cylinder and its mounting on the shaft.

Piston machine, in which the oscillating stroke movement of the piston relative to the cylinder is converted into a rotary movement about the cylinder central axis - or vice versa - whereby a rotary stroke movement occurs, characterized in that at least one short hollow shaft is embedded in the cylinder or with it connected to the cylinder in such a way that it can be rotated about its own axis, its own axis intersecting the cylinder axis approximately at the center of the hollow shaft, that at least one such hollow shaft on the inside, at a point outside the cylinder center axis, on the rotation -Hubkolben is attached, in such a way that this mounting allows relative pivoting movements between the hollow shaft and the rotary piston around all three coordinate axes or at least about those two right-angled coordinate axes which lie in a plane perpendicular to the axis of rotation of the hollow shaft, and that this bearing point in approximately radial direction to the axis of the rotary Hu piston or in an approximately radial direction to the axis of rotation of the hollow shaft in a geometrically guided manner.

Piston machine according to one of claims 1, 2 or 3, characterized in that the oscillating stroke movement of the piston relative to the cylinder is converted into a rotary movement about the central cylinder axis - or vice versa - by means of at least one spatial cam track, which is supported on one or more guides, consisting of guide elements such as rollers or sliders, and rotates relative to these guides, the cam track being designed, for example, as a disk-shaped cam track or as a circumferential groove in which the guide engages.

8. Piston machine according to claim 3, characterized in that the control of the charge change takes place in at least one outer working space according to claim 1 or 2.

9. Piston machine according to claim 4, characterized in that the machine is constructed as a DC machine or as a single-phase or multi-phase AC machine and that the whole number n places where the stator axially guides the outer surface of the armature is equal to the number There are n identical stroke cycles per revolution, and that these n guide points are arranged fixedly on the stator at identical angular distances with respect to the axis of rotation, and that in the variant with a non-permanent-magnet, coil-free armature, a) in the case of the direct current Machine either at all n guide points of the stator the polarity remains constant and between the guide points a whole number of axially or axially tangentially acting, driving magnetic forces from the stator act on the armature by two coils lying axially next to each other at these driver points that attract or repel the magnetized armature with different polarities and you By changing the polarity periodically change their polarity, or that all n command points change their polarity periodically, while the 2 poles at the stator driver points remain constant. b) in the single-phase alternating current machine, the arrangement of the poles is analogous to the direct current machine, but the polarity changes due to the current profile, with the current being rectified for the constant magnetic poles, or a permanent magnet being used, c) in the multiphase three-phase current -Machine, the poles of the n axial guide points of the stator remain constant and the driving fields lying between them are generated by several coils, arranged axially next to each other, which generate an axially moving field by means of three-phase current and move the armature with it either the direction of the three-phase current or the polarity of the guide points is changed for the dead center of movement, with one or more auxiliary coils, which, for example, relative to, are required for certain types of starting or starting the machine or for determining the direction of rotation the other coils are offset by an angle with respect to the axis of rotation, are placed on the stator n.

10. Piston machine according to claim 5, characterized in that the radial bearing surface of the swash plate-like shaft is formed between the axial guide surfaces, so that the transmission element is embedded between the axial guide surfaces and takes over the axial guidance with its side surfaces, or that Swashplate-like shaft is shaped like a circular disk, which is encompassed by the transmission element from the outside, so that the circular disk jacket surface serves as a radial bearing surface and the outer region of the two side surfaces serves as an axial bearing surface, the transmission element in both variants is mounted on the swashplate-like shaft with plain bearings or, for example, in a correspondingly adapted construction, with roller bearings. 11. Piston machine according to claim 5 or 10, characterized in that the swash plate-like shaft and the transmission element mounted thereon are designed such that they together form an electric motor or electric generator, so that a torque is generated between these two parts as a result of magnetic force , whereby the piston movement is generated from electrical energy, or conversely electrical energy is generated from the piston movement,

12. Piston machine according to claim 6, characterized in that the power transmission of the machine to the outside takes place through the rotating hollow shaft, for example mechanically by means of gear wheels, or by the hollow shaft and its mounting in the cylinder being designed such that they together form an electric motor or electric generator, whereby the rotation of the hollow shaft or the rotation of the hollow shaft generates electrical energy by means of electrical energy.

13. Piston machine according to claim 7, characterized in that guide rollers or sliders are connected to one another by rocking.

14. Piston machine according to one of claims 1, 2, 3 or 8, characterized in that the associated piston movements according to claim 4, 5, 6, 7, 9, 10, 11, 12 or 13 arise. 15. Piston machine according to one of claims 1, 2, 3, 7, 8, 13 or 14, characterized in that the piston shape and the number of lifting cycles per revolution are based on the intended use and the working method of the machine, for example 2-stroke or 4 Cycle, is coordinated such that the sequence of the control of openings in the cylinder wall, which is dependent on the piston movement and the piston shape, is repeated periodically with the working cycle of the machine, namely in that, for example, the piston in a 4-stroke engine has two stroke cycles per cycle Revolution and with a 2-stroke machine, a compressor or a pump, one stroke cycle per revolution, and with a 2-stroke internal combustion engine, which controls the gas exchange with the rotary piston and not with only a rotating piston, half a stroke cycle per revolution, for those piston shapes in which the shape of the edge line which is effective for the control and which delimits the piston jacket surface on the front side, n repeats geometrically periodically after a fraction of a revolution, the stated number of lifting cycles does not apply per revolution but per corresponding fraction of a revolution.

16. Piston machine according to one of claims 1, 2, 3, 7, 8, 13, 14 or 15, characterized in that the ability of the piston, through its shape and through its rotary movement or rotary stroke movement, to open openings in the cylinder wall as desired control is used to fulfill the following purposes, namely to let the working medium, sorted according to the content of internal energy, flow out into various outlet channels, so that, for example, in the case of the internal combustion engine after combustion, the exhaust gas passages, which are still high in energy, exert high pressure on the exhaust gas turbocharger are fed and then the remaining exhaust gases are discharged into another duct under low pressure, - 38 -

and / or in order to regulate output or volume, instead of throttling the working medium lossily during suction, to let the unthrottled working medium flow out again at the beginning of the compression stroke through an opening in the cylinder wall - or through several staggered openings - which one with throttle valves or the like can close, and / or to allow additional media to flow into the working medium at certain times.

17. Piston machine according to one of claims 1 to 16, characterized in that the rotation or swirling, which is caused by the rotation of the piston and = if present = the central shaft, is reinforced by a corresponding design of the surface of the working medium facing piston end faces, by a corresponding design of the surface of the central shaft, and / or = if present = by the arrangement of the inlet channels in a tangential-radial direction to the cylinder axis, and / or that additional rotational movements or eddies of the working medium are also generated in other rotational axes are designed in such a way that the two end faces which delimit the working space on both sides are designed in such a way that the working medium squeezed out of narrow squeezing areas flows into a whirling space in the top dead center of the stroke in such a way that in every theoretical section plane it is considered which goes through the whirling space perpendicular to the rotation ¬ axis of the vortex thus generated, the working medium flows from different sides tangentially into the vortex space, this vortex space having, for example, the shape of a torus. - 39 -

18. Piston machine according to one of claims 4 ... 7 or 9 ... 17, characterized in that the kinematics of the oscillating stroke movement relative to the rotary movement is adapted to the intended use and the working method of the machine, namely a) after the machine Claim 4 or 9 by the shape of the armature or the stator, b) in the machine according to claim 7 or 13 by the shape of the cam track, c) in the machine according to claim 5, 10 or 11 by the choice of the angle of the central axis swashplate-like shaft to the cylinder axis, and by the distance between the intersection of these two axes and the joint that connects the transmission element to the cylinder, by the design of this articulated connection, particularly the longitudinal displaceability, and by the creation of an - otherwise actually not required - distance between the theoretical plane, which passes through the intersection mentioned and perpendicular to the central axis of the ta standing disk-like shaft, and the joint, whereby - in the case of a structural opening of the joint into several joints with separate functions - the decisive joint is the one which the guide element mentions the pivoting movement about an axis radially to one of the two Central axes allowed, d) in a machine according to claim 6 or 12, in analogy to the machine according to claim 5, by the choice of the angle of the axis of rotation of the hollow shaft to the cylinder axis, and by the distance between the intersection of these two central axes and the articulated connection of the piston with the hollow shaft, by the design of this articulated connection, particularly the longitudinal displaceability, and by the creation of an otherwise not actually necessary distance between the theoretical plane, which goes through the intersection mentioned and perpendicular - 40 -

is to the central axis of the hollow shaft, and the joint, whereby - in the case of a structural separation of the joint into several joints with separate functions - the relevant joint is the one which allows the guide element to pivot about an axis radially to one of the two central axes.

19. Piston machine according to one of claims 1 to 18, characterized in that the synchronization between the piston rotation and the stroke movement is variable, for example to change the timing by the machine according to claim 4 ... 7 or 9 ... 13 that part of the device which is attached to the cylinder and which causes the rotary stroke movement of the piston is rotated relative to the cylinder about the cylinder axis, or in that the part of the device which is attached to the piston and which causes the rotary stroke movement of the piston relative to the end face of the piston is rotated about the cylinder axis.

20. Piston machine according to one of claims 4..7 or 9..19, characterized in that the length of the stroke and / or the compression ratio is adjustable, in the machine according to claim 4 or 9 by axial displacement of magnetic poles or by means of magnetic poles which can be optionally switched on and off, or by adjusting the strength of the magnetic forces which bring about the axial force of the piston, so that, owing to the external axial force on the piston and owing to the inertia of the piston, the effective piston stroke can be varied deviates from the theoretical piston stroke, in the machine according to claim 5, 10 or 11, or 6 or 12, by adjusting the angle which the central axis of the swashplate-like shaft or the central axis of the hollow - 41 -

has shaft to the cylinder axis by the swash plate-like shaft or the hollow shaft is pivotally mounted, or by the adjustment of geometric lengths listed in claim 16, which affect the kinematics, especially by adjusting the distance between the joint and the mentioned axis intersection.

21. Piston machine according to one of claims 1 to 20, characterized in that the rotary movement of the piston or the piston is transmitted to one or both outer end faces of the machine by means of a shaft leading through the cylinder central axis, which is designed in this way, that a torque is transmitted between the piston and the shaft and the oscillating stroke movement is guaranteed by an axial displaceability.

22. Piston machine according to claim 21, characterized in that the torque is transmitted from the piston to the central shaft leading through the cylinder axis either by means of a spline shaft or a shaped shaft, or by means of rolling elements which transmit tangential forces and move in a rolling manner during the axial displacement , or by means of longitudinally displaceable homokinetic joints.

23. Piston machine according to one of claims 1 to 22, characterized in that the torque transmission from the piston to the central shaft leading through the cylinder axis, or the direct torque transmission between two adjacent pistons, by means of one or more diaphragms or bellows / rolling bellows or others spring-like elements take place, which allow the axial longitudinal displacement by elastic deformation. 24. Piston machine according to one of claims 1 to 23, characterized in that the rotary movement of the piston about the cylinder axis by tangential force on the piston, or on another part rotating about this axis, transmitted to the outside, or is generated from the outside, or that one of the rotating parts forms part of an electric motor or electric generator.

25. Piston machine according to one of claims 1 to 24, characterized in that the torque transmission between the pistons takes place by means of a positive fit by the two adjacent piston end faces also meshing in the lower dead center of the stroke and thus transmitting tangential forces by means of sliding surfaces or indirectly by means of rolling elements.

26. Piston machine according to one of claims 1 to 25, characterized in that, in order to reduce friction, the rotating piston and the rotary reciprocating piston rests on a lubricating film which is located in that region of the cylinder wall where there are no openings to be controlled, the lubricant = if it must not get into the work area = through a scraper ring or the like is kept away from the work area.

27. Piston machine according to one of claims 3..6, 9..12, 18, or 20..24, characterized in that the piston does not rotate relative to the cylinder by the piston or the cylinder being rotatably connected to the device which generates the rotary stroke movement.