Reciprocating-piston machine device and reciprocating-piston machine

Abstract

The invention relates to a reciprocating-piston machine device (12a-b) comprising: a gas-tight pressure housing (14a); at least one rotor (16a-b) which is mounted so as to be translationally movable along a movement axis (18a-b) within the pressure housing (14a); and at least one piston (20a-b) which is arranged within the pressure housing (14a) and which is operatively connected to the rotor (16a-b). According to the invention, in order to provide a device of the type in question with improved properties in terms of efficiency, the piston (20a-b) has a polygonal cross-section.

Description

[0001] Reciprocating piston machine device and reciprocating piston machine

[0002] State of the art

[0003] The invention relates to a reciprocating piston engine device according to the preamble of claim 1 and a reciprocating piston engine according to claim 15.

[0004] Reciprocating piston engine devices with a pressure housing and at least one piston, which are designed to convey and / or compress fluids, are already known from the prior art. Conventional reciprocating piston engine devices have a crank mechanism to convert the rotary movement of a drive motor into a linear piston movement. The often round piston is moved linearly within the pressure housing to suck in fluids via an inlet valve of the reciprocating piston engine devices and expel them again via an outlet valve of the reciprocating piston engine devices. The piston typically has a round cross-section and is movably mounted within a pressure housing designed as a cylinder. The crank mechanism requires a lot of installation space. With cylindrical cross-sections, the forces increase proportionally to the square of the diameter, which is why multiple pistons are required to achieve higher delivery rates.In addition, an increase in stroke in crank drives leads to larger installation volumes and increased starting currents. Sealing materials with good sliding properties, such as PTFE (polytetrafluoroethylene), are standardly used to seal the gap between the round piston and the pressure housing. The reciprocating piston engine device thus features a plain bearing for sealing and supporting at least the piston within the pressure housing. Crank drives combined with prior art plain bearings have the disadvantage that long, continuous operation is not possible due to heat buildup in the pressure housing caused by strong friction between the piston, particularly the seal, and the inside of the pressure housing. Due to increased seal wear, the sealing properties are reduced, and the service life of the reciprocating piston engine device is significantly shortened.To solve such problems, lubricants are used that improve the tribological properties of the piston and pressure housing. This can reduce leakage. However, the disadvantage is that the lubricants contaminate the fluid, which requires considerable effort to clean the fluid of lubricant when generating compressed air or in refrigeration compressors. The present invention thus addresses the problems of piston and pressure housing design, as well as the bearing of the piston within the pressure housing, in conjunction with the prevailing sealing problems.

[0005] The object of the invention is, in particular, to provide a generic device with improved properties in terms of efficiency. This object is achieved according to the invention by the features of claims 1 and 15, while advantageous embodiments and further developments of the invention can be found in the subclaims.

[0006] Advantages of the invention

[0007] The invention is based on a reciprocating piston engine device with a gas-tight pressure housing, with at least one rotor which is mounted within the pressure housing so as to be translationally movable along a movement axis, and with at least one piston arranged within the pressure housing which is in operative connection with the rotor.

[0008] It is proposed that the piston has a polygonal cross-section.

[0009] Such a design can provide a reciprocating piston engine device with improved efficiency properties and increase at least one performance, work, design, product, and / or operating efficiency. A piston with a polygonal cross-section can provide a larger surface-to-volume ratio and increase delivery and / or compression performance. Furthermore, the larger piston surface offers the possibility of arranging larger valve openings, which in turn allows a higher fluid flow rate to be achieved with fewer pressure losses. Furthermore, in combination with the use of the seal according to the invention, in particular a non-contact seal, contamination of the fluid can be prevented, wear on the seal and piston can be reduced, and the service life of the reciprocating piston engine device can be increased.Furthermore, it can provide a more efficient design of the reciprocating piston machine device.

[0010] A "reciprocating piston machine device" should advantageously be understood to mean at least one part, in particular a subassembly, of a reciprocating piston machine. However, it would also be conceivable for the reciprocating piston machine device to form the entire reciprocating piston machine. The reciprocating piston machine, which can also be referred to as a piston engine, can be designed as a working machine, for example as a pump. A reciprocating piston machine designed as a working machine can be provided to convert electrical energy into mechanical energy, in particular into kinetic energy, for example in order to convey and / or compress fluids. Alternatively, the reciprocating piston machine can be designed as a prime mover, in particular a heat engine. A reciprocating piston machine designed as a prime mover can be provided to convert kinetic energy into electrical energy.The reciprocating piston engine could, without being limited thereto, be designed as a Stirling engine. Preferably, the reciprocating piston engine is designed as a reciprocating piston compressor, in particular a reciprocating piston compressor, for example for refrigeration appliances. In particular, the reciprocating piston engine device is intended to compress and / or convey fluids, preferably gases or liquids, such as refrigerants or other incompressible fluids, with the aid of at least the piston. Preferably, the reciprocating piston engine device is intended to convey incompressible fluids and / or to compress and convey compressible fluids. Particularly preferably, the reciprocating piston engine device is a subassembly of a refrigeration appliance, in particular a household refrigeration appliance, which can be designed, for example, as a freezer, a refrigerator and / or freezer cabinet, and / or as a beverage cooler.

[0011] The reciprocating piston machine device preferably has a drive unit. The drive unit can be designed to convert electrical energy into mechanical energy, which acts on at least the rotor to convey and / or compress fluids. The reciprocating piston machine device preferably has a linear drive. In particular, the drive unit is designed as a linear drive. The reciprocating piston machine device can have a stator unit for transmitting drive forces to the rotor. The stator unit can be part of the drive unit.

[0012] Alternatively or in addition to a drive unit, the reciprocating piston engine device can comprise a generator unit. Preferably, the reciprocating piston engine device of a reciprocating piston engine configured as a prime mover comprises a linear generator. In particular, the generator unit is configured as a linear generator. Preferably, at least the stator unit is then part of the generator unit. It is further conceivable for the reciprocating piston engine device to comprise a combination unit configured for alternating operation, either as a drive unit or as a generator unit.

[0013] The reciprocating piston engine device can have a housing unit, in particular an outer housing unit. The pressure housing, the rotor, and at least the piston are preferably arranged within the housing unit. The housing unit can at least partially protect the piston, the rotor, and / or the pressure housing from external influences and effects. Furthermore, the housing unit can at least partially, preferably completely, accommodate the drive unit and / or the generator unit of the reciprocating piston engine device. It would be conceivable for the stator unit to be arranged at least partially or completely within the gas-tight pressure housing. In order to further increase efficiency, in particular cost efficiency, it is proposed that the stator unit be arranged outside the pressure housing.Furthermore, the stator unit outside the pressure housing can be protected from exposure to the fluid to be pumped and / or compressed, thus advantageously reducing wear and increasing longevity.

[0014] In particular, the stator unit is provided for transmitting drive forces to the rotor. The stator unit can provide at least one electromagnetic field, in particular an alternating electromagnetic field, for transmitting drive forces to the rotor. For this purpose, the stator unit can have at least one coil. Preferably, the stator unit has a plurality of coils, each of which is provided for providing electromagnetic fields. In addition to transmitting drive forces to the rotor, the stator unit can also be provided for converting the rotor's kinetic energy into electrical energy.

[0015] The rotor is designed to at least partially absorb drive forces provided by the stator unit in an operating state of the reciprocating piston engine device and to convert them into kinetic energy in the form of, in particular, oscillating, translational movements along the movement axis. Preferably, the rotor is designed to at least partially transfer the kinetic energy in the operating state to the at least one piston in order to drive it to perform, in particular, oscillating, translational movements. Preferably, the rotor is designed to drive the at least one piston to perform, in particular, oscillating, translational movements along the movement axis in the operating state.However, it would also be conceivable for the piston and the rotor to be connected to one another via a movable connecting element, for example, via a joint, and for the rotor to be designed to drive the at least one piston in the operating state to perform, in particular, oscillating, translational movements along a further movement axis that runs parallel or at an angle to the movement axis. Preferably, the rotor and the at least one piston are designed to execute translational movements synchronous to one another in the operating state.

[0016] In the present case, the piston has a polygonal cross-section, in particular a non-circular or oval cross-section. The polygonal cross-section of the piston running perpendicular to the axis of movement can have any integer number of corners greater than or equal to three. Advantageously, the polygonal cross-section of the piston running perpendicular to the axis of movement has equiangular interior angles. Furthermore, the polygonal cross-section of the piston running perpendicular to the axis of movement can form a regular polygon. Particularly advantageously, the polygonal cross-section of the piston running perpendicular to the axis of movement has any even integer number of corners greater than or equal to four. Preferably, the piston has a quadrangular cross-section running perpendicular to the axis of movement.Particularly preferably, the piston has a rectangular cross-section running perpendicular to the movement axis, wherein mutually perpendicular sides of the cross-section have an aspect ratio other than one. Preferably, the polygonal cross-section running perpendicular to the movement axis has an area that is at least substantially constant along a main extension of the piston running parallel to the movement axis, in particular regardless of manufacturing tolerances. However, it would also be conceivable for the piston to have a cross-sectional area running perpendicular to the movement axis, which varies at least in sections along its main extension running parallel to the movement axis.

[0017] The piston could be operatively connected to the rotor indirectly, for example via at least one connecting element. Preferably, the piston is operatively connected directly to the rotor. The piston could be connected to the rotor in a form-fitting and / or force-fitting manner, for example with at least one snap-in connection, plug-in connection, rotary connection, screw connection and / or clamp connection. It is proposed that the piston be formed integrally with the rotor. The piston and the rotor could be connected to one another in a material-fitting manner, for example with an adhesive connection and / or welded connection and / or by an injection-molding process. The piston and rotor are particularly preferably formed in one piece. “One-piece” should be understood to mean formed in one piece.Preferably, this single piece is manufactured from a single blank, a mass, and / or a cast, for example, by a casting process, a stamping process, and / or a printing process, such as a 3D printing process, or another process deemed appropriate by a person skilled in the art. This advantageously allows for particularly high precision to be achieved by eliminating the need for connecting means between the piston and the rotor. Furthermore, efficiency in terms of manufacturing, product, and / or cost effectiveness can be increased by simplifying a manufacturing process, reducing costs, and providing a more compact design.A multi-part design of piston and rotor, on the other hand, allows for more flexible adaptation to certain influencing factors in the operation of the reciprocating piston machine device, for example thermal expansion of the piston and / or the pressure housing, and can therefore be preferred for certain applications of the reciprocating piston machine device.

[0018] Furthermore, the rotor could have an oval or round cross-section running perpendicular to its axis of movement. Preferably, the rotor has a polygonal cross-section running perpendicular to its axis of movement, which can be designed analogously to the polygonal cross-section of the piston.

[0019] In particular, in this context, the statements regarding the polygonal cross-section of the piston should also apply to the polygonal cross-section of the rotor.

[0020] The pressure housing and the piston can each define a working chamber, at least in sections. Within the pressure housing, the piston is mounted for translational movement along its axis of motion. By moving the piston along the axis of motion, the working chamber can expand or contract along the axis of motion.

[0021] The reciprocating piston machine device can have at least one valve unit for supplying and / or discharging a fluid into and / or out of the working chamber. In particular, the valve unit is provided to regulate the supply and / or discharge of the fluid into and / or out of the working chamber. The fluid can enter and / or exit the working chamber through the valve opening. In at least one operating state, in particular an intake operating state, of the reciprocating piston machine device, the fluid can enter the working chamber through at least one valve opening of the valve unit. In the intake operating state, the piston can move along the movement axis away from at least the valve opening and thus generate a negative pressure which sucks in the fluid and draws it through the valve opening into the working chamber. In particular, in the intake operating state, the piston moves away from the valve opening.The intake operating state preferably lasts until the piston reaches a turning point and changes its direction of movement along the movement axis. Preferably, the piston is located at the turning point at a point furthest away from at least the valve opening. In at least one compression operating state of the reciprocating piston machine device, a force can be exerted on the fluid in the working chamber by an opposite movement of the piston along the movement axis, preferably towards at least the valve opening. In particular, the piston compresses the fluid within the working chamber by moving along the movement axis towards at least the valve opening. Once a desired pressure has been reached in the working chamber, the fluid can escape from the working chamber again via the valve opening and / or at least one other valve opening.By moving along the axis of movement, preferably towards at least the valve opening, the piston can at least partially and preferably at least substantially completely force the fluid out of the working chamber through the valve opening and / or at least one other valve opening of the valve unit. The valve opening can have a flow direction running perpendicular to an end face of the piston. Preferably, the valve unit has at least one further valve opening. The further valve opening can be arranged opposite the valve opening and perpendicular to the axis of movement, in particular the end face of the piston. Preferably, the valve opening forms an outlet valve opening and the further valve opening forms an inlet valve opening. In particular, the further valve opening can have a further flow direction running perpendicular to the end face of the piston.

[0022] "Intended" here and below means specifically programmed, configured, designed, and / or equipped. The term "intended" for an object for a specific function means that the object fulfills and / or performs this specific function in at least one application and / or operating state.

[0023] It might be conceivable for the reciprocating piston machine device to have at least one plain bearing that movably supports the piston and / or the rotor within the pressure housing. In order to provide a particularly efficient reciprocating piston machine device with which sliding friction and frictional heat within a pressure housing can be avoided and wear, in particular of seals, can be reduced, it is proposed that the reciprocating piston machine device comprise a bearing unit with at least one rotation element for the linearly movable support of the rotor relative to a pressure housing wall of the pressure housing, wherein the rotation element has an axis of rotation perpendicular to the axis of movement of the rotor. This makes it possible to provide a particularly efficient support for the rotor and in particular the piston. Furthermore, plain bearings can be dispensed with and other forms of seals, such as non-contact seals, can be used.In addition, lubricants can be eliminated, thus providing a particularly clean and operationally and performance-efficient reciprocating piston engine. Furthermore, the design can be simplified and made more cost-effective.

[0024] The bearing unit is preferably a rolling bearing unit. The rotating element could, for example, be designed as a spherical element, in particular a ball, or as a needle. The bearing unit could be a ball-bearing unit and, in particular, with a plurality of rotating elements designed as balls. The rotating element could also be referred to as a rolling element. The rotating element is preferably designed as a roller. In particular, the rotation axis of the rotating element, in particular of the roller, runs in the vertical direction, preferably in the vertical direction, especially when the movement axis is aligned horizontally. The bearing unit could also have additional rotating elements, for example at least two, four, or eight rotating elements. In order to provide particularly uniform and secure mounting, the bearing unit preferably always has an even number of rotating elements.In this document, "perpendicular" shall be understood to mean an angle between 85° and 95°, preferably between 88° and 92° and particularly advantageously 90°, regardless of manufacturing tolerances.

[0025] It is also proposed that the pressure housing have at least one guide element for guiding at least the rotating element. This ensures particularly uniform and reliable guidance of at least the rotating element, preferably the piston and / or the rotor, and thereby further improves the bearing support of at least the piston. In particular, this can increase the design efficiency and the operating and performance efficiency of the reciprocating piston engine device.

[0026] The guide element can be a component of the pressure housing that is formed separately from the pressure housing wall, which component is arranged on the pressure housing wall and connected to the pressure housing wall. The guide element could be connected to the pressure housing wall in a form-fitting and / or force-fitting manner, for example with at least one snap-in connection, plug-in connection, rotary connection, screw connection and / or clamp connection. Preferably, the guide element is formed integrally with the pressure housing wall. The guide element and the pressure housing wall could be connected to one another in a material-fitting manner, for example with an adhesive connection and / or a welded connection. It would also be conceivable for the guide element and the pressure housing wall to be formed in one piece. "Integral" should be understood to mean formed in one piece.Preferably, this one piece is produced from a single blank, a mass and / or a casting, for example by a casting process, a punching process, a cutting process and / or in a printing process, for example a 3D printing process, or any other process that appears appropriate to the person skilled in the art.

[0027] The guide element is preferably aligned parallel to the movement axis. In particular, the guide element guides at least the rotation element parallel to the movement axis. The guide element can prevent a movement, for example an evasive movement, of the rotation element perpendicular to the movement axis. In particular, the guide element is provided to ensure, in at least one operating state of the reciprocating piston engine device, in particular in the intake operating state and / or the compression operating state, a translationally uniform guidance of the piston and / or the rotor in the pressure housing along the movement axis. The guide element can have at least one guide web or a guide rod. It would be conceivable for the guide element to have a first guide web and at least one second guide web, which are arranged parallel to one another, and in particular parallel to the movement axis.The rotating element could be movably mounted between the first guide web and the second guide web. For guidance parallel to the movement axis, the rotating element could only contact the first and second guide rods and, in particular, be free from contact with the pressure housing wall. Preferably, the guide element is a guide rail in which at least the rotating element is movably mounted. The rotating element can roll along the movement axis in the guide rail. Particularly preferably, the rotating element is free from contact with the pressure housing wall when guided in the guide rail.

[0028] The guide element could extend across the entire interior of the pressure housing, specifically across the entire longitudinal extent of the pressure housing wall, parallel to the movement axis. In this context, a "longitudinal extent" of an object is understood to mean an extent of the object in a longitudinal direction of the object. The "longitudinal direction" of the object is a direction that is aligned and / or runs parallel to a longest edge and / or side of a smallest, particularly imaginary, cuboid that just encloses the object. The guide element can extend parallel to the movement axis over at least 30%, advantageously at least 50%, preferably at least 70%, and preferably over at most 95%, particularly preferably at most 80% of the longitudinal extent of the pressure housing wall.

[0029] Alternatively or additionally, it is proposed that the rotating element directly contacts at least the pressure housing wall of the pressure housing. This allows a design to be further optimized and simplified. In particular, possible guide elements can be dispensed with, and direct and immediate guidance of at least the rotating element on the pressure housing can be provided. Furthermore, a manufacturing process can be simplified because the rotor and / or the piston can be inserted directly into the pressure housing, preferably from above, viewed in the vertical direction, possibly without additional positioning and insertion of at least the rotating element into at least one guide element.

[0030] In one embodiment, the reciprocating piston machine device could be free of at least one guide element, so that at least the rotating element directly contacts at least the pressure housing wall and is guided by the contact on the pressure housing wall. If the guide element has the first and second guide rods, these, together with the pressure housing wall, could provide guidance for at least the rotating element parallel to the movement axis and delimit an intermediate space in which at least the rotating element is movably mounted. "Direct" contact should be understood to mean that no further objects, components and / or structural units are arranged between a first object and a second object, which are in direct contact. Preferably, the direct contact is direct surface contact between a surface of the first object and a surface of the second object.

[0031] In this document, numerals such as "first" and "second," which precede certain terms, serve only to distinguish between objects and / or to correlate objects with each other and do not imply a total number and / or ranking of the objects. In particular, a "second" object does not necessarily imply the presence of a "first" object.

[0032] Furthermore, it is proposed that the bearing unit comprise at least one further rotational element with a further rotational axis, which is oriented perpendicular to the rotational axis of the rotational element. This provides particularly stable and uniform support for the piston and / or the rotor within the pressure housing, thus increasing the design and operating efficiency of the reciprocating piston engine device. Furthermore, guide elements of the pressure housing or other aids for guiding the piston and / or the rotor can preferably be dispensed with, thus enabling a simpler design of at least the pressure housing.

[0033] In particular, the further rotational axis is oriented perpendicular to the movement axis. While the rotational axis preferably points vertically, the further rotational axis can be oriented horizontally, particularly if the movement axis is also oriented horizontally. The further rotational element could be designed differently than the rotational element. For example, the further rotational element could be designed as a ball and the rotational element as a roller. Preferably, the rotational element and the further rotational element are designed at least substantially identically to one another, regardless of manufacturing tolerances. Particularly preferably, the further rotational element is designed as a roller.In this document, “at least substantially” is to be understood as meaning that a deviation from a predetermined value and / or orientation is less than 25%, preferably less than 10% and particularly preferably less than 5% of the predetermined value and / or orientation.

[0034] The bearing unit could also have additional rotation elements, in particular a plurality of rotation elements and / or further rotation elements, for example four or six rotation elements and / or further rotation elements, which are designed either analogously to the rotation element or the further rotation element. The bearing unit advantageously has at least two rotation elements and at least two further rotation elements. If the bearing unit has at least the further rotation element in addition to the rotation element, the bearing unit preferably always has an even and equal number of rotation elements and further rotation elements.

[0035] The bearing unit could be at least partially arranged on at least the piston. If the bearing unit is mounted on the rotor, a particularly compact and efficient design of a reciprocating piston engine device can be provided. Advantageously, at least the rotation element is arranged on the rotor such that its axis of rotation is aligned perpendicular to the end face of the piston. Preferably, the bearing unit has at least four rotation elements, with two rotation elements each being arranged opposite one another and symmetrically to the axis of movement on the long sides of the rotor. Furthermore, the bearing unit can have at least eight rotation elements, with four rotation elements each being arranged opposite one another and symmetrically to the axis of movement on the long sides of the rotor.It would also be conceivable for the bearing unit to have at least eight additional rotational elements, with four additional rotational elements being arranged opposite one another and symmetrically to the axis of movement on the long sides of the rotor. The bearing unit, in particular the rotational element and / or the additional rotational element, could be mounted on the rotor by means of a force-locking and / or form-locking connection, for example by means of a snap-in connection and / or plug-in connection and / or rotary connection and / or screw connection. The bearing unit is advantageously arranged on the rotor in such a way that rotation of the rotational element about the axis of rotation, in particular additional rotation of the additional rotational element about the additional axis of rotation, is possible.

[0036] It is further proposed that the reciprocating piston engine device have at least one non-contact seal for sealing at least one gap between the piston and the pressure housing. By using such a non-contact seal, contamination of the fluid can be prevented, precisely because the use of sliding seals and lubricants can be dispensed with. Furthermore, such an oil-free / lubricant-free design eliminates the need for additional sealing elements, which are normally necessary to keep the lubricant away from the piston and the fluid. This allows a design to be significantly improved and made more efficient and compact. Furthermore, friction losses between the piston and the pressure housing can be prevented, thus in turn increasing the operating and performance efficiency of the reciprocating piston engine device.Furthermore, wear on the seal and piston can be reduced, preferably prevented, which in turn increases the overall service life of the reciprocating piston engine device. This preferably enables maintenance-free operation of the reciprocating piston engine device, without the need for complex and / or costly replacement of the piston and / or seal due to wear.

[0037] The non-contact seal is preferably a shaft seal. In particular, the seal is arranged on the piston. The non-contact seal can be arranged on the piston in the circumferential direction of the piston, in particular in the circumferential direction of its polygonal cross-section. The non-contact seal surrounds the piston along its circumferential surface facing the inside of the pressure housing, at least in sections, advantageously at least 50%, preferably at least 80%, and particularly preferably completely. In particular, at least the end face of the piston is free of the non-contact seal.

[0038] The non-contact seal can, for example, be designed as a lamella or gap seal. To provide a particularly efficient and design-friendly seal, it is proposed that the non-contact seal be a labyrinth seal. This can reduce, preferably prevent, friction losses between the piston and the pressure housing, and provide a wear-free seal. In particular, the labyrinth seal is a labyrinth seal known to those skilled in the art. During operation of the reciprocating piston machine device, the fluid can penetrate into gaps in the labyrinth seal and, due to turbulence in chambers / gaps between individual lamellae of the labyrinth seal, create a seal with the pressure housing wall of the pressure housing.

[0039] It is further proposed that the reciprocating piston engine device have at least one coating, which is arranged on an inner side of the pressure housing and / or on an outer side of the piston to compensate for manufacturing tolerances. This makes it possible to dispense with additional manufacturing steps in the manufacture of the reciprocating piston engine device, namely precision grinding and polishing of components, in particular of the pressure housing and / or the piston. This can increase manufacturing and cost efficiency. Furthermore, the use of the coating can provide a secure and closed seal and increase sealing efficiency. This, in turn, can increase the operating and / or performance efficiency of the reciprocating piston engine device.

[0040] After the manufacture / production of the pressure housing, the inside of the pressure housing, and at least the aforementioned pressure housing wall, may exhibit uneven and rough areas due to the manufacturing process. To compensate for this uneven surface of the inside of the pressure housing, in particular the pressure housing wall, and to provide a flat and closed surface on the inside, the coating is preferably applied to the inside of the pressure housing and / or to the outside of the piston. However, after the coating has been applied, this may still exhibit slight unevenness. To eliminate and compensate for these unevenness, the piston can be inserted into the pressure housing and the reciprocating piston machine device can be operated for a certain period of time.In particular, the piston is moved in the pressure housing, preferably until, after a certain running time, the piston reaches a certain bearing clearance of a few micrometers, for example, at most 1000 pm, advantageously at most 500 pm, preferably at most 100 pm, and particularly preferably at most 80 pm, with the pressure housing. In particular, this bearing clearance is formed by mechanical removal of the coating due to the movement of the piston in the pressure housing. Thus, by means of the independent operation of the reciprocating piston machine device itself, a precise and smooth surface of the pressure housing and / or the piston can be provided, without increased manufacturing effort with precision grinding and polishing of components.Furthermore, particularly in combination with the non-contact seal, it can be ensured that the coating on the pressure housing and / or on the piston is not subjected to further mechanical stress and thus is not further worn away during regular operation of the reciprocating piston machine device, whereby the gap between the pressure housing and the piston can be kept constant.

[0041] In order to further increase efficiency in terms of operating, power, and / or working efficiency, and to improve the efficiency of a reciprocating piston engine device, it is proposed that the reciprocating piston engine device have a reset unit with at least one elastic element connected to the piston. The reset unit is preferably provided for recuperating braking energy required by the piston for a change of direction, in particular when changing from the intake operating state to the compression operating state and vice versa. This advantageously makes it possible to achieve a particularly efficient spring-mass system that is only limited by its own damping caused by friction in the bearings and electrical losses in the coils of the stator unit.In this document, an "elastic element" is understood to mean an element that can be repeatedly deformed by applying external force without being mechanically damaged or destroyed, and which, in particular, automatically returns to a basic shape, in particular a rest position, after deformation. In particular, the element is reversibly elastically deformable. The element could exhibit linear-elastic or non-linear-elastic behavior. The elastic element can be flexible, i.e., bendable. The elastic element can absorb external forces, temporarily store them, and release at least a large portion of them when the load is removed, and can function as an intermediate energy store. The elastic element is preferably designed as a spring, in particular as a return spring. The elastic element is preferably designed as a helical spring.As an alternative to a helical spring, however, the use of disc springs, rubber springs, pneumatic springs, or another type of elastic element would also be conceivable without departing from the scope of the present invention. Preferably, the elastic element is fixed at one end to a wall of the housing unit, the pressure housing, and / or a valve unit of the reciprocating piston machine device. The return unit can have at least one guide element and / or at least one bearing element for guiding and / or supporting the elastic element. Preferably, the piston has at least one recess, which can be designed, for example, as a bore or the like, and which is provided for at least partially receiving the elastic element.The recess is preferably provided to accommodate the elastic element at least to a large extent, preferably completely, in at least one operating state of the reciprocating piston engine device, advantageously at maximum displacement of the piston. This advantageously saves space and thus provides a particularly compact and at the same time efficient reciprocating piston engine device. The term "to a large extent" is understood here to mean at least 55%, advantageously at least 65%, preferably at least 75%, particularly advantageously at least 85%, and particularly preferably at least 90% of an amount, in particular a volume and / or mass fraction.

[0042] It is also proposed that the piston have a first piston element and at least one second piston element, which are movable relative to one another. This allows a design to be further improved and the efficiency, with regard to operating and performance efficiency, of the reciprocating piston engine device to be further increased. In particular, thermal expansion of the piston within the pressure housing can be compensated for, and a gap dimension between an outer side of the piston and an inner side of the pressure housing can be reversibly adjusted during operation of the reciprocating piston engine device. This ensures an optimal gap dimension at all times, regardless of the specific thermal expansion of a piston material. This minimizes, preferably prevents, leakage, and provides improved sealing.

[0043] The piston could be formed at least partially, at least largely, or entirely from, for example, stainless steel, titanium, tungsten, glass ceramic, and / or a composite material. In order to compensate for material-specific thermal expansion of the piston within the pressure housing during operation of the reciprocating piston engine device and thus, in turn, increase the efficiency of the reciprocating piston engine device, it is proposed that the second piston element be designed to move the first piston element perpendicular to the movement axis during a movement along the movement axis.

[0044] Advantageously, a first direction of movement of the first piston element runs perpendicular to a second direction of movement of the second piston element. The second piston element is movable along the axis of movement. Due to the movement along the axis of movement of the second piston element, the first piston element can move perpendicular to the axis of movement. The second piston element can press the first piston element outwards perpendicular to the axis of movement, i.e. towards the pressure housing wall. Furthermore, the second piston element can at least partially release a pressure perpendicular to the axis of movement against the first piston element and enable a movement of the first piston element perpendicular to the axis of movement, specifically away from the pressure housing wall. Advantageously, the return unit of the reciprocating piston machine device is at least partially arranged on the second piston element.In particular, the second piston element has the already described recess, in particular bore, in which the elastic element is arranged.

[0045] The piston preferably has at least a third piston element. In particular, all three piston elements are arranged next to one another, with the second piston element being arranged centrally and contacting the first piston element and the third piston element. The descriptions for the first piston element can be applied analogously to the third piston element. In particular, the first piston element and the third piston element are designed identically to one another. When the second piston element moves along the movement axis, the second piston element can simultaneously trigger a movement of the first piston element and the third piston element perpendicular to the movement axis, in particular pressing the first piston element and the third piston element outwards, towards the pressure housing wall, or enabling a movement of the first piston element and the third piston element away from the pressure housing wall.

[0046] It is further proposed that the reciprocating piston machine device have at least one further piston arranged within the pressure housing, which is operatively connected to the rotor on a side opposite the piston. This can advantageously further increase the efficiency of the reciprocating piston machine device with regard to design, operation, and / or performance efficiency. In particular, kinetic energy of the rotor can be used to compress and / or convey fluids in both directions of movement along the axis of movement. Preferably, the further piston is designed to be at least substantially identical to the piston, regardless of manufacturing tolerances. Preferably, the further piston is designed to be integral, in particular one-piece, with the rotor. In particular, the explanations and descriptions relating to the piston in this document are also applicable to the further piston.The further piston could also be divided into a further first piston element and at least one further second piston element, which are movable relative to one another. The invention further relates to a reciprocating piston engine with at least one reciprocating piston engine device according to one of the previously described embodiments. Such a reciprocating piston engine is characterized in particular by an increased degree of efficiency, which can be achieved by the previously described embodiments of the reciprocating piston engine device. The reciprocating piston engine can, without being limited thereto, be designed, for example, as a reciprocating piston pump, as a reciprocating piston compressor, as a heat pump or as a Stirling engine and, depending on the embodiment, can be used for a wide variety of applications, for example for generating compressed air, compressing refrigerants, conveying fluids or generating electrical energy.

[0047] Furthermore, the present invention relates to a system which comprises at least two reciprocating piston machines which are arranged next to one another along the movement axis and are designed for counter-rotating operation. In this way, disruptive effects in the operation of a reciprocating piston machine, such as vibrations, can be compensated. This can increase efficiency, in particular work and / or operating efficiency, and provide improved system performance. Furthermore, the use of absorber masses can advantageously be dispensed with. The system could have further reciprocating piston machines, specifically at least one further reciprocating piston machine which is preferably arranged adjacent to the at least two reciprocating piston machines along the movement axis and is designed for counter-rotating operation to at least one of the two reciprocating piston machines.Advantageously, the system comprises an even number of reciprocating piston engines, with at least two reciprocating piston engines always being balanced to operate in opposite directions to each other, in particular to further increase the effect of increasing efficiency and performance.

[0048] The reciprocating piston engine device and the reciprocating piston engine are not intended to be limited to the application and embodiment described above. In particular, the reciprocating piston engine device and / or the reciprocating piston engine and / or the system may have a number of individual elements, components, and / or units that differs from the number stated herein to fulfill a functionality described herein. Furthermore, within the value ranges specified in this document, values ​​within the stated limits are also considered disclosed and can be used arbitrarily.

[0049] Drawings

[0050] Further advantages will become apparent from the following description of the drawings. The drawings illustrate two exemplary embodiments of the invention. The drawings, the description, and the claims contain numerous features in combination. Those skilled in the art will also expediently consider the features individually and combine them into useful further combinations.

[0051] They show:

[0052] Fig. 1 shows a reciprocating piston machine designed as a working machine, namely as a reciprocating piston compressor, for conveying and / or compressing a fluid with at least one reciprocating piston machine device,

[0053] Fig. 2 shows a system with at least two reciprocating piston engines, which are arranged next to each other along a movement axis and are designed for counter-rotating operation,

[0054] Fig. 3 is a schematic sectional view with a section perpendicular to the movement axis of the reciprocating piston machine with the reciprocating piston machine device in the direction of the movement axis,

[0055] Fig. 4 is a sectional view of the reciprocating piston engine with a section parallel to the movement axis, wherein the reciprocating piston engine device comprises a bearing unit with at least one rotation element for the linearly movable mounting of a rotor relative to a pressure housing of the reciprocating piston engine device,

[0056] Fig. 5 is a close-up view of an arrangement of the rotor and at least one piston of the reciprocating piston engine device within the pressure housing, as well as a close-up view of a seal of the reciprocating piston engine device for sealing a gap between the piston and the pressure housing,

[0057] Fig. 6 is a detailed view of the rotor with the piston and another piston of the reciprocating piston machine device, Fig. 7 is the detailed view according to Figure 6 with a vertical section,

[0058] Fig. 8 shows a cross-section of the pressure housing with a coating to compensate for manufacturing tolerances on an inner side of the pressure housing and a cross-section of the piston arranged within the pressure housing,

[0059] Fig. 9 is a detailed view of a rotor, a bearing unit and at least one piston of a reciprocating piston machine device in an alternative embodiment, wherein the piston has at least two piston elements which are movable relative to one another,

[0060] Fig. 10 shows a changed position / position of a central piston element of the piston in contrast to Figure 9,

[0061] Fig. 11 is a further detailed view according to Figure 9 to illustrate an arrangement of the piston elements to each other and

[0062] Fig. 12 the detailed view according to Figure 9 with only one piston element of the piston.

[0063] Description of the embodiments

[0064] Figure 1 shows a reciprocating piston engine 10a, which is designed as a working machine for converting electrical energy into mechanical energy. In this exemplary embodiment, the reciprocating piston engine 10a is designed as a reciprocating piston compressor. Alternatively, the reciprocating piston engine 10a could also be a prime mover, which could, for example, be designed as a Stirling engine.

[0065] The reciprocating piston engine 10a has a reciprocating piston engine device 12a. The reciprocating piston engine device 12a has a housing unit 98a. In this case, the housing unit 98a is designed as an outer housing unit. The housing unit 98a is cuboid-shaped. The reciprocating piston engine device 12a comprises a gas-tight pressure housing 14a (see Figure 3). In this case, the gas-tight pressure housing 14a is arranged within the housing unit 98a. Furthermore, the reciprocating piston engine device 12a comprises at least one rotor 16a (see Figure 3). The rotor 16a is arranged within the pressure housing 14a and mounted for translational movement along a movement axis 18a. To transmit drive forces to the rotor 16a, the reciprocating piston engine device 12a has at least one stator unit 24a. In this case, the reciprocating piston engine device 12a has a linear drive.In this exemplary embodiment, the reciprocating piston engine device 12a has at least one further stator unit 100a for transmitting drive forces to the rotor 16a. The further stator unit 100a is arranged symmetrically to the stator unit 24a with respect to the movement axis 18a.

[0066] Figures 1 to 3 show that the reciprocating piston engine device 12a has a fan 102a. The fan 102a is arranged on the stator unit 24a and is intended to generate a cooling air flow for dissipating waste heat from the stator unit 24a. Likewise, the reciprocating piston engine device 12a has a further fan 104a, which is arranged on the further stator unit 100a and is intended to generate an air flow for dissipating waste heat from the further stator unit 100a.

[0067] For supplying and / or discharging a fluid into and / or out of a working chamber 106a (see Figure 3), the reciprocating piston machine device 12a has a valve unit 26a. The valve unit 26a has at least one valve opening 110a for the flow of the fluid (see Figure 3). In this exemplary embodiment, the valve opening 110a is an outlet valve opening. An outlet valve 118a of the valve unit 26a is arranged at the outlet valve opening 110a. The outlet valve 118a controls, regulates, and / or regulates an outflow, namely the discharge of the fluid from the working chamber 106a. The reciprocating piston machine device 12a could have only one connection, which is fluidically connected to the valve opening 110a. In the present case, the reciprocating piston machine device 12a has at least two connections 130a, 132a which are fluidly connected to the valve opening 110a.This allows the fluid to be removed more efficiently and pressure losses to be reduced.

[0068] To provide a fluid supply, the valve unit 26a has at least one inlet valve 122a. The inlet valve 122a is arranged at a further valve opening 120a designed as an inlet valve opening (see Figure 3). The inlet valve 122a controls, regulates, and / or regulates an inflow, specifically the supply of fluid, into the working chamber 106a. In the present embodiment, the inlet valve 122a is designed as a reed valve 124a.

[0069] In this case, too, the reciprocating piston engine device 12a could have only one additional connection, which is fluidly connected to the additional valve opening 120a. To provide a particularly advantageous and efficient design, the reciprocating piston engine device 12a has at least two additional connections 164a, 166a, which are fluidly connected to the additional valve opening 120a. In this exemplary embodiment, the additional connections 164a, 166a each have air filters.

[0070] Figure 2 shows a system 50a comprising at least two reciprocating piston machines 10a, 10'a arranged side by side along the movement axis 18a and configured for counter-rotating operation. Counter-rotating operation of the rotors 16a of the respective reciprocating piston machines 10a, 10'a enables mutual cancellation of the dynamic forces of their moving masses, thus preventing vibrations. The reciprocating piston machines 10a, 10'a are configured essentially identically to one another. For the sake of simplicity, the functioning of the reciprocating piston machines 10a, 10'a will be explained below using only the reciprocating piston machine 10a, with the relevant explanations being analogously transferable to the at least one further reciprocating piston machine 10'a.

[0071] Figure 3 shows a schematic sectional view of the reciprocating piston engine 10a with the reciprocating piston engine device 12a according to Figure 1, perpendicular to the movement axis 18a. This view provides a view into the gas-tight pressure housing 14a and onto the rotor 16a, which is mounted within the pressure housing 14a for translational movement along the movement axis 18a. The reciprocating piston engine device 12a comprises at least one piston 20a arranged within the pressure housing 14a, which is operatively connected to the rotor 16a. In this exemplary embodiment, the piston 20a and the rotor 16a are formed integrally, in particular as a single piece (see Figure 7).

[0072] To clarify the arrangement of the rotor 16a and at least the piston 20a within the pressure housing 14a, reference is generally made to Figures 3 to 5. Figures 6 and 7 illustrate the precise design and construction of the rotor 16a and at least the piston 20a. It can be seen that the rotor 16a has a polygonal cross-section running perpendicular to the movement axis 18a. In the present case, the rotor 16a has a rectangular cross-section running perpendicular to the movement axis 18a. Furthermore, the piston 20a also has a polygonal cross-section running perpendicular to the movement axis 18a. In this embodiment, the piston 20a has a rectangular cross-section running perpendicular to the movement axis 18a.

[0073] To seal an intermediate space between the piston 20a and the pressure housing 14a, the reciprocating piston engine device 12a has at least one non-contact seal 70a (see Figures 5, 6, and 7). In this case, the non-contact seal 70a is designed as a labyrinth seal 74a. Figure 5 illustrates the design of the labyrinth seal. This allows for the provision of a reciprocating piston engine device 12a free of sliding seals and lubricants, which can lead to fluid contamination. Furthermore, friction losses between the piston 20a and the pressure housing 14a can be reduced, preferably avoided. Furthermore, maintenance-free operation of the reciprocating piston engine device 12a can be provided, since seal wear can be greatly reduced.

[0074] To provide an efficient spring-mass system, the reciprocating piston engine device 12a has a return unit 60a (see Figures 3 and 4). The return unit 60a comprises at least one elastic element 62a, which is connected to the piston 20a. In this case, the elastic element 62a is designed as a return spring. The piston 20a has a bore within which the elastic element 62a, designed as a return spring, is connected to the piston 20a. The return unit 60a has a guide element 86a for guiding the elastic element 62a. The guide element 86a and the elastic element 62a are connected to the housing unit 98a opposite an end face 68a of the piston 20a.

[0075] Before further detailing the arrangement, design, and mounting of the rotor 16a and at least the piston 20a within the pressure housing 14a, the stator unit 24a and a drive of the reciprocating piston machine device 12a will first be briefly explained. The stator unit 24a has at least one coil 54a (see Figure 3). One coil 54a is sufficient for the operation of the reciprocating piston machine device 12a. In the present case, the stator unit 54a has a plurality of coils 54a, wherein for the sake of clarity, only one coil is provided with a reference symbol. The further stator unit 100a has at least one further coil 134a. In the present case, the further stator unit 100a has a plurality of further coils 134a, wherein here too, for the sake of clarity, only one further coil is provided with a reference symbol. The stator unit 24a is arranged outside the pressure housing 14a.The further stator unit 100a is also arranged outside the pressure housing 14a, specifically symmetrically to the stator unit 24a on the opposite side of the pressure housing 14a with respect to the movement axis 18a. The reciprocating piston machine device 12a has at least two permanent magnets 40a, 42a. The permanent magnets 40a, 42a are arranged on the rotor 16a such that their respective magnetization directions are aligned perpendicular to the movement axis 18a. In the present case, the reciprocating piston machine device 12a has a plurality of permanent magnets 40a, 42a, 44a, 46a, 48a, which are arranged on the rotor 16a in the form of a Halbach array (see Figure 3). The permanent magnets 40a, 42a, 44a, 46a, 48a are arranged on an upper side of the rotor 16a in the form of a Halbach array in order to amplify the magnetic fields of the permanent magnets 40a, 42a, 44a, 46a, 48a in the direction of the stator unit 24a.Likewise, the reciprocating piston engine device 12a has a plurality of additional permanent magnets (not provided with reference numerals) arranged on the underside of the rotor 16a in the form of a Halbach array to amplify the magnetic fields in the direction of the additional stator unit 100a. In an operating state of the reciprocating piston engine device 12a, the coils 54a and the additional coils 134a generate magnetic fields of alternating polarity, which act on the permanent magnets 40a, 42a, 44a, 46a, 48a arranged on the rotor 16a and cause the rotor 16a to oscillate along the movement axis 18a. At least in Figure 3, it can be seen that the working chamber 106a is delimited, at least in sections, by the piston 20a and at least the pressure housing 14a.Through translational movement of the piston 20a and the rotor 16a along the movement axis 18a, the working chamber 106a increases or decreases along the movement axis 18a. In the present exemplary embodiment, the reciprocating piston machine device 12a comprises an additional piston 82a arranged within the pressure housing 14a (see Figures 3, 4, and 5). The additional piston 82a is operatively connected to the rotor 16a on a side opposite the piston 20a. In the present case, the additional piston 82a and the rotor 16a are also formed integrally, in particular as a single piece. In particular, the detailed views in Figures 6 and 7 illustrate the design of the piston 20a, the rotor 16a, and the additional piston 82a.

[0076] Furthermore, the reciprocating piston engine device 12a comprises at least one further working chamber 108a, which is at least partially delimited by the further piston 82a and at least the pressure housing 14a. Due to the oscillating movement of the rotor 16a along the movement axis 18a, a fluid located in the working chamber 106a is alternately compressed and / or conveyed by the piston 20a, and a further fluid located in the further working chamber 108a is alternately compressed and / or conveyed by the further piston 20a.

[0077] For supplying and / or discharging a further fluid into and / or out of the further working chamber 108a, the reciprocating piston engine device 12a has at least one further valve unit 172a. The further valve unit 172a is designed at least substantially identically to the valve unit 26a, regardless of manufacturing tolerances. Therefore, a further detailed description of the further valve unit 172a is omitted here. The statements regarding the valve unit 26a and its subassemblies and components can be applied analogously to the further valve unit 172a.

[0078] In the present case, the reciprocating piston engine 10a is largely mirror-symmetrical with respect to an imaginary plane 170a oriented perpendicular to the movement axis 18a, which plane runs through a center point of the movement axis 18a (see Figures 1 and 3). However, deviating from a mirror symmetry with respect to the plane 170a, the valve unit 26a and the further valve unit 172a are arranged mirror-inverted with respect to the movement axis 18a. It is crucial that the valve unit 26a and the further valve unit 172a are arranged such that the supply of fluid by means of the valve unit 26a takes place on an opposite side perpendicular to the movement axis 18a to a supply of fluid by means of the further valve unit 172a. Furthermore, a discharge of fluid by means of the valve unit 26a takes place on an opposite side perpendicular to the movement axis 18a to a discharge of fluid by means of the further valve unit 172a (see Figures 1 and 3).

[0079] For the linearly movable mounting of the rotor 16s relative to a pressure housing wall 34a of the pressure housing 14a, the reciprocating piston engine device 12a has a bearing unit 28a (see Figure 4). The bearing unit 28a comprises at least one rotational element 30a, which has a rotational axis 32a perpendicular to the movement axis 18a (see Figure 6). Figure 4 illustrates that in this present embodiment, the bearing unit 28a has four rotational elements 30a, wherein, for the sake of clarity, only one rotational element is provided with a reference numeral. In this case, the rotational elements 30a are each identical to one another, regardless of manufacturing tolerances. The statements regarding the rotational element 30a can also be applied to the other rotational elements of the bearing unit 28a. In this case, the bearing unit 28a is a rolling bearing unit. The rotating element 30a is designed as a roller.Alternatively, the rotation element 30a could also be designed as a ball. In an assembled state, the rotation axis 32a of the rolling element 30a points in the vertical direction 186a when the movement axis 18a is aligned in the horizontal direction 188a (see Figure 6). To provide a particularly compact design and construction of the reciprocating piston machine device 12a, the bearing unit 28a is mounted on the rotor 16a. In the present case, four rotation elements 30a are mounted on the rotor 16a, with two rotation elements 30a each arranged opposite one another and symmetrically to the movement axis 18a on the longitudinal sides of the rotor 16a.

[0080] To ensure secure and uniform guidance of at least the rotary element 30a, the pressure housing 14a has at least one guide element 88a (see Figures 4 and 5). In this exemplary embodiment, the guide element 88a is formed separately from the pressure housing wall 34a and arranged thereon, for example by means of a force, form, and / or material connection. The sectional view in Figure 4 illustrates that the guide element 88a is aligned parallel to the movement axis 18a. The guide element 88a guides at least the rotary element 30a parallel to the movement axis 18a. Figure 5 shows that the guide element 88a is designed as a guide rail. To provide particularly stable guidance, the reciprocating piston machine device 12a has at least one further guide element 174a (see Figure 4). The further guide element 174a is arranged parallel to the guide element 88a.Furthermore, the further guide element 174a is arranged on a side opposite the guide element 88a and the pressure housing wall 34a on a further pressure housing wall 190a of the pressure housing 14a.

[0081] To ensure a secure and closed seal between the pressure housing 14a and the piston 20a, one surface of the pressure housing 14a and one surface of the piston 20a must be as flat as possible. Figure 8a schematically shows a vertical section, specifically a cross-section through the pressure housing 14a without the piston 20a inserted. It can be seen that after manufacture / production, an inner side 192a of the pressure housing 14a has uneven and rough spots due to the manufacturing process. To compensate for this uneven surface of the inner side 192a of the pressure housing 14a and to provide a flat and closed surface of the inner side 192a, the reciprocating piston machine device 12a has at least one coating 64a applied to the inner side 192a of the pressure housing 14a (see Figure 8b). Alternatively or additionally, this coating 64a can also be applied to an outer side 66a of the piston 20a.However, after the coating 64a has been applied, it still exhibits slight unevenness. To eliminate and compensate for these unevennesses, the piston 20a is inserted (see Figure 8c) and the reciprocating piston engine 10a is operated for a certain period of time. In particular, the piston 20a is moved in the pressure housing 14a until, after a certain running time, the piston 20a reaches a certain bearing clearance of a few micrometers, in this case a maximum of 100 pm, with the pressure housing 14a, specifically with the coating 64a (see Figure 8d). This bearing clearance has developed due to the mechanical wear of the coating 64a due to the movement of the piston 20a in the pressure housing 14a.Thus, by operating the reciprocating piston engine 10a itself, a precise and smooth surface of the pressure housing 14a and / or the piston 20a can be provided, without the need for precision grinding and polishing of components, in particular the pressure housing 14a and / or the piston 20a, and thus without increased manufacturing effort. Due to the non-contact seal 70a on the piston 20a, the coating 64a is not subjected to further mechanical stress during regular operation of the reciprocating piston engine 10a and thus is not further worn away, whereby the gap between the pressure housing 14a and the piston 20a remains constant.

[0082] Figures 9 to 12 show a further embodiment of the invention. The following descriptions are essentially limited to the differences between the embodiments; with regard to identical components, features, and functions, reference can be made to the description of the embodiment in Figures 1 to 8. To distinguish the embodiments, the letter a in the reference numerals of the embodiment in Figures 1 to 8 has been replaced by the letter b in the reference numerals of the embodiment in Figures 9 to 12.

[0083] Figure 9 shows part of a reciprocating piston engine device 12b in an alternative embodiment. In the present case, the alternative embodiment focuses on a rotor 16b of the reciprocating piston engine device 12b, a bearing unit 28b of the reciprocating piston engine device 12b, and at least one piston 20b of the reciprocating piston engine device 12b. The piston 20b is operatively connected to the rotor 16b. On a side opposite the piston 20b, a further piston 82b of the reciprocating piston engine device 12b is arranged on the rotor 16b, which in turn is operatively connected to the rotor 16b. The rotor 16b, the piston 20b, and the further piston 82b move, in an inserted state, in a pressure housing of the reciprocating piston engine device 12b (not shown here) along a movement axis 18b.In contrast to the design of the piston 20a according to Figures 3 to 7, the piston 20b in the present embodiment is divided into several parts. The piston 20b has a first piston element 76b and at least one second piston element 78b, which are movable relative to one another. In the present case, the piston 20b has at least one third piston element 80b. All three piston elements 76b, 78b, 80b are arranged next to one another, with the second piston element 78b being arranged centrally and contacting the first piston element 76b and the third piston element 80b. The descriptions for the first piston element 76b can be applied analogously to the third piston element 80b. In the present case, the first piston element 76b and the third piston element 80b are designed identically to one another.In this embodiment, the second piston element 78b is designed to move the first piston element 76b perpendicular to the movement axis 18b during a movement along the movement axis 18b. When the second piston element 78b moves along the movement axis 18b, the third piston element 80b moves simultaneously, specifically perpendicular to the movement axis 18b. Thus, for the sake of simplicity, a description is given only with reference to the first piston element 76b, which, however, is also transferable to the third piston element 80b.

[0084] A first direction of movement of the first piston element 76b runs perpendicular to a second direction of movement of the second piston element 78b. The second piston element 78b is movable along the movement axis 18b. Figure 9 shows a state in which the second piston element 78b is pushed out further along the movement axis 18b than in Figure 10. Due to the movement along the movement axis 18b of the second piston element 78b, the first piston element 76b moves perpendicular to the movement axis 18b. In Figure 10, the second piston element 78b pushes the first piston element 76b outward perpendicular to the movement axis 18b, i.e., toward a pressure housing wall (not shown here).Furthermore, the second piston element 78b can at least partially release a pressure perpendicular to the movement axis 18b against the first piston element 76b and enable a movement of the first piston element 76b perpendicular to the movement axis 18b, specifically away from the pressure housing wall (not shown here) (see Figure 9). Figures 9 and 10 illustrate that a return unit with an elastic element 62b of the reciprocating piston machine device 12b is arranged on the second piston element 78b. In the present case, the second piston element 78b has the bore already described in the aforementioned exemplary embodiment "a" according to Figures 1 to 8, in which the elastic element 62b is arranged.

[0085] For the movable fixation of the piston elements 76b, 78b, and 80b relative to one another, it can be seen in Figures 11 and 12 that at least the first piston element 76b has a first opening 176b. At least one retaining element 178b of the piston is arranged in the first opening 176b. The retaining element 178b is designed here as a plug-in element. When the second piston element 78b is inserted, the retaining element engages in a second opening of the second piston element 78b (not shown) and thus movably connects the piston elements 76b, 78b to one another. The same fixation principle is also applied to the second piston element 78b and the third piston element 80b.

[0086] In this embodiment, the further piston 82b also has a further first piston element 180b, a further second piston element 182b, and at least one further third piston element 184b. The explanations and descriptions of the first piston element 76b are transferable to the further first piston element 180b, the explanations and descriptions of the second piston element 78b are transferable to the further second piston element 182b, and the explanations and descriptions of the third piston element 80b are transferable to the further third piston element 184b.

[0087] To support at least the rotor 16b, the reciprocating piston machine device 12b has a bearing unit 28b. The bearing unit 28b has at least one rotation element 30b. The rotation element 32b has a rotation axis 32b perpendicular to the movement axis 18b. In the present case, the bearing unit 28b has at least one further rotation element 36b with a further rotation axis 38b, which is oriented perpendicular to the rotation axis 32b of the rotation element 30b. The further rotation axis 32b is oriented perpendicular to the movement axis 18b (see Figures 9 and 11). While the rotation axis 32b points in the vertical direction 186b, the further rotation axis 32b is oriented horizontally, although the movement axis 18a is also oriented in the horizontal direction 188b.Figures 9 to 11 illustrate that, in this embodiment, the bearing unit 28b has a total of eight rotation elements 30b and eight further rotation elements 36b, whereby, for the sake of clarity, only one further rotation element 36b is provided with a reference symbol. The further rotation elements 36b are each identical to one another in this case, regardless of manufacturing tolerances. The statements regarding the further rotation element 36b are also applicable to the other further rotation elements of the bearing unit 28b. The further rotation element 36b is designed as a roller. Alternatively, the further rotation element 36b could also be designed as a ball. The further rotation element 36b is arranged on the rotor 16b.In this case, eight rotation elements 32b are mounted on the rotor 16b, with four rotation elements 32b each arranged opposite one another and symmetrically to the movement axis 18b on the longitudinal sides of the rotor 16b. Furthermore, a total of eight further rotation elements 36b are mounted on the rotor 16b, with four further rotation elements 36b each arranged opposite one another and symmetrically to the movement axis 18b on the longitudinal sides of the rotor 16b.

[0088] The special arrangement of the rotation element 30b and at least the further rotation element 36b, as well as the design of the bearing unit 28b, enable direct contact and mounting on a pressure housing wall of the pressure housing (not shown here) of the reciprocating piston engine device 12b. This eliminates the need for guide elements of the pressure housing for guiding the rotation element 30b and at least the further rotation element 36b, thus providing a particularly compact and efficient design of a reciprocating piston engine device 12b.

[0089] Reference symbol

[0090] 10 reciprocating piston engine

[0091] 12 Reciprocating piston machine device

[0092] 14 pressure housing

[0093] 16 runners

[0094] 18 Movement axis

[0095] 20 pistons

[0096] 24 Stator unit

[0097] 26 Valve unit

[0098] 28 storage units

[0099] 30 rotation element

[0100] 32 rotation axis

[0101] 34 Pressure housing wall

[0102] 36 additional rotation element

[0103] 38 additional rotation axes

[0104] 40 permanent magnet

[0105] 42 permanent magnet

[0106] 44 permanent magnet

[0107] 46 permanent magnet

[0108] 48 permanent magnet

[0109] 50 systems

[0110] 54 coil

[0111] 60 reset unit

[0112] 62 elastic element

[0113] 64 Coating

[0114] 66 Outside piston

[0115] 68 Piston face

[0116] 70 non-contact seal

[0117] 74 Labyrinth seal

[0118] 76 first piston element second piston element third piston element further piston guide element guide element housing unit further stator unit

[0119] Fan additional fan

[0120] Workspace additional workspace

[0121] Valve opening exhaust valve further valve opening inlet valve

[0122] Tongue valve connection connection additional coil additional connection additional connection additional flow direction

[0123] Level further valve unit further guide element

[0124] Opening Holding element Further first piston element Further second piston element Further third piston element Vertical direction 188 Horizontal direction

[0125] 190 additional pressure housing wall

[0126] 192 Inside pressure housing

Claims

Claims 1. Reciprocating piston machine device (12a-b) with a gas-tight pressure housing (14a), with at least one rotor (16a-b) which is mounted within the pressure housing (14a) for translational movement along a movement axis (18a-b), and with at least one piston (20a-b) arranged within the pressure housing (14a) and which is in operative connection with the rotor (16a-b), characterized in that the piston (20a-b) has a polygonal cross-section.

2. Reciprocating piston machine device (12a-b) according to claim 1, characterized by a bearing unit (28a-b) with at least one rotation element (30a-b) for the linearly movable mounting of the rotor (16a-b) relative to a pressure housing wall (34a) of the pressure housing (14a), wherein the rotation element (30a-b) has a rotation axis (32a-b) perpendicular to the movement axis (18a-b) of the rotor (16a-b).

3. Reciprocating piston machine device (12a) according to claim 2, characterized in that the pressure housing (14a) has at least one guide element (88a) for guiding at least the rotation element (30a).

4. Reciprocating piston machine device (12b) according to claim 2 or 3, characterized in that the rotary element (30b) directly contacts at least the pressure housing wall (34a) of the pressure housing (14a).

5. Reciprocating piston machine device (12b) according to one of claims 2 to 4, characterized in that the bearing unit (28b) has at least one further rotation element (36b) with a further rotation axis (38b) which is aligned perpendicular to the rotation axis (32b) of the rotation element (30b).

6. Reciprocating piston machine device (12a-b) according to one of claims 2 to 5, characterized in that the bearing unit (28a-b) is mounted on the rotor (16a-b).

7. Reciprocating piston machine device (12a-b) according to one of the preceding claims, characterized in that the piston (20a-b) and the rotor (16a-b) are formed in one piece, in particular in one part.

8. Reciprocating piston machine device (12a-b) according to one of the preceding claims, characterized by at least one coating (64a) which is arranged on an inner side (192a) of the pressure housing (14a) and / or on an outer side (66a) of the piston (20a-b) to compensate for manufacturing tolerances.

9. Reciprocating piston machine device (12a-b) according to one of the preceding claims, characterized by at least one contactless seal (70a-b) for sealing at least one intermediate space between the piston (20a-b) and the pressure housing (14a).

10. Reciprocating piston machine device (12a-b) according to claim 9, characterized in that the non-contact seal (70a-b) is a labyrinth seal (74a-b). 11 . Reciprocating piston machine device (12b) according to one of the preceding claims, characterized in that the piston (20b) has a first piston element (76b) and at least one second piston element (78b) which are movable relative to one another.

12. Reciprocating piston machine device (12b) according to claim 11, characterized in that the second piston element (78b) is provided to move the first piston element (76b) perpendicular to the movement axis (18b) during a movement along the movement axis (18b).

13. Reciprocating piston engine device (12a-b) according to one of the preceding claims, characterized by a return unit (60a) with at least one elastic element (62a-b) which is connected to the piston (20a-b).

14. Reciprocating piston engine device (12a-b) according to one of the preceding claims Claims, characterized by at least one further piston (82a-b) arranged within the pressure housing (14a), which is operatively connected to the rotor (16a-b) on a side opposite the piston (20a-b).

15. Reciprocating piston engine (10a) with at least one reciprocating piston engine device (12a-b) according to one of the preceding claims.

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