EP0240467A1 - Rotating-reciprocating 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

The key points of the rotary reciprocating piston machine are the simple conversion of the reciprocating motion of the piston into a rotary motion, which creates a rotary and reciprocating motion. In addition, the use of this piston movement for the direct control of the gas exchange by the piston: valves are 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 (equivalent 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 picture 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 load 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, when the piston movement is generated electrically 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 treated 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 also called "slot control"). The solution should be suitable for all known working processes and applications, including machines that compress the working medium in the cylinder. This requirement requires that the working space at the upper stroke dead center can be reduced to an arbitrarily small final volume.
The rotary piston 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.
Illustrative examples are shown in Figure 5.
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.
This means that 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.
Achieving the small final volume (often called "final compression volume"):
The working space is limited on one side by the rotary piston and on the other side by a piston that rotates synchronously but does not need to perform a lifting movement. At the top dead center, the surface shape of one piston fits into the surface of the other piston, which is designed as a negative shape. 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 hand by the piston, which makes a rotating or rotating stroke movement, on the other by a non-rotating end face. This can be a non-rotating piston or the cylinder head. To achieve a small final volume, these areas must also fit into one another as described above. The following measures are taken so that these two end faces do not collide at the top dead center of the stroke:
In this position, no or only a slight rotary movement may take place as the distance between the two end faces and the shape of the end faces allows. 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 as follows: Man he produces an oscillating stroke movement in a known manner and adds an arbitrary rotary movement to the piston with another known device. Example:
Large ship 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 additional drive (electric motor etc.) etc. etc.
Figure 2 shows a schematic example of this.
The rotary movement can be matched to the stroke movement. (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 rotary movement with a periodically alternating direction of rotation is also useful, which allows very large openings.
Lubrication : See point 26.
Sealing : Through 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 only has 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 that do not require a small final volume.
Solution: A rotary-reciprocating machine, in which the piston performs a rotary-stroke movement and controls the openings, whereby the piston geometry has two typical features:
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 by the rotary movement of the rotary stroke piston.
Secondly, low friction is achieved by simultaneously shaping the piston so 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. Incidentally, the second feature does not necessarily require symmetry of the piston face.

3rd and 8th Integrated piston engine inside the rotating-stroke piston, integrated supercharger

• a) mittels Turbo oder Kompressor
• b) mit einem in die Dreh-Hubkolben-Maschine integrierten, mechanischen Vorverdichter.

Possibilities of pre-compression (charging) on the rotary reciprocating machine:

• a) using turbo or compressor
• b) with a mechanical pre-compressor integrated in the rotary reciprocating machine.

Function of the integrated pre-compressor:

see example sketch of Fig. 16 and the detailed description on the next but one page.

General advantages of the integrated pre-compressor:

- Zero space requirement: 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.
- Simple and cheap.
- The gas cushion in the pre-compressor improves the smooth running of the machine under certain conditions.
- The outlet control via the rotary piston enables different systems to be fed with different pressure levels. (See also claim 16).

Applications

- Two-stage compressors.
- Pump or compress 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:
  (NB: Claim 8 is the integration of the inner piston machine (integrated precompressor) into a rotary 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:
  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 combustion of an overall extremely lean mixture,
  - 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 pre-compressor also 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: Use 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 as a compressor (e.g. as an oil pump, hydraulic pump, etc.).

Constructive

- Check valves in the pre-compression 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.

Rotary reciprocating machine with integrated pre-compressor ( description of the schematic diagram, figure 16)

The rotary 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; however, it can still transmit a torque to the shaft (not visible in the picture, dealt with 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. (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 are used to control 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.

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 shaft rotation drives a pump, for example. In the pump, the shaft rotation must be converted mechanically, for example by means of a crank mechanism, into a stroke movement. 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 an engine:

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 piston (for example according to claim 2) can be built with only one moving part: the rotary piston !!

- generator:

The rotary piston 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 :

• a) Der Anker ist mit ortsfesten Magnetpolen versehen.
  Das heisst, der Anker enthält entweder Wicklungen, oder ist mit Dauermagneten versehen bzw. ist dauermagnetisiert.
• b) Der Anker ist zwar magnetisierbar, aber nicht dauermagne­tisch. Das heisst, er besteht aus einem Werkstoff mit geringer magnetischer Remanenz.

The anchor is specially shaped, see examples 20 and 22. This is the important, characteristic peculiarity.
We differentiate between two anchor types:

• a) The armature is provided with fixed magnetic poles.
  This means that the armature either contains windings, is provided with permanent magnets or is permanently magnetized.
• b) The armature is magnetizable, but not permanently magnetic. This means that 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 outer 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 not only acts 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 surface of the armature. Not only do they 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 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 with magnetic poles on the anchor.
Due to the special shape of the armature according to claim 4, such electric motors can be realized. See Figures 18 to 21. At 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, ie an even number of magnetic poles. The driving forces do not work in a purely tangential direction, as with a conventional electric motor. (NB: 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. Due to the shape of the anchor, this tangential force component is created automatically, unless the anchor is 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 armature outer surface 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 min. 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 electronic, for example regulated and kept constant by varying the magnetic forces. As a result, this device also serves as a magnetic, practically frictionless magnet warehouse. With two such devices, the shaft or the piston is stored cleanly.
In Figure 21 we again have two guide poles, but three points on the stator that drive the armature. In such machines, care must be taken 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. This allows the armature to exert or withstand high axial forces. If the driving magnetic stator forces always have an attractive effect on the armature, the driving poles actually take on axial guiding tasks. According to this principle, machines can also be implemented that no longer have actual, fixed guide poles on the stator, but only wandering, driving fields that 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 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 drifts with its magnet fields the stator so that the stator makes a rotary-lifting movement relative to the armature, etc. In most cases this is the less favorable design: the external stator is usually 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 Figures 1 and 6):
The stroke movement in this rotary reciprocating machine is converted into a rotary movement as follows (or vice versa): The swashplate-like shaft (Figure 1, Item 35 or Figure 6, Item 37) is firmly connected to the piston or is 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 swash plate-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. Examples 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 only transmits 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).
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 joint 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 : Engines:

The joint in Figure 1 is intentionally drawn very large. On the one hand, the function can be seen better. On the other hand, this is to illustrate that this device can be dimensioned very firmly and is therefore also suitable for large engines, for example for ships. (Items 37 and 38 can also be dimensioned to any size). The slim design is also ideal for deep installation lengthways in the keel. The slim design and low weight are also interesting for aircraft engines and vehicle engines, etc.
In addition, there are the other advantages of the rotary piston engine, for example the simple 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 ideal for petroleum pumps, for example.

Variants:

- Two such devices per rotary piston, with the joints diametrically opposite. This compensates for the eccentricity of the axial force on the piston.
- Swash plate-like shaft and transmission element together form an electric motor or electric generator. (Claim 11).

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

Function :

For 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, for example the articulation point (item 42), you will 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 to claim 5:

- The axial space requirement in the cylinder is less here. This allows the rotary piston to be made shorter.
- The constructive application of force to the piston is different
- The joint rotates around the cylinder axis.

Variants :

- The arrangement of two such devices per rotary piston is also possible here. This can compensate for the eccentric application of force to the piston.
- 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.

7., 13. A spatial cam track (Fig. 9..11, item 3) is responsible for the piston movement, for example in the form of a cam disc 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 also 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 :

It goes without saying that the claims mentioned for generating the rotary / lifting 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. Match slot control, piston shape and movement

• a) The decisive factor is the gas exchange and the piston shape:
  In 2-stroke engines, pumps and compressors, a work cycle (consisting of two cycles) is completed after the piston has been reciprocated.
  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.
  Now that the rotation of the pistons determines the control of the gas exchange, and since the "program" for the control of the gas exchange as a period comprises an entire work cycle, it is best if the (asymmetrical) pistons make one revolution per work cycle.
  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. (Analog, with appropriate 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 point, 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. So this means that the piston should make two revolutions per stroke cycle (half a stroke cycle per revolution). Or that one can choose a "shear force-free" 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.
• b) (Welcome) effects on the number of tours:
  For a given stroke frequency, the number of revolutions of the shaft is determined by the number of stroke cycles per revolution, or vice versa.
  For pumps and compressors, for example, the stroke frequency can be increased for a given number of revolutions.
  For propeller drives in aircraft and for propeller drives, a slow shaft speed is desired due to the propeller or screw efficiency. - However, slow-running motors 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 in particular for use in aircraft:
  - The very slim, cylindrical motor contour with a central (propeller) shaft, which can be integrated into the wings in a flow-friendly manner. (With the rotary piston engine, 4, 6, 8 or more combustion chambers and a corresponding number of pistons can be installed in a cylinder without any problems).
  - 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 manifold 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 manifold. As a result, a lot of useful energy is lost.
  It is better if the pressure in the exhaust manifold is relatively high in this first phase. This gives the exhaust gas turbocharger more energy. If the pressure in the exhaust manifold does not exceed approximately half the cylinder pressure, the speed of sound is still 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:
  The high back pressure now complicates the ejection stroke of the piston. 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 channel. In the simplest case, it leads directly to the outside via a silencer. Due to the higher exploitation of the exhaust gas energy in the first phase, the turbo receives enough energy and therefore does not need 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 change.
  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 so that the exhaust gas flows out at the speed of sound at full load and at a 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 become linear with the speed. For this, the number of openings per unit of time increases linearly. As a result, 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 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 realized with compressors: one 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: In order to be able to reduce the cylinder charge and thereby the power (partial load), throttle valves are used in the intake duct today. The negative pressure created by throttling during suction results in efficiency losses. With the rotary reciprocating piston engine, you 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 that 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: acts 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 protect valves, nozzles, igniters, sensors etc. from the high combustion temperatures or the high pressures.

17. Increasing the rotation of the medium

• a) Beim Verbrennungsmotor wird die schnelle Ausbreitung der Ver­brennung und die Zündwilligkeit, vor allem bei mageren Gemi­schen, wesentlich gesteigert, wenn das Arbeitsmedium kräftig verwirbelt wird. Siehe Bild 14.
  Man kann sogar anstreben, dass die Trägheitskräfte (Zentrifu­genwirkung) eine Schichtung der Ladung erzeugen, d.h. dass an der Peripherie bie der Zündkerze das Gemisch reicher und da­mit zündwilliger ist als im Zentrum des Arbeitsraumes.
• b) Bei Pumpen und Verdichtern kann man durch das Umrühren für bestimmte Einsatzzwecke
  - eine Entmischung des Pumpmediums oder eine Sedimentation verhindern
  - mit hohen Umfangsgeschwindigkeiten ein gezieltes Auszentri­fugieren des Mediums bewirken.
  - Vernetzungsvorgänge im Pumpmedium während des Pumpens verhindern
  - das Festkleben oder Angefrieren des Mediums an der Zylin­derwänden verhindern
  - Durch ein sich gegen die Zylinderwand hin konisch vergrös­serndes Endvolumen im oberen Totpunkt, wird bei zähflüssi­gen Pumpmedien zudem das radiale Ausstossen erleichtert.

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 the combustion and the ignitability, especially in the case of lean mixtures, is significantly increased if the working medium is vigorously swirled. See picture 14.
  One can even strive for the inertial forces (centrifuge effect) to create a stratification of the load, ie that the mixture at the periphery near the spark plug 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 pumping medium or sedimentation
  - Effectively centrifuging 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
  - With a conically increasing end volume at top dead center towards the cylinder wall, radial ejection is also made easier with viscous pumping media.

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, a different course of the piston movement, ie a different stroke kinematics, would be desirable.
The lifting kinematics of the rotary reciprocating machine according to claims 4, 9, 7 and 13 can be chosen freely and match the application. In the other claims regarding the generation of the piston movement, the lifting kinematics can also be selected to a certain extent. Claim 18 mentions the geometric sizes with which the lifting kinematics of these systems are influenced. Application examples are also listed.

19. The purpose of changing the synchronization between piston rotation and the lifting movement can be, 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 a reverse gear (e.g. large marine diesel).

20. Stroke adjustment:

Stroke length adjustment devices are normally used to change the delivery volume of a pump or the displacement volume of a (hydraulic) motor, for example in hydrostatic transmissions.

Transmission of the piston rotation to the outside

21. We have seen that the piston is rotating and lifting. The transmission of the rotation of the piston from the inside of the machine is the subject of this point:
Imagine a central shaft that goes through the machine on the central axis of the cylinder and leads outwards at one end of the machine (or at both ends). 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 let the shaft take part in the stroke movement of the piston and then compensate for the stroke movement of the shaft at another point, for example on the front of the machine.
The shaft is easily sealed, for example with rod seals (analogous to the piston rings on the reciprocating piston engine, but with an internal 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 so that the lifting movement also runs with little friction. Such a construction would, for example, be designed in a similar way to the homokinetic shaft joints with length compensation, which are known from car front wheel drive. This construction also compensates for misalignments.

23. Diaphragms or bellows (see Figure 15 a and b) can also transmit the torque with their torsional rigidity (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, for example by attaching 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 be transmitted electromagnetically to the outside directly via the outer surface of the rotary piston and converted into electrical energy (or vice versa).
A motion transmission, especially for the rotary piston 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 "claw clutch". Piston shapes according to Figure 5 c..e are suitable for this, for example.
Piston shape and stroke length must be coordinated so that the pistons remain engaged with each other at every stroke position.
In order to reduce the friction, the force can be transmitted indirectly via rolling elements instead of directly via sliding surfaces 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 usually occurs here with 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 transverse 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 type of construction whether lateral forces occur at all:
Shear forces are present on 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, without any problems and with little friction.
No lateral forces normally arise 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 (eg point symmetry) (Fig. 5 c..e).
Back to the lubrication: In order to prevent the lubricant from getting into the work area or the outlet openings, a scraper ring is installed in the cylinder.

• Bild 1: Schematische Zeichnung eines 2-Takt - Dreh-Hubkolben-Motors mit vier Arbeiträumen, Ladungswechsel nach Anspruch 1, Erzeugung der Kolbenbewegung nach Anspruch 5. (Vgl. auch Bild 13)
• Bild 2: Illustration der Steuerung des Gaswechsels mit den Kolben. Die Kolbenbewegung wird mit einem konventionellen Kreuzkopf-Kurbeltrieb erzeugt. Zusätzlich wird wird eine Drehbewegung überlagert.
• Bild 3: Schema des Ladungswechsels bei einer Pumpe. Gleichzeitig findet ein Hubzyklus statt. Jede halbe Hublänge ist gezeichnet.
• Bild 4: Schema der 4 Takte eines Verbrennungsmotors (2 Hubzyklen).
• Bild 5: Kolbenform - Beispiele:
  a, b: asymmetrische Kolben,
  c,d,e: "querkraftfreie" Kolben (hier punktsymmetrisch)
• Bild 6: Mechanische Umwandlung der Hub- in eine Drehbewegung nach Anspruch 5. Vergleiche auch Bild 1.
  a und b zeigen als Beispiele zwei verschiedene Arten des Längenausgleichs.
• Bild 7 und 8: Erzeugung der Dreh-Hub-Bewegung des Kolbens nach Anspruch 6. Schematische Beispiele.
• Bild 9: Mechanische Umwandlung der Hub- in eine Drehbewegung nach Anspruch 7. Beispiel mit scheibenähnlicher Kurvenbahn, ein Hubzyklus pro Umdrehung.
• Bild 10: wie Bild 9, aber mit zwei Hubzyklen pro Umdrehung.
• Bild 11: wie Bild 9, aber mit Kurvenbahn als umlaufende Nut.
• Bild 12: Verbindung der Führungen mit Wippen (Anspruch 13)
• Bild 13: Schematische Beispiel eines 2-Takt - Dreh-Hubkolben-Motors mit vier Arbeitsräumen, um eine halbe Wellendrehung unterschiedlich dargestellt. Bewegungsumwndlung nach Anspruch 7. Vgl. auch Bild 1.
• Bild 14: Beispiel einer Brennraumgestaltung für einen Dieselmotor mit Erzeugung von Turbulenz im torusförmigen Wirbelraum (43).
  Oben: Schnitte je durch beide Kolben im oberen Hubtotpunkt.
  Unten: Anschicht auf die Stirnseite des unteren Kolbens.
• Bild 15: Drehmomentübertragung zw. zentraler Welle und Kolben mit Membrane (a), mit Balg (b).
• Bild 16: Integrierter Vorverdichter nach Anspruch 3, 8, 14 und 16 mit innerem, drehenden Kolben im Dreh-Hubkolben, schematisches Beispiel.
• Bild 17: Dreh-Hubkolben-Maschine mit elektrischer Erzeugung der Dreh-Hubbewegung nach Anspruch 4. Links ist die Steuerung des Ladungswechsels konventionell mit Ventilen dargestellt, rechts gemäss Anspruch 1. Die Mantelfläche des Ankers ist oben durch das konzentrierte Magnetfeld des Stators axial geführt.
• Bild 18: Erzeugung der Dreh-Hubbewegung nach Anspruch 4 und 9. Beispiel für nicht dauermagnetischen, aber magnetisierbaren An­ker. Ein Hubzyklus pro Umdrehung. Die Hilfswicklung (46) dient nur für den Start der Maschine.
• Bild 19: wie Bild, aber als Unterschied mit zwei zusätzlichen Stellen, an denen Treiberpole (45) angeordnet sind. Die Treiber­pole werden zueinander zeitlich verschoben (phasenverschoben) angesteuert. Hilfswicklungen für den Start sind nicht nötig.
• Bild 20: Erzeugung der Dreh-Hubbewegung nach Anspruch 4 und 9. Der Anker ist nicht dauermagnetisch, aber magnetisierbar. Zwei Hubzyklen pro Umdrehung. Zwei Führungspole (44) und zwei Stellen am Stator, wo der Stator den Anker treibt (45).
• Bild 21: wie Bild 20, aber mit 4 Stellen, die den Anker treiben. Beispiel mit Mehrphasen-Wechselstrom (Drehstrom).
• Bild 22: Form des Ankers von Bild 20 und 21. Beachte die Analo­gie zur Form der Kurvenbahn nach Anspruch 7, Bild 2 b.

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.

• Figure 1 : Schematic drawing of a two-stroke rotary piston engine with four working spaces, charge change according to claim 1, generation of the piston movement according to claim 5. (See also Figure 13)
• Figure 2 : Illustration of the control of the gas exchange with the pistons. The piston movement is generated with a conventional crosshead crank drive. In addition, a rotary movement is superimposed.
• Figure 3 : Scheme of the charge change for a pump. A lifting cycle takes place at the same time. Every half stroke length is drawn.
• Fig. 4 : Scheme of the 4 cycles of an internal combustion engine (2 lifting cycles).
• Figure 5 : Piston shape - examples:
  a, b: asymmetrical pistons,
  c, d, e: "shear-free" pistons (here point-symmetrical)
• Figure 6 : Mechanical conversion of the stroke into a rotary motion according to claim 5. Compare also Figure 1.
  a and b show two different types of length compensation as examples.
• 7 and 8 : Generation of the rotary-stroke movement of the piston according to claim 6. Schematic examples.
• Figure 9 : Mechanical conversion of the stroke into a rotary movement according to claim 7. Example with a disc-like cam track, one stroke cycle per revolution.
• Picture 10 : like picture 9, but with two lifting cycles per revolution.
• Picture 11 : like picture 9, but with curved track as a circumferential groove.
• Figure 12 : Connection of the guides with rockers (claim 13)
• Figure 13 : Schematic example of a 2-stroke rotary piston engine with four working spaces, shown differently by half a shaft rotation. Movement conversion according to claim 7. See also Figure 1.
• Figure 14 : Example of a combustion chamber design for a diesel engine with turbulence generation in the toroidal swirl chamber (43).
  Above: cuts through both pistons at the top dead center.
  Bottom: Layer on the face of the lower piston.
• Figure 15 : Torque transmission between the central shaft and piston with diaphragm (a), with bellows (b).
• Figure 16 : Integrated pre-compressor according to claim 3, 8, 14 and 16 with an inner, rotating piston in the rotary piston, schematic example.
• Figure 17 : Rotary reciprocating machine with electrical generation of the rotary stroke movement according to claim 4. The control of the charge exchange is shown conventionally on the left with valves, on the right according to claim 1. The outer surface of the armature is guided axially 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 armature. One stroke cycle per revolution. The auxiliary winding (46) is only used to start the machine.
• Image 19 : like 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.

Caption

1 cylinder
1a, b, c cylinder parts
2 rotary pistons (makes rotary-stroke movement)
3 curved track
4 tours
5 pistons, only rotating
6 piston rings
7 work space
7a same, maximum volume
7b ditto, final volume or final compression volume
8 inlet duct
9 outlet duct
10 inlet flow
11 outlet flow
12 spark plugs
13 injector (diesel)
14 continuous, central wave
15 radial shaft seal
16 seesaw
17 Rocker storage
18 diaphragm (for torque transmission)
19 bellows (for torque transmission)
20 anchors
21 stator
22 Drive for generating the piston rotation
23 piston rod
24 thrust bearings
25 crosshead
26 crosshead slideway
27 connecting rod
28 crankshaft
29 valve
30 intake duct via hollow shaft
31 rotating inner pre-compression piston
32 Check valve
33 Outlet channel of the compressed medium from the rotary piston.
34 Inlet channel of the pre-compressed medium into the working space of the cylinder
35 swashplate-like shaft, disc-shaped in piston.
36 swashplate-like shaft, sunk in the piston.
37 geometric center axis of the swashplate-like shaft
38 transmission element
39 pivot point between the transmission element and the cylinder
40 hollow shaft
41 geometric central axis of the hollow shaft (intersects the cylinder axis)
42 pivot point between the piston and the hollow shaft
43 toroidal vertebral space
44 magnetic pole, which guides the armature
45 magnetic pole, which drives the armature
"N" = North Pole
"S" = South Pole
46 Auxiliary winding for start

Claims (28)

1. piston machine, with one or more working spaces per cylinder, usable as a power or working machine,
characterized in that
Pistons rotating synchronously with each other around the cylinder central axis delimit the working area or the working areas on both sides,
wherein at least one of the two pistons delimiting a working space also performs an oscillating stroke movement parallel to the cylinder axis in addition to the rotary movement, and that at least one of these two pistons controls one or more openings in the cylinder wall by covering or opening openings with its outer surface during each working cycle,
the end faces of both pistons being shaped such 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, in terms of their shape and their position relative to one another, fit into one another at the top dead center of the stroke 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 only limited on one end face by a piston described above, which executes a rotary movement or a 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, in terms of their shape and their position relative to one another, fit into one another in the top dead center of the stroke in such a way that a small final volume is achieved, but in order to avoid a combination butt between the rotating and the non-rotating end face, the rotating piston in the area of the upper dead center of the stroke does not perform any or only a slight rotational movement as the distance between the two end faces and the shape of the end faces allows,
where, in all 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 an axial and radial component, or so that the radial force components cancel each other out so that only one axial force acts on the Piston results. 2. 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 covering or uncovering openings with its outer surface during each working cycle,
the edge line that delimits the piston end face facing the working chamber and at the same time also the piston skirt surface and therefore acts as a control edge, does not lie in one plane, but is also placed in such a way that the radial force components resulting from the pressure of the working medium are on the piston end face cancel each other out so that only one axial force results on the piston. 3. piston machine with several working spaces per cylinder, usable as working or power machine,
characterized,
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 acts on a central shaft or axis extending into the rotary piston or passing through the rotary piston is fastened 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. 4. Device for converting an oscillating stroke movement into a rotary movement - or vice versa -
or to generate a lifting, rotating or rotating lifting movement by means of electrical energy
or to generate electrical energy from the movements mentioned,
especially in use for the rotary stroke 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 lifting movement, this rotating lifting movement being achieved in that the armature is shaped in such a way that the two edge lines which form the outer surface of the armature limit axially, do not lie 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 designed with stationary magnetic poles or windings and the outer surface of the armature is guided axially by concentrated magnetic force at one or more, usually stationary, locations of the stator, with those locations of the stator where the outer surface of the armature is axial Executes movement relative to the stator, this axial movement is supported by the stator by means of axially or axially tangentially acting oscillating magnetic force action, or is not impeded by the stator field there, with respect to the axial width, not being concentrated or being zero, or 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 least two points on its circumference, namely in such a way that the stator passes through at least one concentrated magnetic field magnetizes the armature 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 has a pole as a result of the stator field, the stator acts on the armature by means of oscillating magnetic force acting axially or axially tangentially, or that, as an alternative to the variants mentioned, the stator arranged on the outside has the described functions and features of the armature and analogously the armature has the described functions and features of the stator. 5. 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 arises,
characterized in that
at least one swashplate-like shaft, the central axis of which intersects the cylinder axis at an intersection, is molded into the rotary piston or is connected to the rotary piston,
that a transmission element is rotatably mounted on this swashplate-like shaft 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
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
that this articulated bearing point can be moved in a geometrically guided manner approximately radially to the cylinder axis, or that the transmission element permits a change in length with respect to the distance between its mounting on the cylinder and its mounting on the shaft. 6. 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 arises,
characterized in that
at least one short hollow shaft is embedded in the cylinder or 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 its inside, at a point outside the cylinder center axis, on which rotary reciprocating pistons are attached, in such a way that
that this mounting permits relative pivoting movements between the hollow shaft and the rotary reciprocating 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 is displaceable in a geometrically guided manner in an approximately radial direction to the axis of the rotary reciprocating piston or in an approximately radial direction to the axis of rotation of the hollow shaft. 7. Piston machine according to one of claims 1, 2 or 3,
characterized,
that 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 -,
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,
wherein the cam track is 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 charge change is controlled in at least one outer work space according to claim 1 or 2. 9. Piston machine according to claim 4,
characterized in that
the machine is constructed as a direct current machine or as a single-phase or multi-phase alternating current machine and that the whole number n places where the stator axially guides the outer surface of the armature is equal to the number n identical lifting cycles per revolution, and that these n Guide points are arranged at identical angular intervals with respect to the axis of rotation in a stationary manner on the stator,
and that in the variant with non-permanent magnetic, coilless armature, a) in the DC machine
Either the polarity remains constant at all n guide points of the stator and a large number of axially or axially tangentially acting, driving magnetic forces from the stator act on the armature between the guide points, by two coils lying axially next to each other at these driver points different polarities attract or repel the magnetized armature and periodically change their polarity by changing the polarity, or that all n guide points change their polarity periodically together, while the two poles at the driver points of the stator remain constant, b) in the single-phase AC machine
the arrangement of the poles is analogous to the DC machine, but the polarity changes due to the current profile, the current being rectified for the constant magnetic poles, or a permanent magnet is used, c) in the multi-phase three-phase machine
the poles of the n axial guide points of the stator remain constant and the driving fields, which lie between them, are generated by several coils, which are arranged axially next to one another, which generate an axially moving field by means of three-phase current and move the armature, whereby either the Direction of the three-phase current or the polarity of the control points is changed,
whereby, in certain embodiments, one or more auxiliary coils are necessary for starting the machine or for determining the direction of rotation, which are placed on the stator, for example, offset relative to the other coils by an angle with respect to the axis of rotation. 10. Piston machine according to claim 5,
characterized,
that the radial bearing surface of the swashplate-like shaft is molded 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 the swashplate-like shaft is shaped like a circular disk, which is encompassed by the transmission element from the outside, so that the circular disk outer 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 being open in both variants the swashplate-like shaft with plain bearings or, for example, in a correspondingly adapted design, is mounted with roller bearings. 11. Piston machine according to claim 5 or 10,
characterized in that
the swashplate-like shaft and the transmission element mounted thereon are designed such that they together form an electric motor or electric generator, so that due to the action of magnetic force, a torque is generated between these two parts, whereby the piston movement is generated from electrical energy or, conversely, electrical energy is generated from the piston movement becomes, 12. Piston machine according to claim 6,
characterized in that
the machine transmits power externally through the rotating hollow shaft, for example mechanically by means of gears,
or in that the hollow shaft and its mounting in the cylinder are designed such that together they form an electric motor or electric generator, whereby electrical energy is used to generate the rotation of the hollow shaft, or electrical energy is generated by the rotation of the hollow shaft. 13. Piston machine according to claim 7,
characterized,
that guide rollers or gliders are connected to each other by rocking. 14. Piston machine according to one of claims 1, 2, 3 or 8,
characterized,
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 shape of the piston and the number of lifting cycles per revolution are matched to the intended use and the working method of the machine, for example 2-stroke or 4-stroke, so that the sequence of the control of openings in the cylinder wall, which is dependent on the movement of the piston and the shape of the piston, periodically changes repeated the machine cycle,
namely, for example, the piston makes two stroke cycles per revolution in a 4-stroke engine and one stroke cycle per revolution in a 2-stroke machine, a compressor or a pump, and in a 2-stroke internal combustion engine which rotates -Hub piston and not with a rotating piston controls the charge change, half a stroke cycle per revolution,
for those piston shapes in which the shape of the edge line effective for the control, which delimits the piston lateral surface at the front, repeats itself periodically after a fraction of a revolution, the stated number of stroke 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
that the ability of the piston, through its shape and through its rotary movement or rotary stroke movement, to control openings in the cylinder wall as desired, is used to achieve the following purposes, namely:
in order to allow the working medium, sorted by content of internal energy, to flow out into various outlet channels, so that, for example, in the case of the internal combustion engine after combustion, the exhaust pipes, which are still high in energy, are fed to the exhaust gas turbocharger under high pressure and the remaining exhaust gases are then discharged into another channel under low pressure ,
and / or, in order to regulate output or volume, instead of throttling the working medium at a loss, let the unthrottled working medium flow out again at the beginning of the compression cycle through an opening in the cylinder wall - or through several, staggered openings - which one with throttle valves or similar 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,
that the rotation or turbulence caused by the rotation of the piston and = if present = the central shaft is increased
by an appropriate design of the surface of the piston end faces facing the working medium,
by appropriate design of the surface of the central shaft, and / or = if available =
by the arrangement of the inlet channels in the tangential-radial direction to the cylinder axis, and / or
that additional rotational movements or swirling of the working medium are also generated in other axes of rotation, in 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 upper stroke dead center in such a way that in every theoretical cutting plane considered, which goes through the vertebral space and is perpendicular to the axis of rotation of the vertebrae generated in this way, the working medium flows tangentially into the vertebral space from different sides, this vertebral space having, for example, the shape of a torus. 18. Piston machine according to one of claims 4 ... 7 or 9 ... 17,
characterized,
that the kinematics of the oscillating lifting movement relative to the rotary movement is adapted to the intended use and the working method of the machine, namely a) in the machine according to 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 of the swash plate-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 this articulated connection, especially the longitudinal displaceability,
and by creating a - otherwise not actually necessary - distance between the theoretical plane, which passes through the intersection mentioned and is perpendicular to the central axis of the swashplate-like shaft, and the joint, whereby - in the case of a constructive separation of the joint into several joints with separate ones Functions - that joint is decisive that allows the guide element to pivot about an axis radially to one of the two central axes mentioned, d) in a machine according to claim 6 or 12, analogous 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 ,
through the design of this articulated connection, especially the longitudinal displaceability,
and by creating an otherwise unnecessary distance between the theoretical plane, which passes through the intersection mentioned and perpendicular 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 - that joint is decisive 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,
that the synchronization between the piston rotation and the stroke movement is variable, for example to change the timing,
in that, in the machine according to claim 4 ... 7 or 9 ... 13, the part of the device which is attached to the cylinder and which causes the rotary-lifting movement of the piston is rotated relative to the cylinder about the cylinder axis, or
by rotating the part of the device which is attached to the piston and which causes the rotary-lifting movement of the piston about the cylinder axis relative to the end face of the piston. 20. Piston machine according to one of claims 4..7 or 9..19,
characterized,
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 magnetic poles which can optionally be switched on and off,
or by adjusting the strength of the magnetic forces which cause the axial force of the piston so that, due to the external axial force on the piston and due to the inertia of the piston, the effective piston stroke deviates variably from the theoretical piston stroke,
in the machine according to claim 5, 10 or 11, or 6 or 12, by adjusting the angle, the central axis of the swash plate-like shaft or the central axis of the hollow 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 influence 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 pistons is transmitted to one or both outer end faces of the machine by means of a shaft which leads through the cylinder central axis and is designed in such a way that a torque is transmitted between the piston and the shaft and the oscillating stroke movement by means of an axial displacement is guaranteed. 22. Piston machine according to claim 21,
characterized in that
the torque transmission from the piston to the central shaft leading through the cylinder axis
either by spline or form wave,
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, takes place by means of one or more diaphragms or bellows / roller bellows or other spring-like elements which allow the axial longitudinal displacement due to elastic deformation. 24. Piston machine according to one of claims 1 to 23,
characterized,
that the rotational movement of the piston about the cylinder axis is transmitted to the outside by means of tangential force on the piston, or on another part rotating about this axis, 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 at the bottom 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,
that, in order to reduce friction, the rotating piston and the rotating reciprocating piston rests on a lubricating film which is located in that area of the cylinder wall where there are no openings to be controlled, the lubricant = if it must not get into the working area = by means of a scraper ring o. Ä. 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
that the piston does not rotate relative to the cylinder in that the piston or cylinder is rotatably connected to the device that generates the rotary stroke movement.

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