Rotary stroke piston positive displacement machine

Abstract

The invention relates to a piston machine (10) for taking in or outputting work from or to a gaseous or liquid working medium, comprising at least one cylinder (1) in which a piston (2) is arranged, the piston (2) being guided in a working chamber (3) of the cylinder (1) in such a way that it can perform both a reciprocating movement along the cylinder axis and a rotational movement about the cylinder axis, in particular a sinusoidal rotational stroke movement, the piston (2) being connected to a drive mechanism (9), in particular via a piston rod (29), for forced guidance of the piston (2) and for conversion of the rotational stroke movement into a rotational movement, the piston machine (10) having at least one inlet channel (4) for the working medium into the working chamber (3) and at least one outlet channel (5) for the working medium from the working chamber (3). According to the invention, the inlet channel (4) and the outlet channel (5) are arranged in the cylinder wall (11) in such a way that the piston (2) can sweep over the inlet channel (4) and the outlet channel (5) with its piston skirt (21) during its rotational stroke movement and can periodically, in particular completely, cover and reopen these channels, the inlet channel (4) and the outlet channel (5) being arranged and configured in such a way that they each achieve a dynamic seal relative to the working chamber (3) for the working medium independently of one another, the effective sealing surface between the piston skirt (21) and the inlet channel (4) and / or the outlet channel (5) being arranged around the inlet channel (4) and / or the outlet channel (5), respectively.

Description

Technical Field

[0001] The present invention relates to a piston engine according to the preamble of claim 1 for obtaining or outputting work from or to a gaseous or liquid working medium, an internal combustion engine according to the preamble of claim 20, a compressor according to the preamble of claim 21, and a steam expander according to the preamble of claim 22. Background Technology

[0002] Various rotary-stroke piston positive displacement machines are known in the prior art. In these machines, the working medium expands and applies force to the piston through pressure, and the piston is then subjected to rotary and stroke motions via a forced motion mechanism. For example, EP0240467A1 discloses such a rotary-stroke piston machine. In this machine, power output is achieved via a central shaft along which the rotary-stroke piston can move but is torsionally supported. Motion conversion is accomplished via a swashplate shaft and transmission elements.

[0003] Similar stroke piston machines known in the prior art are also found in US5517952A, US1572068A, EP0320171A1, and DE3038673A1. However, stroke piston machines with rotary stroke pistons, spool valve motors, and rotary spool valve control devices known in the prior art have not been widely applied beyond theoretical applications due to various problems. For example, known devices in the prior art cannot satisfactorily solve problems related to heat, lubrication, and excessive structural complexity, especially sealing. In particular, piston rings known in the prior art for sealing the working chamber relative to other machine parts cannot guarantee a satisfactory seal. Summary of the Invention

[0004] Therefore, the object of the present invention is to provide a universal stroke piston machine or positive displacement machine that can be used as both a working machine and a power machine, and eliminates the need for a complex valve train mechanism with, for example, a disc valve.

[0005] This objective is achieved by the piston machine according to the preamble of claim 1, utilizing the features described in its characteristic portion. According to the invention, the inlet and outlet passages are arranged within the cylinder wall such that the piston, during its rotational stroke, can sweep across the inlet and outlet passages with its piston skirt and periodically (especially completely) cover and reopen these passages; and wherein the inlet and outlet passages are arranged and constructed with the piston such that they are dynamically sealed independently of each other relative to the working chamber for the working medium, wherein the effective sealing surfaces between the piston skirt and the inlet and / or outlet passages are arranged around the inlet and / or outlet passages, respectively.

[0006] The advantages of the piston press according to the present invention are that it can perform both symmetrical and asymmetrical control of gaseous and liquid working media, and eliminates the need for the typically complex and fault-prone crankshaft transmission mechanism. Furthermore, the piston press according to the present invention has a compact structure, fewer moving parts, low operating and maintenance requirements, and high efficiency. Moreover, compared with known piston ring seals in the prior art, the sealing method of the inlet and outlet channels relative to the working chamber according to the present invention has advantages: it not only reliably avoids undesirable pressure loss and leakage in the working chamber, but also features a reliable and simple sealing design.

[0007] Because the inlet and outlet channels are both arranged within the cylinder wall according to the invention, the piston machine according to the invention is particularly small in size and requires less installation space, as it eliminates the clearance volume reserved for valves (e.g., disc valves) known in the prior art. Furthermore, the piston machine according to the invention essentially comprises only one reciprocating moving part (i.e., the piston), which is used both to control the working fluid and to apply and obtain expansion and compression forces. Simultaneously, due to the elimination of the crankshaft drive mechanism, the piston machine experiences minimal vibration during operation, and due to its compact structure and few moving parts, it eliminates the need for complex mass balancing as required by prior art piston machines.

[0008] In the context of this invention, the effective sealing surface should be understood as the surface that achieves a sealing effect between the piston skirt and the inlet and / or outlet channels. According to this invention, this sealing effect can be achieved either without contact or through a sealing element directly attached to the piston skirt. However, for this invention, the key point is that when the piston covers the inlet and / or outlet channels with its piston skirt, a sealing effect must be achieved around the inlet and / or outlet channels relative to the working chamber.

[0009] A particularly advantageous embodiment of the piston machine according to the invention is defined in more detail by the features of the dependent claims: A particularly simple sealing scheme is proposed: a piston machine has multiple sealing units, each of which has a sealing sleeve that can press against the piston skirt of the piston. Sealing units (especially sealing sleeves) are arranged around the inlet channel and around the outlet channel, respectively sealing the inlet and outlet channels relative to the working chamber. The sealing units (especially sealing sleeves) are constructed such that when the piston sweeps across the inlet and / or outlet channels, the sealing units are always in contact with the piston skirt at at least two points. Specifically, the sealing units (preferably sealing sleeves) are shaped into a spherical form to match the radius of the piston skirt.

[0010] By utilizing the sealing unit and rotary stroke mechanism, symmetrical and asymmetrical control timing of the working fluid or scavenging process relative to the piston's top dead center or bottom dead center can be achieved particularly easily, without the need for dedicated valve trains, disc valves, camshafts, etc. Therefore, the piston engine according to the present invention is suitable for internal combustion engines operating on a four-stroke principle, as well as for high-efficiency gas expanders operating using a regenerative cycle (CR cycle) or organic Rankine cycle (ORC cycle), and can also be used as a compressor.

[0011] The inlet and outlet channels can always remain sealed or isolated from the working chamber through the sealing unit (especially the sealing sleeve), thereby achieving a favorable seal. The sealing sleeve is preferably designed to be circular or elliptical and extends completely around the inlet of the inlet or outlet channel.

[0012] Preferably, the sealing unit can be configured with a spring, which presses the sealing unit (especially the sealing sleeve) against the piston skirt of the piston. By applying a force to the sealing unit in the direction of the piston through the spring, it is reliably ensured that the sealing unit or sealing sleeve always remains against the piston, thereby achieving dynamic sealing during the piston's rotational stroke using simple components.

[0013] To easily set the force of the sealing unit pressing against the piston and optimize friction, the sealing unit can be configured such that it is connected to the working chamber or inlet and / or outlet channel via a pressure transmission channel. The dominant pressure difference between the inlet or outlet channel and the working chamber can be transmitted through this channel to the sealing unit (especially the sealing sleeve), pressing the sealing unit (especially the sealing sleeve) against the piston skirt. Furthermore, this allows for a smaller spring, as the spring force can be compensated for by the pressure difference.

[0014] A preferred embodiment of a piston press is proposed: the piston has a piston base that is rearwardly offset relative to the piston's end face, such that the piston forms a cavity open towards the working chamber. The piston has at least one piston inlet channel constructed within the piston, which connects from the piston skirt to the cavity and / or to the piston base, allowing the working medium to flow into the working chamber when the piston sweeps through the inlet channel. The piston also has at least one piston outlet channel constructed within the piston, which connects from the cavity and / or from the piston base to the piston skirt, allowing the working medium to flow out of the working chamber when the piston sweeps through the outlet channel. This preferred embodiment of the piston with a rearwardly offset piston base allows for a particularly compact piston press structure, enabling the working medium to flow into the working chamber not only through the piston end face sweeping through the inlet or outlet channel, but also through the overlap of the inlet or outlet channel with the piston inlet or outlet channel in a controlled time.

[0015] To more effectively achieve asymmetrical control time, the following configuration can be made: the inlet and / or outlet channels can extend along a segment of the piston skirt's (preferably the piston inlet and / or piston outlet channels) trajectory (especially a sinusoidal trajectory), wherein, in particular, the inlets of the inlet and / or outlet channels leading to the cylinder have a sinusoidal extension shape within the cylinder wall, and / or the extension shapes of the piston inlet on the piston skirt and / or the piston outlet inlet on the piston skirt correspond to a segment of the piston's trajectory (especially being partially sinusoidal). If the piston inlet or outlet channel, or the inlet and / or outlet channels, extend along a certain segment of the sinusoidal trajectory (or the piston's trajectory), the control time of the working medium (i.e., the entry and exit times) can be extended, and, as needed, the control time can be achieved over a larger range of the piston's trajectory for the entry or exit of the working medium.

[0016] In order to directly convert the high pressure that the working medium usually has when it flows into the working chamber into a favorable impulse or force on the piston, the piston inlet channel can be set such that it extends into the working chamber in such a way that the working medium entering the piston from the inlet channel can apply fluid pressure to the piston in the direction of piston movement.

[0017] An advantageous embodiment of the piston machine according to the invention is proposed: the cylinder has two working chambers, wherein the piston is configured as a double-acting piston, and the two working chambers are arranged at opposite ends of the cylinder and separated from each other by the piston, wherein, in particular, the piston has an H-shaped configuration in the meridional section. The double-acting piston design allows for advantageous utilization of the expansion and / or compression processes within the piston, and also enables a particularly compact structure. Furthermore, the dual-working-chamber design further reduces the number of moving parts, and thus allows both working chambers to be handled by a single piston.

[0018] To achieve an advantageous seal between the working chambers, the two working chambers can be fluid-tightly separated by at least one piston ring disposed on the piston. Preferably, the piston ring has an anti-torsion structure, particularly an extension or hook embedded in the piston, which prevents the piston ring from twisting relative to the piston. By designing an anti-torsion structure for the piston ring, twisting relative to the piston can be advantageously prevented, thereby further improving the seal.

[0019] An alternative embodiment of the invention is proposed: the transmission mechanism has a forced guiding unit for forcibly guiding the piston, and a conversion unit for converting rotary stroke motion into rotary motion, wherein the forced guiding unit and the conversion unit are spatially separated within the piston mechanism, and in particular, the conversion unit and / or the forced guiding unit are configured to be fluid-tightly sealed relative to the working chamber and arranged separately from the working chamber. With this alternative embodiment, the piston assembly and the transmission mechanism (i.e., the forced guiding unit and the conversion unit) can be arranged separately from each other, thereby achieving a sealed separation from the working chamber. This allows for both lubricated (or unlubricated) design of the components and further reduces wear. Furthermore, the separate design of the forced guiding unit and the conversion unit forms two independent components, which can be specifically designed and lubricated according to the specific needs of each unit.

[0020] To advantageously convert rotary stroke motion into rotary motion, the conversion unit can be configured with a sliding element (particularly arranged at the end of the piston rod), which is constructed, in particular, as a cylindrical polygonal body (preferably a square or hexagonal prism). This sliding element is movable relative to a bearing bushing constructed in a shape-matched manner toward the piston axis, wherein the bearing bushing is rotatably supported relative to the piston housing, and through this bearing bushing, the rotary stroke motion converted into rotary motion can be output. By means of the advantageous design of the sliding element, it can move along the piston axis relative to the bearing bushing, but simultaneously the rotation of the piston can be transmitted through the sliding element to the bearing bushing, and then the bearing bushing transmits the pure rotary motion to other components (e.g., the transmission). For example, the sliding element can be constructed as a cylindrical polygonal body (such as a rod with a square or hexagonal cross-section), which can move along the piston cylinder axis within a shape-matched bearing bushing. Alternatively, other shaft-to-shaft or shaft-to-hub connection structures known in the prior art can be employed. These structures, for example, have a clearance fit or other fits or elements between the sliding element and the bearing bushing, allowing the sliding element to be guided to move relative to the bearing bushing along the cylinder axis or piston axis, while simultaneously driving the bearing bushing during rotational motion. For example, the bearing bushing can be supported within the housing by a rolling bearing or ball bearing to withstand axial forces, but simultaneously allowing the bearing bushing to withstand radial forces or achieve rotational motion. The sliding element and bearing bushing can also optionally be constructed as linear bearings known in the prior art.

[0021] Another advantageous embodiment of the piston machine is proposed: the conversion unit has a torque spherical bushing for acquiring or delivering torque, which allows the rotary stroke motion introduced into the piston (especially the piston rod) to be converted into rotary motion on the conversion unit, or the rotary motion to be converted into rotary stroke motion on the piston on the transmission mechanism.

[0022] Another advantageous embodiment of the piston machine is proposed: the forced guiding unit has multiple ball grooves and multiple ball sockets, wherein the ball sockets are arranged opposite to the ball grooves. The ball grooves are designed according to the piston's rotational stroke, particularly in a sinusoidal or quasi-sinusoidal curve shape. Balls or other rolling elements are arranged within the ball sockets, which move along the raceways of the ball grooves during the piston's rotational stroke and guide the piston during this stroke. Thus, by constructing the ball grooves, for example, within the housing of the cylinder or piston machine, the forced movement trajectory of the piston can be easily preset by the sinusoidal orientation of the ball grooves on the housing. As an alternative to the previously described variant, the piston machine may also have other curve guiding mechanisms known in the art, which guide the piston during its rotational stroke or are capable of guiding the piston's rotational stroke.

[0023] Advantageously, the transition between the piston and the transmission mechanism (especially the forced guide unit) can be configured as a universal joint, especially having at least three pins and multiple roller, ball, or needle roller bearings.

[0024] To achieve a particularly compact structure for the piston machine, the piston can be constructed as a hollow unit, with the forced guidance unit housed inside the piston. This advantageous implementation further reduces the moving mass of the piston, and the structural dimensions of the piston machine can be further reduced through the internal support or forced guidance of the piston.

[0025] Advantageously, the ball groove is arranged on the inner side of the piston, and the ball socket is arranged on the stator connected to the piston housing; or the ball socket is arranged on the inner side of the piston, and the ball groove is constructed on the stator.

[0026] Another advantageous embodiment of the piston machine is proposed: the transmission mechanism (especially the forced guiding unit) is constructed in the form of a sinusoidal disc transmission mechanism, wherein the transmission mechanism has a disc configured in a sinusoidal shape on its circumference, the disc being connected to the piston, wherein the disc is connected to a rolling element via a guiding element connected to the housing, wherein the rolling element is fitted onto the disc for guiding and supporting the disc. By means of the design of the sinusoidal disc transmission mechanism, the piston can be guided in a particularly advantageous manner, or the pressure applied to the piston by the working medium can be converted into an advantageous rotary stroke motion according to the invention.

[0027] An advantageous embodiment of a piston machine utilizing a sinusoidal disk drive mechanism is proposed: At least two guide elements are provided, each rotatably supported within a housing. Each guide element has two guide pins pointing towards the disk, on which rolling elements are rotatably supported. The guide pins and rolling elements are configured and spaced apart such that the rolling elements can conform to the opposite end faces of the disk, and the disk is guided and supported by the rolling motion of the rolling elements and the pivoting motion of the guide elements. A forced guiding unit has a ball joint arranged between the piston and the disk, wherein the disk is connected to the ball joint via spring washers in a torque-transmitting manner, allowing relative tilting or torsion of the disk through the elastic deformation of the spring washers. The guide elements and the sinusoidal disk form a so-called balance beam support structure, which enables disk rotation with minimal friction and prevents disk jamming or seizing through the pivoting or rotation of the guide elements.

[0028] To cool the piston or the various components of a piston engine, it is advantageous to arrange the piston with two piston rings spaced apart from each other, forming a cooling chamber between them. At least one cooling passage within the cylinder wall leads to this cooling chamber, into which a cooling medium can be introduced to cool the piston and / or cylinder. In this way, the cooling medium can be delivered through the gap between the two piston rings, thereby cooling the components within the working chamber region without concern about contact between the cooling medium and the working medium flowing within the working chamber.

[0029] Another aspect of the invention is to provide an advantageous internal combustion engine for generating work from a combustion fluid (as the working medium) mixed with an oxidant, and having a particularly advantageous design. This objective is achieved by the internal combustion engine according to the characterizing portion of claim 20. According to the invention, the internal combustion engine is constructed as a piston engine according to the invention, wherein the working fluid (especially by means of a spark plug) expands, the energy generated can be output through a transmission mechanism, and the combusted working medium can be discharged from the working chamber as exhaust gas through an exhaust passage.

[0030] Another aspect of the invention is to provide a compressor (especially a pump) for compressing a working medium, which possesses all the advantages of the piston compressor according to the invention. According to the invention, the compressor is configured as a piston compressor according to the invention, wherein the working medium is compressed within the working chamber and can be discharged from the piston compressor through a discharge passage as a compressed working medium or a working medium with an increased pressure level.

[0031] Another advantageous embodiment of the piston machine is proposed: it is constructed as a steam expander for generating mechanical work from a gaseous working medium. According to the invention, the steam expander is constructed as a piston machine according to the invention, or includes a piston machine according to the invention, wherein the working medium expands within the working chamber, thereby driving the piston and outputting mechanical work at the transmission mechanism. Attached Figure Description

[0032] The invention will now be illustrated illustratively with reference to the accompanying drawings, which show particularly advantageous but non-limiting embodiments, and the invention will be described by way of example with reference to the drawings: Figure 1 A first embodiment of the piston machine according to the present invention is shown in cross-sectional view. Figures 2 to 7 Various implementations of the sealing unit are shown. Figure 8 One embodiment of the piston ring is shown. Figure 10 and Figure 11 Shown in detail form according to Figure 1 According to one embodiment of the piston machine of the present invention, Figure 12 and Figure 13 A second embodiment of the piston machine according to the invention, with ball grooves, is shown. Figures 14 to 16 A third embodiment of the piston engine according to the present invention, which is an internal combustion engine, is shown. Figure 17 and Figure 18 A fourth embodiment of the piston machine according to the invention, having a transmission mechanism constructed within the piston, is shown. Figure 19 and Figure 20 The diagram shows various designs for the piston inlet and outlet passages of a steam expander, presented as an unfolded view of the cylinder wall and piston skirt. Figure 21 and Figure 22 This shows a view of the piston skirt and cylinder wall after they have been extended in one embodiment of the piston engine according to the present invention, which is an internal combustion engine. Detailed Implementation

[0033] Figure 1A first embodiment of a piston mechanism 10 according to the present invention is shown, which is used to obtain work from or output work to a gaseous or liquid working medium. The piston mechanism 10 includes a cylinder 1, within which a piston 2 is arranged. The cylinder 1 is closed at its end face by a cylinder head 12. The piston 2 is movable within the cylinder 1 along the cylinder axis and is rotatable about either the piston axis or the cylinder axis. Therefore, the piston 2 performs both rotational and stroke motion within the cylinder 1, or in other words, it can perform a so-called rotary stroke motion. When the piston 2 performs a stroke motion within the cylinder 1, the volume of the working medium flowing into the working chamber 3 increases or decreases with the movement of the piston 2. The piston mechanism 10 also has an inlet channel 4 through which the working medium enters the working chamber 3. For example, after the working medium expands or compresses, it can be discharged from the working chamber 3 through a discharge channel 5. Both the inlet channel 4 and the discharge channel 5 are arranged within the cylinder wall 11 of the cylinder 1 and open circumferentially to the working chamber 3. When piston 2 performs its rotary stroke, its piston skirt 21 periodically sweeps across inlet channel 4 and outlet channel 5 in sequence, allowing the working medium to enter the working chamber 3 through inlet channel 4, be expanded or compressed, and then be discharged from the working chamber 3 through outlet channel 5. During the operation of piston 2 or piston machine 10, inlet channel 4 and outlet channel 5 form a sealing structure, thereby achieving a dynamic seal between inlet channel 4 and outlet channel 5 and the working chamber 3 used for the working medium.

[0034] exist Figure 1 In the illustrated embodiment, the number of sealing units 6 in the piston mechanism 10 is the same as the number of inlet channels 4 and outlet channels 5. A preferred embodiment of the sealing unit 6 is as follows: Figure 2 and Figure 3 As shown. The sealing unit 6 has a sealing sleeve 63 ( Figure 2 and Figure 3The sealing sleeve 63 is pressed against the piston skirt 21 of the piston 2. The sealing unit 6 also has a spring 65, which is a compression spring and applies a force towards the piston 2 to the sealing sleeve 63 relative to the housing of the sealing unit 6. Therefore, the spring force 65 ensures that the sealing sleeve 63 always rests against the piston skirt 21 of the piston 2, forming a dynamic seal with the piston skirt. This dynamic seal between the sealing sleeve 63 and the piston skirt 21 prevents the working medium present in the inlet channel 4 from flowing into the working chamber 3 when the inlet to the working chamber 3 is not opened by the piston skirt 21. Similar to the inlet channel 4, a sealing sleeve 63 is also arranged in the sealing unit 6 within the outlet channel 5, and this sealing sleeve is also pressed against the piston skirt 21 of the piston 2 by the spring 65. If the outlet channel 4 is not opened by the piston skirt 21 or the edge of the piston end face 23, the sealing unit 6 or the sealing sleeve 63 prevents the working medium from flowing from the working chamber 3 into the outlet channel 5. Therefore, the sealing unit 6 or the sealing sleeve 63 of the sealing unit 6 in the discharge channel 5 can prevent the working medium from accidentally flowing into the discharge channel 5 from the working chamber 3.

[0035] The arrangement of the sealing unit 6 or the inlet channel 4 and the outlet channel 5 within the cylinder wall 11 of the cylinder 1 is matched with the rotational stroke of the piston 2. This arrangement ensures that when the piston 2 sweeps past or opens the outlet channel 5 or the inlet channel 4, the sealing unit 6 or the sealing sleeve 63 can always be in contact with the piston skirt 21 at at least two points, thereby avoiding tilting or jamming with the piston 2.

[0036] Figure 4 and Figure 5 An alternative embodiment of the sealing unit 6 is shown. The sealing unit utilizes the adjusting sleeve 66 to pass towards the piston 2. Figure 4 and Figure 5 The arrow shown is adjusted to preset the distance between the sealing sleeve 63 and the piston skirt 21 of the piston 2. Figure 4 and Figure 5 The sealing unit 6 also includes a spring 65, which in these embodiments prevents the sealing sleeve 63 from overextending into the working chamber 3. In this way, the gap between the piston skirt 21 and the sealing sleeve 63 can be advantageously adjusted, thereby forming, for example, a non-contact seal between the sealing unit 6 and the piston 2. For example, the sealing effect of the inlet channel 4 or outlet channel 5 relative to the working chamber 3 can be achieved by varying pressure conditions or configurations for gap sealing and the movement of the piston 2. During initial startup or maintenance, the sealing gap between the sealing sleeve 63 and the piston skirt 21 can be adjusted by adjusting the sleeve 66 and optimized to the minimum gap width.

[0037] Optionally, the surface of piston 2 and / or the end face of sealing sleeve 63 facing piston 2 may have a special surface structure that improves non-contact sealing. For example, the entire surface of piston skirt 21 may be provided with a rough, structured, honeycomb, scaly, or other surface structure that generates fluid-technical vortices. This surface structure, through the fluid-technical vortices generated by the flowing working medium, applies a resistance exceeding the simple throttling effect of the throttling gap between piston skirt 21 and sealing sleeve 63, thereby correspondingly reducing leakage flow.

[0038] Figure 6 and Figure 7 Other alternative embodiments of the sealing unit 6 are shown. The sealing unit 6 is connected to the working chamber 3 via a pressure transmission channel 62. Figure 6 The pressure in the working chamber 3 can be transmitted to the back of the sealing sleeve 63 through the pressure transmission channel, and affect the force of the sealing sleeve 63 pressing against the piston skirt 21 of the piston 2.

[0039] like Figure 7 As shown, for example, the back cavity of the sealing sleeve 63 can also be connected to the inlet channel 4 or the outlet channel 5 through the channel 62, thereby establishing a pressure difference in the back cavity based on the pressure difference between the working chamber 3 and the inlet channel 4 and the outlet channel 5, and using this pressure difference to press the sealing sleeve 63 toward the piston skirt 21.

[0040] like Figures 2 to 7 As shown, the sealing sleeve 63 or the sealing unit 6 may be spherical to match the radius of the piston skirt 21 or the piston 2, so that when viewed along the piston axis, the sealing sleeve 63 or the sealing unit 6 can always fully fit on the piston skirt 21 or the circumference of the piston 2.

[0041] like Figure 1 As shown, in a preferred embodiment of the piston machine 10, the piston 2 is constructed as a double-acting piston 2. Therefore, the piston machine 10 has two working chambers 3, which are respectively arranged at opposite ends of the cylinder 1. The two working chambers 3 are separated from each other by the piston 2, and the piston 2 performs strokes in opposite directions within the respective working chambers 3. That is, when the volume of one working chamber 3 is compressed or reduced, conversely, the volume of the second working chamber 3 increases or expands within it. Figures 1 to 17As shown, piston 2 preferably has an H-shape, that is, it is constructed as an H-shaped piston 2 in the meridional section, and has piston bottoms 26 that are offset rearward relative to the end face 23 of piston 2. Through the rearwardly offset piston bottoms 26, a cavity 27 is formed inside piston 2, which serves as an extension of working chamber 3 and is configured to open towards working chamber 3. For this purpose, piston 2 has a piston inlet channel 24, which forms a connection between piston skirt 21 and cavity 27 or piston bottom 26. Therefore, when the working medium flows to working chamber 3 through inlet channel 4, the working medium first flows into piston inlet channel 24, and then through piston inlet channel into cavity 27 or working chamber 3. Piston 2 also has a piston outlet channel 25, which connects working chamber 3 or cavity 27 to piston skirt 21. Therefore, when piston outlet channel 25 is aligned with outlet channel 5, the working medium flows from working chamber 3 or cavity 27 into outlet channel 5 through piston outlet channel 25, and then is discharged from working chamber 3 or cylinder 1. Cylinder 1 is closed at both end faces by cylinder head 12, and the cylinder head defines the working chamber 3 within cylinder 1 on the end sides. Optionally, as... Figures 1 to 18 As shown, the cylinder head 12 can be adapted to the end face shape of the piston 2, so that during the stroke, the working chamber 3 can be completely or almost completely filled by the piston 2, and the piston 2 is almost in contact with the cylinder head at the top dead center with a small gap from the cylinder head 12 at its end face 23.

[0042] like Figure 1 As shown, each working chamber 3 of the piston machine 10 has at least one inlet channel 4 and at least one outlet channel 5, and as preferably described above, at least one piston inlet channel 24 and at least one piston outlet channel 25. However, in alternative embodiments, the piston 2 or the piston machine 10 may also have multiple, especially two, inlet channels 4, outlet channels 5, piston inlet channels 24 and / or piston outlet channels 25.

[0043] In a preferred embodiment of the piston mechanism 10 according to the invention, the piston inlet channel 24 is configured in a curved shape or extends in a curved manner within the piston 2. The piston inlet channel 24 is guided or extended within the piston 2 such that the working medium flowing in through the inlet channel 24 can generate an impulse or force within the piston inlet channel 24, causing the piston 2 to move in the direction of the cylinder axis or applying a favorable impulse or force to the piston. Therefore, through the advantageous guidance of the piston inlet channel 24, the fluid pressure of the working medium can be used to apply a favorable impulse to the piston 2 in the direction of piston 2 movement.

[0044] like Figures 1 to 17As shown, the two working chambers 3 can be advantageously separated from each other by a plurality of piston rings 22 respectively arranged on the piston 2, or by a single piston ring 22, so that the pressure conditions in the two working chambers 3 do not affect each other, and the working chambers 3 are relatively sealed to each other with respect to the working medium by the piston rings 22. Figure 8 As shown, the piston ring 22 may advantageously have an anti-torsion structure, which in this embodiment is constructed as a hook 28. When the piston ring 22 is arranged on the piston 2, the hook 28 will engage with a groove on the piston 2 that is constructed to match its shape, thereby preventing the piston ring 22 from torturing relative to the piston during the rotational stroke of the piston 2.

[0045] In an embodiment of the piston machine 10 according to the present invention, the piston 2 is connected to the transmission mechanism 9, which on the one hand realizes forced guidance of the piston 2, and on the other hand converts the rotational stroke motion of the piston 2 into rotational motion.

[0046] According to Figure 1 In a first embodiment of the piston machine 10 shown, the transmission mechanism 9 has a forced guiding unit 7 for forcibly guiding the piston 2 or for guiding the piston 2 so that the piston performs or completes a predetermined rotary stroke motion. Furthermore, the transmission mechanism 9 or the piston machine 10 also has a conversion unit 8 for converting the rotary stroke motion into pure rotary motion. The conversion unit 8 has a sliding element 81, which has an elongated quadrangular prism shape or is configured as a so-called quadrangular prism (…). Figure 10 , Figure 11 The sliding element 81 or a quadrangular prism is connected to the piston 2 via the piston rod 29, allowing the sliding element 81 to complete the rotational stroke of the piston 2 along with the piston. A bearing bushing 82, configured to match the shape of the sliding element 81, is arranged within the conversion unit 8. This bearing bushing is rotatably supported within the cylinder housing by rolling bearings. When the piston 2 performs its rotational stroke, the sliding element 81 adjusts along with the piston 2 via the piston rod 29, extending further into or out of the bearing bushing 82 along the cylinder axis. Because the sliding element 81 is constructed as a quadrangular prism, it can drive the bearing bushing 82 in the rotational direction of the piston 2, thereby converting the rotational stroke of the piston 2 into the pure rotational motion of the bearing bushing 82. Therefore, the sliding element 81 can move relative to the bearing bushing 82 along the cylinder axis of the piston 2 or cylinder 1, but can drive the bearing bushing during rotational motion about the axis of the piston 2 or cylinder 1. Other components can be arranged on the bearing bushing 82, through which the rotational motion is derived and output to other components, such as a transmission. In an alternative embodiment, the sliding element 81 and the bearing bushing 82 may also be constructed as linear bearings known in the prior art.

[0047] As Figures 1 to 18In an alternative to the embodiment shown, which utilizes a conversion unit 8 with a sliding element 81 and a bearing bushing 82, the conversion unit 8 may also have a torque ball bushing or other components known in the prior art, which are connected to the piston rod 29 and can convert the rotary stroke motion into pure rotary motion as described above.

[0048] Figure 1 The first embodiment of the piston machine 10 shown also includes a forced guiding unit 7, which guides or forces the piston 2 to perform forced motion, i.e., rotary stroke motion. Figure 1 , Figure 10 , Figure 11 In the first embodiment shown, the forced guide unit 7 is constructed as a sinusoidal transmission mechanism. The forced guide unit 7 or transmission mechanism 9 has a disc 75 configured in a sinusoidal shape on its circumference, which is connected to the piston 2 via a guide rod 79. Viewed on its circumference, the disc 75 has a sinusoidal orientation and is connected to the piston 2 via a ball joint 100 (…). Figure 1 The disc 75 is connected to the guide rod 79. Therefore, the disc 75 can tilt or pivot slightly relative to the guide rod 79 via the ball joint 100. A spring washer 102 is arranged between the ball joint 100 and the disc 75. This spring washer 102 transmits the torque of the guide rod 79 to the disc 75 via the ball joint 100, while allowing the disc 75 to tilt or twist relative to the guide rod 79 through elastic deformation. The disc 75, together with the ball joint 100, the spring washer 102, and the guide rod 79, constitute a so-called balance beam support structure (Waagebalkenlagerung), which allows the disc to tilt relative to the guide rod while also transmitting the torque of the piston 2 or the guide rod 79 to the disc. Furthermore, this arrangement also achieves load balance.

[0049] Relative to the housing of cylinder 1, disc 75 is guided in its movement by two guide elements 76. Each guide element 76 has two guide pins 78, on which rolling elements 77 are arranged. Figure 1 In the illustrated embodiment, the rolling elements 77 are tapered rollers, each abutting one end face of the disc 75 and spaced apart from each other along the thickness of the disc 75. The disc 75 is guided by the rolling elements 77, wherein the guide element 76 is pivotable relative to the housing of the cylinder 1. Through the arrangement and sinusoidal design of the disc 75, combined with the ball joint 100, the guide element 76, and the rolling elements 77, the piston 2 can be guided by the guide rod 79 or forced to perform forced movement. Figure 1 In the embodiment shown, the piston 2 is forced to perform a sinusoidal rotary stroke.

[0050] Figure 12 and Figure 13A second embodiment of the piston mechanism 10 according to the present invention is shown. In this second embodiment, the transmission mechanism 9 has an alternative forced guide unit 7. The forced guide unit 7 has a ball groove 71 arranged inside the housing 1, and the housing is also constructed in a cylindrical shape in the area where the forced guide unit 7 is located. Corresponding to the ball groove 71, three ball sockets 72 are arranged on the guide rod 79, and balls 73 are tightly fixed in the ball sockets. The balls 73 are inserted from the ball sockets 72 into the ball grooves 71, and the piston 2 is forced to perform a forced movement according to the design of the ball grooves 71 by the guide rod 79. The ball grooves 71 have a sinusoidal curve shape, thus forcing the piston 2 to perform a sinusoidal rotary stroke movement along the raceway of the ball grooves 71.

[0051] As Figure 12 and Figure 13 In an alternative to the embodiment shown, the ball socket 72 or ball groove 71 together with the ball 73 can also be constructed in the form of a universal joint, for example, three balls 73 together forming a triangular joint structure.

[0052] As Figure 12 and Figure 13 In an alternative to the implementation described herein using ball bearings 73, other rolling elements may also be arranged on the guide rod 79, which may be supported in or move within a groove on the housing of the cylinder 1 that is shaped to match it.

[0053] Figures 14 to 16 A third embodiment of the piston machine 10 according to the present invention is shown. In this third embodiment, the forced guide unit 7 is arranged inside the piston 2. The piston 2 is constructed as a hollow cylinder with ball sockets 72 on its inner wall, in which balls 73 are arranged. A stator 74 is also arranged inside the piston 2, which is connected to the housing of the cylinder 1 via a connecting rod. The stator 74 is arranged torsionally inside the piston 2 and has two ball grooves 71 offset from each other by 90°. The movement of the piston 2 is forcibly applied to the piston via the balls 73 or the ball grooves 71, and the piston 2 can perform a sinusoidal rotary stroke motion according to the design of the ball grooves 71, for example. Therefore, the piston 2 is forcibly supported inside by the forced guide unit 7 and performs a rotary stroke motion when the working medium flows in through the inlet channel 4 and the piston inlet channel 24.

[0054] Figure 17 and Figure 18 A fourth embodiment of the piston mechanism 10 according to the present invention is shown. The piston mechanism 10 has a forced guiding unit 7 disposed inside the piston 2. The piston 2 has three ball sockets 72, each containing three balls 73. Figure 18An intermediate bushing 87 is arranged between the stator 74 and the piston 2, and the intermediate bushing has a ball groove 71. The intermediate bushing 87 is fixedly connected to the stator 74, so that the piston 2 can perform a rotary stroke. Figure 17 and Figure 18 The embodiment shown has only one ball groove 71.

[0055] like Figures 14 to 18 As shown, the third and fourth embodiments have multiple circulation channels 103, which allow the air present in the piston 2 to circulate during the stroke, preventing the air from being compressed and hindering the movement of the piston 2.

[0056] pass Figures 14 to 18 The preferred embodiment shown enables a particularly compact structure for the piston machine 10, with only a small number of moving parts, which reduces the failure rate and the mass of the moving parts.

[0057] like Figures 1 to 18 As shown, the transmission mechanism 9 or conversion unit 8 and the forced guide unit 7 can be arranged separately from the working chamber 3 and designed as individually sealed. For example, this allows for optional lubrication of the transmission mechanism 9 or conversion unit 8 and forced guide unit 7 and seals them off from the working chamber, thereby extending the service life of these components and effectively preventing them from mixing or coming into contact with the working medium.

[0058] like Figures 14 to 17 As shown in the preferred embodiment, the piston machine 10 may optionally have two piston rings 22, which are spaced apart on the circumference of the piston 2 relative to the cylinder axis or the piston 2 axis, respectively. In this case, the gap between the piston rings 22 can be configured as a cooling chamber 14 within the piston 2 or cylinder 1, through which coolant can enter and be delivered to the piston 2 via a cooling channel 15. For example, the coolant introduced through the cooling channel 15 can circulate within the cooling chamber 14 and be discharged again from the cooling chamber 14 via another cooling channel 15. In this way, the piston 2 or cylinder 1 can be targeted for cooling in the area of ​​the cooling chamber 14 by the coolant or cooling medium, thereby avoiding unwanted temperature increases.

[0059] In a preferred embodiment, the cylinder 1, piston 2, and other components or parts thereof of the piston mechanism 10 are made of ceramic materials, carbon-graphite composite materials, or high-tech plastics and high-tech composite materials.

[0060] Figures 1 to 21The piston machine 10 shown can be configured as an expander in which the compressed working gas expands in the working chamber 3 and thereby outputs work to the piston 2, or it can be configured in the opposite form, that is, by applying mechanical work to the piston 2, the piston 2 transmits work to the working medium in the form of compression work.

[0061] In an alternative embodiment shown, the piston machine 10 according to the present invention may also have a plurality of cylinders 1, each of which has a piston 2 arranged in the cylinder.

[0062] In one advantageous application of the piston engine 10 according to the invention, the piston engine 10 is configured as an internal combustion engine, or an internal combustion engine incorporates the piston engine 10 according to the invention. In the piston engine 10, for example, a combustion fluid can be introduced as a working medium through an inlet channel 4 into the working chamber 3 and combust with an oxidant. During combustion, the working medium expands and pushes the piston 2 in a rotary stroke motion, thereby transferring work to the piston 2 and outputting it to the conversion unit 8. Subsequently, the work can be output to the wheels or transmission of a vehicle, for example, through the conversion unit 8. For this purpose, it can be done as follows: Figure 14 The spark plug 101 is shown, extending into the working chamber 3. This internal combustion engine can operate, for example, based on the Otto cycle, or can be used as a diesel or gas engine without significant modifications.

[0063] In another application of the piston mechanism 10 according to the invention, it is configured as a compressor or pump, or a compressor having the piston mechanism 10. In this case, the working medium enters the piston mechanism 10 according to the invention, is compressed in the working chamber 3, and is then discharged through the discharge passage 5 in the form of compressed working medium or working medium with an increased pressure level. In the case of a compressor, work is transmitted to the piston 2 via the conversion unit 8, and the piston 2 then outputs work to the working medium through a rotary stroke motion.

[0064] Another advantageous application of the piston mechanism 10 according to the invention is to construct it as a steam expander for RC or ORC cycles, or to incorporate the piston mechanism 10 according to the invention into a steam expander. In this case, the working medium (e.g., steam or ORC fluid) expands within the working chamber 3 and outputs work through the piston 2 and the transmission mechanism 9 or the conversion unit 8.

[0065] In a preferred embodiment of the piston machine 10 according to the invention, the piston inlet passage 24 or piston outlet passage 25 may be extended elongatedly with its inlet leading to the piston skirt 21 according to the rotational stroke of the piston 2.

[0066] Figure 19 One embodiment of the piston 2 is shown in unfolded form. The piston inlet channel 24 and piston outlet channel 25 extend along the piston skirt 21 along a segment of the rotational stroke of the piston 2, and are partially sinusoidal in shape. Figure 20 In the cylinder wall 11, the discharge passage 5 or the inlet passage 4 is also shown in an expanded form. During one segment of the piston 2's rotary stroke, the piston inlet passage 24 corresponds to the inlet passage 4, through which the working medium flows into the working chamber 3. For example, after the working medium (e.g., in a compressor) has completed its expansion, the piston discharge passage 25 aligns with the discharge passage 5, through which the working medium is discharged from the cylinder. Figure 19 As shown, for example, in the case where the piston mechanism is a steam expander, the extension length of the piston discharge passage 25 on the circumference of the piston skirt 21 is greater than that of the piston inlet passage 24.

[0067] Figure 21 and Figure 22 correspond Figure 19 and Figure 20 This illustrates a design for a piston inlet passage 24 and a piston outlet passage 25 for a four-stroke internal combustion engine. Depending on the design of the piston inlet passage 24 or the piston outlet passage 25, the asymmetric control time of the piston 2 or the process within the working chamber 3 can be controlled, and the piston 2 can be forced to execute a favorable motion pattern.

Claims

1. A piston machine (10) for obtaining or outputting work from or to a gaseous or liquid working medium, the piston machine comprising at least one cylinder (1), the cylinder being closed at its end face, in particular by a cylinder head, and a piston (2) arranged in the cylinder (1), wherein, The piston (2) is guided in the working chamber (3) of the cylinder (1) in such a way that it can perform both reciprocating motion along the cylinder axis and rotational motion about the cylinder axis, especially sinusoidal rotary stroke motion. The piston (2) is connected to the transmission mechanism (9) via a piston rod (29) for forced guidance of the piston (2) and for converting the rotary stroke motion into rotational motion. The piston machine (10) has at least one inlet channel (4) for allowing the working medium to enter the working chamber (3), and at least one outlet channel (5) for allowing the working medium to exit the working chamber (3). The feature is that the inlet channel (4) and the outlet channel (5) are arranged in the cylinder wall (11) such that the piston (2) can sweep across the inlet channel (4) and the outlet channel (5) with its piston skirt (21) during its rotational stroke, and can periodically, especially completely cover and reopen these channels, and wherein the inlet channel (4) and the outlet channel (5) are arranged and constructed with the piston (2) such that the inlet channel (4) and the outlet channel (5) are dynamically sealed independently of each other with respect to the working chamber (3) for the working medium, wherein the effective sealing surfaces between the piston skirt (21) and the inlet channel (4) and / or the outlet channel (5) are arranged around the inlet channel (4) and / or the outlet channel (5).

2. The piston machine (10) according to claim 1, characterized in that, The piston mechanism (10) has multiple sealing units (6), each of which has a sealing sleeve (63) that can press against the piston skirt (21) of the piston (2). The sealing units (6), particularly the sealing sleeves (63), are arranged around the inlet channel (4) and also around the outlet channel (5). The sealing units (6) can seal the inlet channel (4) and the outlet channel (5) relative to the working chamber (3), respectively. The sealing units (6), particularly the sealing sleeves (63), are constructed such that when the piston (2) sweeps across the inlet channel (4) and / or the outlet channel (5), the sealing units are always in contact with the piston skirt (21) at at least two points. In particular, the sealing unit (6), preferably the sealing sleeve (63), is shaped into a spherical shape to match the radius of the piston skirt (21).

3. The piston machine (10) according to claim 2, characterized in that, The sealing unit (6) has a spring (65), which, by means of the spring (65), can press the sealing unit (6), especially the sealing sleeve (63), against the piston skirt (21) of the piston (2).

4. The piston machine (10) according to claim 2 or 3, characterized in that, The sealing unit (6) is connected to the working chamber (3) or the inlet channel (4) and / or the outlet channel (5) through a pressure transmission channel (62), wherein the dominant pressure difference between the inlet channel (4) or the outlet channel (5) and the working chamber (2) can be transmitted to the sealing unit (6), especially the sealing sleeve (63), through the channel (62), and can press the sealing unit (6), especially the sealing sleeve (63), against the piston skirt (21).

5. The piston machine (10) according to any one of the preceding claims, characterized in that, The piston (2) has a piston bottom (26) which is offset rearward relative to the end face (23) of the piston (2), so that the piston (2) forms a cavity (27) open toward the working chamber (3). -in, The piston (2) has at least one piston inlet channel (24) constructed within the piston (2), the piston inlet channel forming a connection from the piston skirt (21) to the cavity (27) and / or the piston bottom (26), and allowing the working medium to enter the working chamber (3) as the piston (2) sweeps through the inlet channel (4), and -The piston (2) has at least one piston discharge passage (25) constructed within the piston (2), the piston discharge passage being able to form a connection from the cavity (27) and / or from the piston bottom (26) to the piston skirt (21), and being able to discharge the working medium from the working chamber (2) when the piston (2) sweeps through the discharge passage (5).

6. The piston machine (10) according to any one of the preceding claims, characterized in that, The inlet channel (4) and / or the outlet channel (5) can extend along a segment of the movement trajectory, especially a sinusoidal trajectory, of the piston skirt (21), preferably the piston inlet channel (24) and / or the piston outlet channel (25). In particular, the inlets of the inlet channel (4) and / or the outlet channel (5) leading to the cylinder (1) have a sinusoidal extension shape within the cylinder wall (11), and / or the extension shape of the opening of the piston inlet channel (24) and / or the opening of the piston outlet channel (25) at the piston skirt (21) corresponds to a segment of the piston's movement trajectory, especially being partially sinusoidal.

7. The piston machine (10) according to any one of the preceding claims, characterized in that, The piston inlet channel (24) extends into the working chamber (3) in such a way that the working medium entering the piston (2) from the inlet channel (5) can apply fluid pressure to the piston (2) in the direction of movement of the piston (2).

8. The piston machine (10) according to any one of the preceding claims, characterized in that, The cylinder (1) has two working chambers (3), wherein the piston (2) is constructed as a double-acting piston (2), and the two working chambers (3) are arranged at opposite ends of the cylinder (1) and separated from each other by the piston (2). In particular, the piston (2) is constructed in an H-shape in the meridional section.

9. The piston machine (10) according to claim 8, characterized in that, The two working chambers (3) are separated from each other in a fluid-tight manner by at least one piston ring (22) arranged on the piston (2). Preferably, the piston ring (22) has an anti-torsion structure, especially an extension or hook (28) embedded in the piston (2), which prevents the piston ring (22) from torturing relative to the piston (2).

10. The piston machine (10) according to any one of the preceding claims, characterized in that, The transmission mechanism (9) has a forced guiding unit (7) for forcibly guiding the piston (2) and a conversion unit (8) for converting the rotary stroke motion into rotary motion. -The forced guiding unit (7) and the conversion unit (8) are spatially separated within the piston machine (10), and -In particular, the conversion unit (8) and / or the forced guiding unit (7) are configured to be fluid-tightly sealed relative to the working chamber (3) and arranged separately from the working chamber.

11. The piston machine (10) according to claim 10, characterized in that, The conversion unit (8) has a sliding element (81), which is arranged in particular at the end of the piston rod (29). The sliding element is constructed in particular as a columnar polygonal body, preferably a quadrangular prism or a hexagonal prism. The sliding element is movable relative to the bearing bush (82) constructed in a shape matching the piston axis of the piston (2). The bearing bush (82) is rotatably supported relative to the housing of the piston machine (10) and can output a rotary stroke motion converted into rotary motion through the bearing bush.

12. The piston machine (10) according to any one of claims 10 or 11, characterized in that, The conversion unit (8) has a torque ball bushing for acquiring or transmitting torque. The torque ball bushing can convert the rotary stroke motion of the piston (2), especially the piston rod (29), into rotary motion on the conversion unit (8), or can convert the rotary motion into rotary stroke motion on the piston (2) on the conversion unit (8).

13. The piston machine (10) according to any one of claims 10 to 12, characterized in that, The forced guiding unit (7) has a plurality of ball grooves (71) and a plurality of ball sockets (72), wherein the ball sockets (72) are arranged relative to the ball grooves (71), wherein the ball grooves (71) are constructed according to the rotational stroke of the piston (2), in particular having a sinusoidal or quasi-sinusoidal curved shape, wherein balls (73) or other rolling elements are arranged in the ball sockets (72), which can move in the ball sockets (72) following the raceways of the ball grooves (71) when the piston (2) performs the rotational stroke, and can guide the piston during the rotational stroke of the piston (2).

14. The piston machine (10) according to any one of the preceding claims, characterized in that, The transition between the piston (2) and the transmission mechanism (9), especially the forced guide unit (7), is constructed in the form of a universal joint, and in particular has at least three pins and multiple roller or ball or needle roller bearings.

15. The piston machine (10) according to any one of the preceding claims, characterized in that, The piston (2) is hollow, wherein the forced guiding unit (7) is constructed inside the piston (2).

16. The piston machine (10) according to claim 15, characterized in that, The ball groove (71) is arranged on the inner side of the piston (2), and the ball socket (72) is arranged on the stator (74) connected to the housing of the piston mechanism (10); or - The ball socket (72) is arranged on the inner side of the piston (2), and the ball groove (71) is constructed on the stator (74).

17. The piston machine (10) according to any one of the preceding claims, characterized in that, The transmission mechanism (9), especially the forced guiding unit (7), is constructed in the form of a sinusoidal disk transmission mechanism, wherein the transmission mechanism (9) has a disk (75) which is sinusoidally shaped on its circumference and is connected to the piston (2). -The disc (75) is connected to the rolling element (77) via a guide element (76) connected to the housing. -The rolling element (77) rests against the disc (75) for guiding and supporting.

18. The piston machine (10) according to claim 17, characterized in that, At least two guide elements (76) are provided, each rotatably supported within the housing. Each guide element (76) has two guide pins (78) pointing toward the disk (75), on which a rolling element (77) is rotatably supported. The guide pins (78) and the rolling elements (77) are configured and spaced apart from each other such that the rolling elements (77) can fit against the opposite end faces of the disk (75), and the disk is guided and supported by the rolling motion of the rolling elements (77) and the pivoting motion of the guide elements (76). -The forced guiding unit (7) has a ball joint (100) arranged between the piston (2) and the disk (75). The disk (75) is connected to the ball joint (100) via a spring washer (102) in a torque transmission manner such that the relative tilting or twisting of the disk (75) can be achieved through the elastic deformation of the spring washer (102).

19. The piston machine (10) according to any one of the preceding claims, characterized in that, The piston (2) has two piston rings (22) arranged at intervals on the piston (2) and forming a cooling chamber (14) between the piston rings. At least one cooling channel (15) is provided in the cylinder wall (11) leading to the cooling chamber (14) and a cooling medium can be introduced into the cooling chamber to cool the piston (2) and / or the cylinder (1).

20. An internal combustion engine for generating work from a combustion fluid mixed with an oxidant as a working medium, said internal combustion engine comprising a plurality of cylinders, characterized in that, The internal combustion mechanism is a piston engine (10) according to any one of claims 1 to 19, wherein the working fluid, especially by means of a spark plug, expands and the energy generated can be output through the transmission mechanism (9), and the working medium after combustion can be discharged from the working chamber (3) as exhaust gas through the discharge channel (5).

21. A compressor, especially a pump, for compressing a working medium, characterized in that, The compressor is configured as a piston machine (10) according to any one of claims 1 to 19, wherein the working medium is compressed in the working chamber (3) and can be discharged from the piston machine (10) through the discharge passage (4) as a compressed working medium or a working medium with an increased pressure level.

22. A steam expander for generating mechanical work from a gaseous working medium, particularly steam or an ORC fluid, characterized in that, The steam expansion mechanism is constructed as a piston machine (10) according to any one of claims 1 to 19, wherein the working medium expands in the working chamber (3) to drive the piston (2) and output mechanical work at the transmission mechanism (9).

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