Rotary piston fluid machine

Abstract

The invention relates to a fluid-energy machine (3), with an external rotor (5) which is rotatably mounted about an external rotor rotational axis (6), and with an internal rotor (8) which is rotatably mounted about an internal rotor rotational axis (9) which is different from the external rotor rotational axis (6), which internal rotor (8) is arranged in a rotor receptacle of the external rotor (5) and whose outer circumferential surface (17) bears sealingly against an inner circumferential surface (16) of the external rotor (5) at a sealing point (19), which inner circumferential surface (16) delimits the rotor receptacle, wherein there is a fluid space (18) between the outer circumferential surface (17) of the internal rotor (8) and the inner circumferential surface (16) of the external rotor (5), which fluid space (16) is divided into a first fluid chamber (21) and a second fluid chamber (22) by a piston component (20) which is mounted moveably on the internal rotor (8) and sealingly abutting the external rotor (5) or mounted moveably on the external rotor (5) and sealingly abutting the internal rotor (8). According to the invention, the external rotor (5) and the internal rotor (8) are drivingly synchronously coupled to one another such that an angular speed of the external rotor (5) and an angular speed of the internal rotor (8) are continuously the same. The invention also relates to a fluid-energy machine arrangement (1), a drive unit and a method for operating a fluid-energy machine (2, 3).

Description

[0001] DESCRIPTION

[0002] Fluid energy machine, fluid energy machine arrangement, drive device and method for operating a fluid energy machine

[0003] The invention relates to a fluid energy machine with an outer rotor rotatably mounted about an outer rotor axis of rotation and an inner rotor rotatably mounted about an inner rotor axis of rotation different from the outer rotor axis of rotation. The inner rotor is arranged in a rotor receptacle of the outer rotor and its outer circumferential surface abuts, at a sealing point, an inner circumferential surface of the outer rotor, which defines the rotor receptacle. A fluid chamber is located between the outer circumferential surface of the inner rotor and the inner circumferential surface of the outer rotor. This fluid chamber is divided into a first fluid chamber and a second fluid chamber by a piston component that is movably mounted on the inner rotor and abuts, or is movably mounted on the outer rotor and abuts, the inner rotor. The invention further relates to a fluid energy machine arrangement, a drive device, and a method for operating a fluid energy machine.

[0004] For example, the prior art document WO 2021 / 255224 Al describes a fluid energy machine with an outer rotor rotatably mounted about an outer rotor axis and an inner rotor rotatably mounted about an inner rotor axis different from the outer rotor axis. The inner rotor is arranged in a rotor receptacle of the inner rotor and its outer circumferential surface seals against an inner circumferential surface of the outer rotor, which defines the rotor receptacle. A fluid space exists between the outer circumferential surface of the inner rotor and the inner circumferential surface of the outer rotor. This fluid space is divided into a first fluid chamber and a second fluid chamber by a connecting lever that is rotatably mounted on the inner rotor about a first connecting lever axis and on the outer rotor about a second connecting lever axis.

[0005] It is provided that the outer rotor is arranged in a fluid collection chamber formed in the machine housing, into which at least one outer rotor fluid passage opening of the outer rotor, formed in the outer rotor and opening into the second fluid chamber, opens, wherein the outer rotor has side walls that limit the fluid space in the axial direction with respect to the outer rotor axis of rotation on opposite sides, between which the inner rotor engages and against which the inner rotor bears continuously in a sealing manner in the circumferential direction, wherein the side walls are rigidly connected to an outer rotor ring forming the inner circumferential surface of the outer rotor, or wherein the inner rotor has side walls that limit the fluid space in the axial direction with respect to the inner rotor axis of rotation on opposite sides, between which the outer rotor engages and against which the outer rotor bears continuously in a sealing manner in the circumferential direction.wherein the side walls are rigidly connected to an inner rotor ring forming the outer circumferential surface of the inner rotor.

[0006] Furthermore, US patent 10,309,222 B2 discloses energy systems and, in particular, rotating components that enable shaft work, propulsion work, power generation, jet propulsion, and / or thermodynamic systems relating to aerothermodynamic thrust and shaft power, exhaust heat recovery shaft power, ventilation, cooling, heat, pressure, and / or vacuum generating devices. Some embodiments involve vane assemblies for eccentrically mounted rotating compressors and expanders that can be used either together or in conjunction with other mechanical, electrical, hydraulic, and / or pneumatic machines. Some implementations further relate to mechanical devices for fluid energy recovery designed to power gas turbine engines, internal combustion engines, furnaces, rotary kilns, cooling and cooling rotary components, and / or expansion machines.

[0007] Furthermore, publication GB 192 938 A reveals a rotary pump and publication JP 2014-040831 A reveals a compressor.

[0008] The object of the invention is to propose a fluid energy machine which has advantages over known fluid energy machines, in particular operates very efficiently and has low wear, so that it has a high fatigue strength.

[0009] This is achieved according to the invention with a fluid energy machine having the features of claim 1. It is provided that the outer rotor and inner rotor are coupled to each other in a synchronous drive system, so that the angular velocity of the outer rotor and the angular velocity of the inner rotor are consistently the same.

[0010] Advantageous embodiments with expedient further developments of the invention are specified in the dependent claims. It should be noted that the exemplary embodiments described in the description are not limiting; rather, any variations of the features disclosed in the description, the claims, and the figures are possible.

[0011] A fluid energy machine is fundamentally designed to supply energy to or extract energy from a fluid. It can be configured as either a working machine or a power machine. When configured as a working machine, it primarily converts mechanical energy into thermal energy and / or the fluid's internal energy. Examples of such working machines include pumps and compressors. Conversely, when configured as a power machine, it extracts thermal and / or internal energy from the fluid and converts it into mechanical energy. More generally, a power machine can be used to convert chemical and / or thermal energy into mechanical energy. An example of a power machine is a motor.In the case of its design as a working machine, the fluid energy machine can also be called a fluid working machine, and in the case of its design as a power machine, it can be called a fluid power machine.

[0012] The fluid energy machine is preferably part of a fluid energy machine assembly, but it can, of course, also exist separately. The fluid energy machine assembly comprises one or more fluid energy machines, each as described in this document. The fluid energy machine has as its essential components the outer rotor and the inner rotor. The outer rotor is rotatably mounted about its axis of rotation, namely relative to a machine housing of the fluid energy machine and / or on the machine housing. It is particularly preferred that the outer rotor is rotatably mounted directly on the machine housing. The inner rotor is rotatably mounted about its axis of rotation, particularly also relative to the machine housing and / or on the machine housing.

[0013] Preferably, the inner rotor is also rotatably mounted directly on the machine housing. For example, the inner rotor sits on a machine shaft of the fluid power machine, which is also connected to the outer rotor, preferably via the inner rotor. In particular, it is thus provided that the inner rotor is directly coupled to the machine shaft for drive purposes. The outer rotor, on the other hand, is only indirectly connected to the machine shaft for drive purposes, namely via the inner rotor. In one variant, this can also be reversed. The axis of rotation of the inner rotor is different from the axis of rotation of the outer rotor. This ultimately means that the outer and inner rotors are mounted eccentrically to each other. Accordingly, the axis of rotation of the outer rotor and the axis of rotation of the inner rotor are arranged parallel to and spaced apart from each other.

[0014] The inner rotor is arranged within the outer rotor. The outer rotor is, for example, ring-shaped and has a rotor housing in which the inner rotor is located. The rotor housing is bounded radially outwards by the inner circumferential surface of the outer rotor. The outer and inner rotors together define the fluid space. This space is therefore bounded radially outwards by the outer rotor or its inner circumferential surface, and radially inwards by the inner rotor or its outer circumferential surface. Whenever axial, radial, or tangential directions are mentioned in this description, they always refer to the axis of rotation of the outer rotor and / or the axis of rotation of the inner rotor, unless otherwise indicated.

[0015] The inner rotor, or rather its outer circumferential surface, seals against the inner circumferential surface of the outer rotor at the sealing point. It is designed such that, in the circumferential direction, it only contacts the outer rotor at the sealing point and is spaced away from the outer rotor, or rather its inner circumferential surface, away from the sealing point, in particular spaced throughout. Preferably, the rotor housing has a round cross-section, i.e., it is a right circular cylinder. This means that the inner circumferential surface of the outer rotor lies on a lateral surface of such a right circular cylinder. The inner rotor also has a round cross-section and is correspondingly cylindrical. The outer circumferential surface of the inner rotor therefore also lies on a lateral surface of a right circular cylinder.

[0016] The fluid chamber is divided circumferentially by the piston component into two fluid chambers: the first and the second. Each fluid chamber extends circumferentially from the sealing point to the piston component, with the fluid chambers located on opposite sides of the sealing point and the piston component, respectively. The piston component is thus positioned within the fluid chamber and, together with the sealing point, divides it into two fluid-technically separate fluid chambers: the first and the second.The outer rotor, the inner rotor and the piston component are arranged and designed in such a way that the two fluid chambers are fluidically separated from each other, so that a fluid present in one of the fluid chambers cannot flow directly in the circumferential direction or in the tangential direction over the sealing point or the piston component into the other of the fluid chambers, apart from a technically unavoidable leakage.

[0017] The piston component is mounted on one of the rotors in a way that allows it to move freely, and it seals against the other rotor. For example, the piston component can be mounted on the inner rotor and seal against the outer rotor. Alternatively, the piston component can be mounted on the outer rotor in a way that allows it to move freely, and it seals against the inner rotor. The mounting is fluid-tight in each case, so that ultimately the piston component is mounted on one rotor in a fluid-tight manner and seals against the other rotor. The piston component is mounted in a way that allows it to move freely, particularly in the radial direction. For example, it can be mounted to rotate around a piston axis or to move linearly.Due to the eccentric mounting of the outer rotor and the inner rotor, the piston component is deflected at least in the radial direction during a rotational movement of the rotors, for example at least temporarily in the radial direction inwards and / or at least temporarily in the radial direction outwards.

[0018] Preferably, the piston component is rigid, in particular made of metal or plastic. Additionally, the piston component may have a seal through which it rests against one of the rotors. This achieves a high degree of sealing, resulting in a particularly high efficiency of the fluid power machine. However, the piston component may also be flexible, for example, made of an elastomer. In this case, the piston component may be attached to both the outer and inner rotors. The term "piston component" is understood to mean a component that is movable and divides the fluid space or delimits each of the fluid chambers, so that the fluid chambers each have a variable volume.

[0019] It is important that the outer and inner rotors are not connected via the piston component, or at most only by frictional engagement between the piston component and the rotor against which it rests. Thus, no rigid connection is established between the outer and inner rotors via the piston component; rather, the outer and inner rotors could move freely relative to each other in a tangential direction by displacing the piston component, unless they were coupled to each other separately from the piston component. In any case, a drive connection between the outer and inner rotors via the piston component is either not established or is only of minor significance. According to the invention, the outer and inner rotors are coupled to each other in a synchronous drive configuration.This means that they are connected to each other independently of the piston component, or rather, separately from the piston component. The coupling is designed such that the angular velocity of the outer rotor and the angular velocity of the inner rotor are consistently the same. In other words, the outer rotor and the inner rotor exhibit identical angular velocities throughout operation of the fluid power machine. Preferably, the outer rotor and the inner rotor are rigidly connected to each other, taking into account usual and / or unavoidable tolerances.

[0020] When one of the rotors rotates, for example, the outer or inner rotor, the other rotor also rotates, particularly the inner or outer rotor. Due to the synchronous rotation of the outer and inner rotors and the corresponding absence of imbalance, the fluid power machine experiences exceptionally low wear, especially at the sealing point, resulting in high fatigue strength. This leads to a very low lubricant requirement, or the fluid power machine can even be operated entirely without lubricant. Accordingly, it is also suitable for applications where lubricants are prohibited, particularly in the medical field. The absence of imbalance also results in very high efficiency.

[0021] A further development of the invention provides that the outer rotor and the inner rotor are arranged between the fluid chamber on opposite sides bounding it in the axial direction with respect to the outer rotor's axis of rotation and / or the inner rotor's axis of rotation, wherein the outer rotor or the inner rotor is rigidly connected to the side walls and the other rotor abuts the side walls in a sealing manner. Thus, in the axial direction, the fluid chamber is bounded by the side walls, which are arranged on opposite sides of the fluid chamber. To seal the first fluid chamber and the second fluid chamber from each other, the side walls are tightly connected to one of the rotors and abut the other in a sealing manner. For example, the side walls are tightly connected to the outer rotor and abut the inner rotor in a sealing manner, but are movable relative to it.Alternatively, the side walls could be tightly connected to the inner rotor and abut the outer rotor in a sealing, yet movable, manner. The side walls could be integrally formed with one of the rotors, for example, the outer or the inner rotor, and / or made of a single material.

[0022] If the side walls are tightly connected to the outer rotor, the inner rotor engages between the side walls extending from the outer rotor, namely in a radial direction from the inside. It also seals against both side walls continuously in the circumferential direction. At the same time, however, the inner rotor is movable relative to the side walls, particularly in the radial direction. If, on the other hand, the side walls are tightly connected to the inner rotor, the outer rotor engages between the side walls, namely in a radial direction from the outside. Furthermore, the outer rotor seals against both side walls continuously in the circumferential direction. At the same time, the outer rotor is movable relative to the side walls, also particularly in the radial direction.

[0023] A further development of the invention provides that the drive coupling of the outer and inner rotors is implemented by means of a gear drive or a traction drive, or that coupling projections extend from at least one of the side walls, in particular from both side walls, which engage positively in coupling recesses of the outer or inner rotor. In any case, the coupling between the outer and inner rotors is essentially rigid, so that the outer and inner rotors can only be rotated together. For example, the coupling between the outer and inner rotors can be achieved indirectly via the gear drive or the traction drive. Alternatively, the rotors can be directly coupled using the coupling projections and the coupling recesses. The gear drive is, for example, a spur gear drive with a gear ratio of 1:1.Alternatively, a traction drive is used, which can be designed, for example, as a chain drive or belt drive. Traction drives also preferably have a gear ratio of 1:1.

[0024] Preferably, however, the rotors are directly connected to each other by a positive locking mechanism. For this purpose, they have coupling projections and coupling recesses. For positive locking, the coupling projections extend from one of the rotors and engage positively in the coupling recesses located on or in the other rotor. For example, the coupling projections are rigidly connected to the outer rotor, while the coupling recesses are located in the inner rotor. Conversely, it can also be provided that the coupling projections extend from the inner rotor and engage positively in the coupling recesses located in the outer rotor.

[0025] Preferably, the coupling projections extend in the axial direction, thus each having a longitudinal center axis parallel to one of the axes of rotation. Alternatively, the coupling projections can also extend in the radial direction, but the axial orientation results in less wear. In any case, the outer and inner rotors are connected in such a way that they always rotate synchronously, i.e., they have the same angular velocities. Consequently, no imbalance caused by relative movement of the rotors relative to each other in the circumferential direction occurs. This reduces wear and also achieves excellent efficiency.Preferably, rolling bearings are arranged on the coupling projections, or the coupling projections are formed by rolling bearings, such that the inner rings of the rolling bearings are firmly connected to the respective rotor and the outer rings of the rolling bearings roll on guide walls that define the coupling recesses. This results in particularly low-wear operation with reliable coupling.

[0026] A further development of the invention provides that the coupling recesses have a non-circular cross-section and are composed of round core recesses and compensation recesses extending radially outwards with respect to the outer rotor axis of rotation and / or the inner rotor axis of rotation. In cross-section, the coupling recesses are non-circular, i.e., they have a shape that deviates from a circular form. Each recess has a round core recess to which one or more compensation recesses extend radially outwards. For example, each coupling recess has two compensation recesses arranged on opposite sides of the respective core recess. In this case, the coupling recesses have an approximately lemon-shaped form. The non-circular coupling recesses ensure reliable and low-wear coupling of the rotors.

[0027] A further development of the invention provides that the compensation recesses are arranged such that a first coupling projection is spaced apart from a first guide wall that defines the outermost boundary of the first coupling recess in a radial direction, while a second coupling projection abuts a second guide wall that also defines the outermost boundary of the second coupling recess in a radial direction. The coupling projections and the coupling recesses are arranged and configured such that the coupling projections abut the guide walls defining the coupling recesses away from the compensation recesses, but not within the area of ​​the compensation recesses.In other words, viewed radially, each coupling projection rests against a portion of the corresponding guide wall that defines the core recess of the respective coupling recess and is spaced apart from a portion of the guide wall that defines the compensation recess. In the area of ​​the compensation recesses, the respective coupling projection is thus decoupled from the rotor that has the respective coupling recesses.

[0028] The compensating recesses serve to prevent over-constraint of the positive-locking connection between the rotors. The coupling projections and the coupling recesses are arranged and oriented such that at least one of the coupling projections is always in contact with the guide walls that define the coupling recesses. However, at least temporarily, at least one other coupling projection can be spaced away from the guide walls. For example, a rotational angular range within which several, in particular all, of the coupling projections are in contact with the guide walls is defined. This is the case, for example, within a rotational angular range or within several spaced-apart rotational angular ranges over one revolution of the rotors. The rotational angular range, or each of the several rotational angular ranges, comprises, for example, at most 30°, at most 15°, but preferably at most 10°, at most 5°, or at most 2.5°.Preferably, particularly to space at least one of the coupling projections from the respective guide wall, the compensation recesses of different coupling recesses are located at different circumferential positions, i.e., they have different angular positions with respect to the longitudinal center axes of the coupling recesses. Such a design enables a particularly reliable and low-wear drive-related coupling of the rotors.

[0029] A further development of the invention provides that an internal rotor fluid channel is provided in the inner rotor, opening into the fluid chamber and containing a valve designed and configured for adjusting the flow cross-section of the internal rotor fluid channel, wherein the valve is a control valve. The internal rotor fluid channel preferably extends radially within the inner rotor, and in particular precisely in the radial direction. It opens into the fluid chamber on one side and is fluidically connected to a fluid port of the fluid power machine on the other. Fluid can thus be exchanged between the fluid port and the fluid chamber, or vice versa, via the internal rotor fluid channel.

[0030] The valve is located within the inner rotor fluid channel. This valve is adjustable and thus serves to regulate the flow cross-section of the inner rotor fluid channel. Different valve settings result in different flow cross-sections, or rather, different flow cross-sectional areas, within the inner rotor fluid channel. Preferably, in the first valve setting, the flow connection through the inner rotor fluid channel is completely interrupted, resulting in a flow cross-sectional area of ​​zero. In the second setting, the fluid connection through the inner rotor fluid channel is open, and the flow cross-sectional area is therefore greater than zero. The control valve enables flexible operation of the fluid power machine.

[0031] A further development of the invention provides that an actuating element of the control valve interacts with a cam track of a cam ring to adjust the flow cross-section, that the valve is a check valve, or that a valve body of the control valve is rotatably mounted about a valve body axis of rotation in the inner rotor and is drive-connected to at least one of the coupling projections. In a first embodiment of the valve, it is designed as a control valve. A control valve is understood to be, in particular, a valve that is adjustable by means of an external actuating force, i.e., not automatically. Specifically, the valve has the actuating element that interacts with the cam track of the cam ring, in particular bearing against the cam track. Depending on a deflection of the cam track, the actuating element is displaced, or a specific position of the actuating element, and thus a specific setting of the valve, is established.The cam track is designed such that it exhibits different deflections in the circumferential direction. Furthermore, it is stationary relative to the machine housing, at least temporarily; that is, it does not rotate with the inner rotor.

[0032] The actuating element, however, rotates together with the inner rotor and is thus connected to it circumferentially. Depending on the rotational angle of the inner rotor relative to the cam ring, the actuating element rests at a specific circumferential position of the cam ring or cam track, at which a specific deflection occurs. Accordingly, the setting of the control valve depends on the rotational angle of the inner rotor relative to the cam ring. The cam track exhibits different deflections for different rotational angles of the inner rotor relative to the cam ring, resulting in different valve settings. The control valve is used particularly when the fluid power machine is designed as a motor.

[0033] Alternatively, the valve can be configured as a check valve. A check valve is defined as a valve that allows fluid flow in one direction and prevents flow in a second direction opposite to the first. For example, the check valve allows fluid to flow through the internal rotor fluid channel from the fluid chamber towards the fluid connection, but prevents flow in the opposite direction, or vice versa. The check valve is preferably used in a configuration of the fluid power machine as a compressor. In any case, the aforementioned advantages are achieved.

[0034] According to a third variant, the valve, or control valve, has a rotatably mounted valve body. The valve body is arranged in the inner rotor and rotatably mounted therein, namely about the valve body's axis of rotation. The valve body's axis of rotation differs from the inner rotor's axis of rotation; in particular, it is parallel to and spaced apart from it. Additionally, the valve body is connected to one of the coupling projections for actuation purposes. Specifically, the coupling projection is eccentrically positioned on the valve body with respect to the valve body's axis of rotation; for example, it projects axially beyond the valve body or a base part of the valve body with respect to the valve body's axis of rotation.

[0035] Due to its rotatable mounting in the inner rotor and its coupling to one of the coupling projections, the valve body is drive-wise connected to both the inner and outer rotors. The valve body is mounted and connected to the coupling projection in such a way that a rotational movement of the outer and inner rotors relative to each other causes a rotational movement of the valve body about the axis of rotation of the valve body. The valve body thus serves not only to adjust the flow cross-section of the inner rotor fluid channel, but also to drive the outer and inner rotors together via the valve body. Preferably, the valve body is rotatably mounted in the inner rotor by means of a rolling bearing, and the coupling projection is connected to the outer rotor via another rolling bearing.This effectively prevents wear and tear, resulting in maintenance-free or at least low-maintenance operation of the fluid energy machines.

[0036] It should be noted that the valve can also exist independently of the synchronous coupling of the rotors via the drive system. Accordingly, a fluid energy machine with the features of the preamble of claim 1 is also to be described, which is characterized in that an inner rotor fluid channel is provided in the inner rotor, which opens into the fluid chamber and in which a valve designed and configured for adjusting the flow cross-section of the inner rotor fluid channel is arranged, wherein the valve is a control valve and an actuating element of the control valve for adjusting the flow cross-section interacts with a cam track of a cam ring, wherein the valve is a check valve or wherein a valve body of the control valve is rotatably mounted about a valve body axis of rotation in the inner rotor and is drive-connected to at least one of the coupling projections.Regarding further advantageous embodiments of such a fluid energy machine, reference is made in its entirety to the description.

[0037] A further development of the invention provides that the cam ring is adjustable for setting the flow cross-section. The cam ring is rotatably mounted, i.e., displaceable in the circumferential direction, particularly with respect to the machine housing and / or on the machine housing. The rotational angle of the inner rotor relative to the cam ring depends on the rotational angle of the cam ring relative to the machine housing. By adjusting the cam ring, the operating cycle of the fluid power machine can therefore be influenced. For example, a variable valve control can be implemented using the cam ring. It can be provided that the cam ring is manually displaceable. For this purpose, the cam ring is connected to an adjustment device that temporarily allows the cam ring to be adjusted relative to the machine housing and temporarily locks the cam ring in place relative to the machine housing.The adjustment device preferably includes a control element, for example a lever, which is designed and intended for manual adjustment by a user.

[0038] The cam ring can also be mechanically displaced by means of a drive. In this case, the drive is designed and configured to change the rotational angle of the cam ring relative to the machine housing. It may be possible to adjust the rotational angle only periodically, for example, according to a user's instructions. However, it may also be possible to adjust the rotational angle periodically during a rotor revolution, i.e., to shift it temporarily in one direction and temporarily in the other during a single revolution. Adjusting the angle for each of several revolutions is particularly preferred, especially during the entire operation of the fluid power machine. The described procedure achieves a variable expansion ratio over the course of the rotor revolutions.Overall, the adjustable cam ring enables particularly flexible operation of the fluid energy machine with high efficiency.

[0039] A further development of the invention provides that the cam ring is part of several cam rings, each of which has a cam track that interacts with the actuating element or with several actuating elements of the control valve to adjust the flow cross-section of the control valve. The cam rings are adjustable relative to each other, in particular rotatable relative to each other in the circumferential direction. Only one of the cam rings can be rotatably mounted, while the other is stationary, particularly with respect to the machine housing. However, both cam rings can also be rotatably mounted, preferably on the machine housing. For example, it is provided that one of the cam rings can be adjusted mechanically by means of an actuator, while the other of the cam rings can only be adjusted manually.It can also be provided that each cam ring is connected to one or more actuators in terms of drive technology, so that they can be moved independently of each other by machine.

[0040] Each of the cam rings interacts with the control valve at least temporarily, namely via the actuating element. This means that, with each revolution of the inner or outer rotor, the actuating element interacts with or bears against the cam track of a first cam ring and, at the same time, with the cam track of a second cam ring. For example, the cam rings or their cam tracks are designed such that each cam ring actuates the valve at least once during each revolution of the inner or outer rotor, in particular opening and / or closing it. Preferably, the cam rings interact with the valve to open and close it once during each revolution. In particular, one of the cam rings is configured as an opening cam ring and another as a closing cam ring.The opening cam ring opens the valve or exerts a force on the valve directed towards opening, in particular for letting in or letting out the fluid; the closing cam ring closes it or exerts a force on the valve directed towards closing.

[0041] This can be implemented, for example, by having the actuating element, viewed radially, overlap with each of the cam rings. Depending on which cam ring projects further axially, the actuating element is displaced axially by that cam ring. Alternatively, the cam rings can be arranged axially on opposite sides of the valve, and the valve can have multiple actuating elements, each designed and arranged to interact with one of the cam rings. Preferably, the cam rings are arranged around the same longitudinal center axis and have their cam tracks at the same positions radially. By means of the multiple cam rings, which interact with the valve via the actuating element(s) to displace it, a variable expansion ratio of the fluid power machine is implemented in a structurally simple manner.For example, the expansion ratio is continuously adjustable, especially between expansion ratios of 1 : 12 to 1 :2.

[0042] During operation of the fluid power machine, preferably only one of the cam rings is adjusted, while the other remains stationary. This cam ring is adjusted, for example, only when the fluid power machine is not in operation, particularly when it is at a standstill. Specifically, it is provided that the adjustable cam ring, or the cam ring adjusted during operation, closes the valve, i.e., it is a closing cam ring. The cam ring that is not adjustable, or only manually adjustable, or that is adjusted only when not in operation, is an opening cam ring, i.e., it opens the valve. The opening cam ring determines, in particular, the opening point of the valve or a rotational angle of the rotors at which the valve opens. The closing cam ring, on the other hand, determines the closing point of the valve or a rotational angle of the rotors at which the valve closes.

[0043] A further development of the invention provides that the rotatable mounting of the valve body is implemented by means of a bearing journal which projects axially on opposite sides of a base body of the valve body with respect to the valve body's axis of rotation, and / or that a drive element is arranged on the valve body eccentrically to the valve body's axis of rotation, on which at least one coupling projection is arranged. The valve body thus comprises the base body and the bearing journal. The base body is designed and configured to adjust the flow cross-section of the inner rotor fluid channel, in particular by interacting with an inner wall of the inner rotor that delimits the inner rotor fluid channel. The bearing journal, on the other hand, serves to rotatably mount the valve body, more precisely the base body of the valve body, about the valve body's axis of rotation.For this purpose, the bearing journal projects axially beyond the base body, at least on one side, but preferably on both sides. Adjacent to the valve body, the bearing journal engages in a bearing recess formed in the inner rotor. Preferably, the bearing journal is rotatably mounted on the inner rotor by means of the aforementioned rolling bearing or several rolling bearings. This allows for a particularly compact design of the valve body.

[0044] Additionally or alternatively, a drive component is arranged on the valve body. This drive component serves to establish the drive connection between the valve body and the outer rotor. Accordingly, the drive component features a coupling projection. For example, the drive component is designed as a drive shaft that extends at least partially through the valve body, but preferably projects beyond the valve body or its base body on both sides. Particularly preferably, the drive component has coupling projections on both sides of the base body, so that the drive component is connected to the outer rotor on opposite sides of the base body.The drive component or drive axis is arranged eccentrically to the valve body's axis of rotation, so that the rotational movement of the outer and inner rotors relative to each other causes the rotational movement of the valve body or base body relative to the inner rotor. This described design of the fluid energy machine achieves a particularly effective connection between the outer and inner rotors, as well as precise adjustment of the flow cross-section of the inner rotor fluid channel.

[0045] A further development of the invention provides that the rotatably mounted valve body has a flow channel which, in the axial direction with respect to the valve body's axis of rotation, is bounded on opposite sides of the valve body's walls and, in the radial direction, partially extends through an outer circumferential surface of the valve body. The valve body, in particular the base body of the valve body, is preferably cylindrical in cross-section with respect to the valve body's axis of rotation, and more specifically circular cylindrical. The flow channel is formed in the valve body and extends through the valve body or the base body in the radial direction. In the axial direction, the flow channel is bounded by the walls of the valve body or the base body. The flow channel is thus located between the walls.

[0046] In a radial direction, the flow channel extends through the outer circumferential surface of the valve body, at least partially. In particular, the flow channel is designed to be open at the edges in cross-section. The flow channel extends radially through the outer circumferential surface on opposite sides, forming two outlet openings that are fluidically connected via the flow channel. The outlet openings may be designed to be closed at the edges, i.e., each enclosed by a continuous rim formed by the valve body. Alternatively, the outlet openings may be open at the edges and thus form part of a recess that extends through the outer circumferential surface from the first outlet opening to the second.This means that the flow channel is formed, at least in part, by the valve body and the inner rotor. Such a valve body design allows for a particularly large flow cross-section and correspondingly low flow losses.

[0047] A further development of the invention provides that a drive element, connected to the outer rotor, is arranged in the piston receiving chamber. The piston component is supported against this drive element in the radial direction with respect to either the outer rotor's axis of rotation or the inner rotor's axis of rotation. The drive element is preferably rigidly connected to the outer rotor and extends axially from it into the piston receiving chamber. The drive element is preferably arranged such that the outer and inner rotors are connected to each other exclusively away from the drive element; the drive element itself does not establish such a connection between the outer and inner rotors.Preferably, the driver is arranged in a tangential direction with respect to the inner rotor axis of rotation or the outer rotor axis of rotation, regardless of the position of the outer rotor and inner rotor relative to each other, at a distance from walls which define the piston receiving chamber in a tangential direction.

[0048] A rotational movement of the inner and outer rotors relative to each other causes the driver to shift within the piston receiving chamber, particularly in the radial and tangential directions. The driver is designed to propel the piston component, pushing it towards the outer rotor so that it seals against it. Since the driver is connected to the outer rotor, particularly rigidly, the piston component is clamped radially between the driver and an inner circumferential surface of the outer rotor. This ensures reliable compression of the piston component against the outer rotor or its inner circumferential surface. In a preferred embodiment, a spring element or a magnetic arrangement is positioned between the driver and the piston component.This allows for compensation of manufacturing tolerances and ensures a particularly uniform contact force between the piston component and the outer rotor. The spring element or the magnetic assembly pushes the piston component away from the driver, ensuring reliable contact with the outer rotor. The spring element and the magnetic assembly will be discussed in more detail below.

[0049] A further development of the invention provides that the piston component is supported in the tangential direction with respect to the outer rotor axis of rotation or the inner rotor axis of rotation against a linear guide projection of the inner rotor, in particular via a rolling bearing which engages in a guide recess of the outer rotor in at least one position of the outer and inner rotors relative to each other. In such a configuration of the fluid power machine, the piston component is mounted so as to be linearly displaceable, namely in particular by means of the linear guide projection. For this purpose, the piston component is supported against the linear guide projection so that it is mounted so as to be linearly displaceable in the radial direction. Preferably, the piston component rests against the linear guide projection via the rolling bearing. This enables low-friction displacement of the piston component and low-maintenance operation of the fluid power machine.

[0050] The linear guide projection is part of the inner rotor or at least attached to it. To support the piston component over a significant portion of its displacement, and in particular over its entire displacement, the linear guide projection extends to the outer rotor and engages in the guide recess formed in the outer rotor. The guide recess is dimensioned tangentially such that the linear guide projection is consistently spaced tangentially from the outer rotor, meaning it does not collide with any wall of the outer rotor that tangentially defines the guide recess. The linear guide projection preferably forms an extension of a wall of the piston receiving chamber. This design ensures highly reliable guidance of the piston component.A further development of the invention provides that the piston component is subjected to spring force or magnetic force in the direction of the inner or outer rotor by means of a spring element or a magnetic arrangement. It has already been explained that the piston component is movably mounted on one of the rotors and merely rests against the other rotor. This is achieved by means of the spring element or the magnetic arrangement, which pushes the piston component in the direction of the rotor against which it rests. Thus, if the piston component is movably mounted on the inner rotor, it is pushed by the spring element or the magnetic arrangement towards or against the outer rotor. In the case of mounting on the outer rotor, the spring element or the magnetic arrangement pushes the piston component towards or against the inner rotor.By means of the spring element and the spring force it generates, or the magnet arrangement and the magnetic force it generates, a reliable seal between the fluid chambers is achieved using the piston component. The magnet arrangement comprises at least one magnet, and preferably several magnets. The multiple magnets are preferably arranged such that they repel each other and the piston component is subjected to the magnetic force in the direction of the corresponding rotor. The magnet(s) of the magnet arrangement are preferably designed as permanent magnets.

[0051] A further development of the invention provides that the piston component is located, at least partially, in a piston receiving chamber formed in the inner rotor and extending through the outer circumferential surface of the inner rotor, in at least one position. The inner rotor fluid channel opens into the fluid space at a distance from the piston receiving chamber. The piston receiving chamber serves to receive the piston component, at least partially, in at least one position. The piston component is displaceably mounted on the inner rotor, in particular rotatably mounted on the inner rotor. At least temporarily, it is pushed by the outer rotor towards the inner rotor. In doing so, it is forced into the piston receiving chamber.

[0052] Preferably, the piston component is at least partially and completely located within the piston receiving chamber, so that it does not protrude beyond the outer circumferential surface of the inner ring. The piston receiving chamber extends through the outer circumferential surface of the inner rotor, forming an outlet opening. To design the fluid power machine with the smallest possible dead space, the inner rotor fluid channel opens into the fluid space at a distance from the piston receiving chamber. This means that an outlet opening through which the inner rotor fluid channel opens into the fluid space is located circumferentially away from the piston receiving chamber. This results in a particularly high efficiency of the fluid power machine.

[0053] A further development of the invention provides that seals, in particular elastic seals, are arranged on the outer rotor and / or the inner rotor, which abut the respective other rotor in a radially sealing manner. The seals serve to provide a particularly effective seal between the fluid combs at the sealing point. Preferably, the seals are arranged such that they overlap the outer rotor and / or the inner rotor in the axial direction by at least 80%, at least 90%, or completely, thus achieving a seal over a large portion of the axial extent of the rotors. The seals preferably consist of an elastic material, for example, polytetrafluoroethylene (PTFE), an elastomer, or rubber. However, they can also consist of another plastic or metal, provided it is elastic.Seals made of essentially rigid material can also be used, provided they are in contact with the other rotor, at least temporarily. The seals can be designed as hollow elements or as solid elements. They can be manufactured in the form of profile strips, particularly T-profile or L-profile strips, spring strips, or similar designs. The seals, especially elastic seals, can also be made in one piece from a single material and, for example, be formed by a coating on the respective rotor, such as an NBR coating (NBR: Nitrile Butadiene Rubber or Acrylonitrile Butadiene Rubber). In any case, a reliable seal between the fluid chambers is achieved, resulting in high efficiency of the fluid power machine. The seals effectively counteract thermally induced material expansion.

[0054] A further development of the invention provides that the seals are located in seal receptacles manufactured in the outer rotor and / or the inner rotor, wherein the seals project from the seal receptacles into the fluid chamber, at least temporarily, particularly in the uncompressed state, to form a sealing contact with the outer or inner rotor. The seal receptacles are manufactured as recesses in the respective rotor and consequently extend through the inner circumferential surface of the outer rotor or the outer circumferential surface of the inner rotor. The seals arranged in the seal receptacles extend at least temporarily beyond the seal receptacles, thus projecting radially beyond them. This ensures a sealing contact with the respective other rotor and thus a reliable sealing of the fluid chambers from one another, particularly in the area of ​​the sealing point.A particularly reliable seal is achieved with the elastic seals, which protrude from the seal receptacles in an uncompressed state and rest against the respective rotor.

[0055] A further development of the invention provides that the outer rotor is coupled in a rotationally fixed manner to a machine shaft of the fluid power machine, which is rotatably mounted about a shaft axis. The machine shaft serves to rotatably mount the outer rotor about the outer rotor axis. The fluid power machine provides drive torque via the machine shaft, or it is subjected to drive torque via the machine shaft. Preferably, the outer rotor is rigidly coupled to the machine shaft via the side walls. This results in a simpler design of the fluid power machine.

[0056] A further development of the invention provides that the outer rotor is arranged in a fluid collection chamber formed in the machine housing, into which at least one outer rotor fluid channel, formed in the outer rotor and opening into the second fluid chamber, opens. The fluid collection chamber serves to supply fluid to the fluid chamber or to remove fluid from it. Preferably, an outer rotor fluid passage opening is formed in the outer rotor, through which the second fluid chamber is fluid-connected to the fluid collection chamber. The outer rotor is thus arranged in a fluid collection chamber formed in the machine housing, into which the outer rotor's fluid passage opening opens. The outer rotor fluid passage opening, which is fluid-connected to the second fluid chamber, rotates with the outer rotor during operation of the fluid power machine.Accordingly, it is not possible, for example, to attach a fluid line to the outer rotor that is in flow contact with the outer rotor fluid passage opening.

[0057] To still allow the fluid to be supplied to and extracted from the outer rotor fluid passage opening, the outer rotor is enclosed by the fluid collection chamber. This is done in such a way that the outer rotor fluid passage opening permanently opens into it, regardless of the outer rotor's rotational angle. Fluid can be introduced into or extracted from the second fluid chamber via the fluid collection chamber. The inclusion of the fluid collection chamber allows for a structurally simple, fluid-flow connection to the second fluid chamber. Furthermore, the fluid collection chamber serves to calm the fluid before it enters the second fluid chamber or is extracted from the fluid energy machine. This further improves the efficiency of the fluid energy machine.

[0058] The invention further relates to a fluid energy machine arrangement comprising several fluid energy machines coupled to a common machine shaft for drive purposes, in particular fluid energy machines according to one or more of the preceding claims, wherein each of the fluid energy machines has an outer rotor rotatably mounted about an outer rotor axis of rotation and an inner rotor rotatably mounted about an inner rotor axis of rotation different from the outer rotor axis of rotation, which is arranged in a rotor receptacle of the outer rotor and bears with an outer circumferential surface sealingly at a sealing point against an inner circumferential surface of the outer rotor which delimits the rotor receptacle, wherein a fluid space is present between the outer circumferential surface of the inner rotor and the inner circumferential surface of the outer rotor.The piston component is divided into a first fluid chamber and a second fluid chamber by a piston component that is movably mounted on the inner rotor and sealingly in contact with the outer rotor, or movably mounted on the outer rotor and sealingly in contact with the inner rotor. It is provided that the outer rotor and the inner rotor are coupled to each other in a synchronous drive system, so that the angular velocity of the outer rotor and the angular velocity of the inner rotor are constantly the same.

[0059] The advantages of such a design for the fluid energy machine arrangement or the fluid energy machines have already been mentioned. Both the fluid energy machine arrangement and the fluid energy machine can be further developed as explained in this description, and reference is made to these explanations in that regard.

[0060] The fluid power machine arrangement comprises several fluid power machines connected to each other via a common machine shaft. For example, the internal rotors of the fluid power machines are rigidly connected to the machine shaft. Specifically, the rotors of the fluid power machines are arranged circumferentially offset from one another, meaning that the sealing points and piston components of the fluid power machines are offset relative to each other in the circumferential direction. For example, the sealing points and piston components are arranged evenly distributed around the circumference. Thus, with two fluid power machines, the sealing points and piston components are offset by 180° relative to each other, with three fluid power machines by 120°, with four fluid power machines by 90°, and so on. This achieves a uniform distribution of the drive torque.

[0061] The invention further relates to a drive unit with a fluid circuit comprising a fluid pump, a fluid heater, and a fluid energy machine according to one or more of the preceding claims. Regarding the advantages of the drive unit and the possible advantageous embodiments of the drive unit and the fluid energy machine, reference is made to the corresponding descriptions. Optionally, the drive unit can include a fluid evaporator. The drive unit serves in particular to provide drive torque to the machine shaft of the fluid energy machine. For operating the fluid energy machine, the drive unit has the fluid circuit in which a fluid is circulated, at least temporarily, by means of the fluid pump. The fluid is heated by the fluid heater and then supplied to the fluid energy machine.

[0062] A fluid evaporator can be located between the fluid heater and the fluid power machine. The fluid evaporator serves to evaporate the heated fluid, so that the fluid is supplied to the fluid power machine at least partially, and preferably completely, as vapor. In the fluid power machine, the fluid expands again, whereby the enthalpy contained in the fluid is converted into kinetic energy of the machine shaft. The fluid is then condensed, for example, by means of a condenser in the fluid power machine or a separate condenser in the drive unit. Subsequently, the fluid is pumped back towards the fluid power machine and heated using the fluid heater.

[0063] The fluid is preferably heated by superheating, in which it is heated above its boiling point. Preferably, the pressure of the fluid is set such that it is liquid, preferably completely liquid, before reaching the fluid power machine. In this case, a fluid evaporator is not required. Accordingly, the fluid reaches the fluid power machine in a completely liquid state. Only within the fluid power machine does the fluid evaporate during expansion; thus, it passes through the fluid power machine at least partially as a liquid and partially as vapor. A particularly high efficiency is achieved with this approach. The invention further relates to a method for operating a fluid power machine, in particular a fluid power machine as described in this description.wherein the fluid energy machine has an outer rotor rotatably mounted about an outer rotor axis of rotation and an inner rotor rotatably mounted about an inner rotor axis of rotation different from the outer rotor axis of rotation, the inner rotor being arranged in a rotor receptacle of the outer rotor and having an outer circumferential surface sealingly in contact with an inner circumferential surface of the outer rotor which delimits the rotor receptacle, wherein a fluid space is located between the outer circumferential surface of the inner rotor and the inner circumferential surface of the outer rotor, which is divided into a first fluid chamber and a second fluid chamber by a piston component which is displaceably mounted on the inner rotor and sealingly in contact with the outer rotor or which is displaceably mounted on the outer rotor and sealingly in contact with the inner rotor, and wherein at least one of the fluid chambers is supplied with a fluid at least temporarily.

[0064] It is again provided that the outer and inner rotors are coupled to each other via a drive system, ensuring that the angular velocity of the outer rotor and the angular velocity of the inner rotor are consistently the same. The advantages of this design of the fluid energy machine and this approach have already been mentioned. Both the fluid energy machine and the method for operating it can be further developed as described in this document, and reference is made to these details.

[0065] During operation of the fluid power machine, it may be possible to supply one of the fluid chambers with fluid to drive the outer and inner rotors. For example, pressurized fluid is used. In this case, the fluid pressure is chosen such that it increases the volume of the fluid chamber and thus drives the rotors. However, it may also be possible for the fluid to be supplied to and drawn into the fluid power machine. In this case, fuel is preferably added to the fluid and used to increase the volume of the fluid chamber in order to increase the available mechanical energy. Any substance that causes expansion, i.e., an increase in volume, when combined with the fluid can serve as fuel.

[0066] A combustible fuel, i.e., a fuel, is used as the propellant. However, it is also possible to use a vaporizable fluid, preferably non-flammable, as the propellant. Water is particularly preferred as the propellant. In this case, the fluid is supplied to the fluid energy machine at a high temperature sufficient to vaporize the propellant. When the propellant is introduced into the fluid energy machine, it vaporizes due to the high temperature of the fluid present there, resulting in a significant increase in volume. This volume is converted into mechanical energy, which is used, at least in part, to drive the rotors. For example, it is possible to draw hot fluid into the fluid chamber. In this case, the fluid in the fluid chamber has a temperature higher than the boiling point of the propellant.The fuel is then introduced into the fluid chamber in such a way that it comes into contact with the hot fluid. For example, the fuel is introduced in the form of droplets, or more specifically, it is injected. This gives it a large surface area, allowing it to evaporate particularly quickly.

[0067] Preferably, the fluid is introduced into the fluid chamber until it reaches a specific volume. For example, the fluid is introduced until the volume of the fluid chamber reaches at least 10% and at most 30%, at most 25%, or at most 20% of its maximum volume. The maximum volume is understood to be the largest volume the fluid chamber exhibits over a complete operating cycle, i.e., the largest volume of the fluid chamber occurring during the operation of the fluid power machine. Subsequently, the introduction of the fluid is stopped, and the fuel is introduced into the fluid chamber. The fuel expands through interaction with the fluid, causing a pressure increase that increases the volume of the fluid chamber. This drives the rotors, enabling the fluid power machine to provide mechanical energy.

[0068] A further development of the invention provides that a superheated fluid in a liquid state is periodically introduced into one of the fluid chambers, particularly the first fluid chamber, such that it evaporates within the fluid chamber, increasing in volume. The fluid is thus superheated before being introduced into the fluid chamber so that it has a temperature above its boiling point. Simultaneously, the pressure of the fluid is adjusted so that it is liquid, preferably completely liquid. The superheated fluid is introduced into the fluid chamber in a liquid state, particularly completely liquid. There, it evaporates rapidly, resulting in a significant increase in volume. This provides mechanical energy, particularly at the machine shaft. The described procedure is carried out according to a thermodynamic triangular process.When the fluid is introduced into the first fluid chamber in a liquid state, flash evaporation or expansion evaporation occurs. The fluid energy machine described here is particularly well-suited for operation with fluids that are partially liquid and partially gaseous. Due to the machine's operating principle and motion sequence, the fluid present in the liquid state in the fluid chamber is propelled radially outwards and forced out of the chamber. Specifically, the fluid in the first fluid chamber is propelled outwards and collected there. The fluid in the second fluid chamber is also propelled outwards and thus forced out of the second chamber. Overall, this operating mode results in a significantly higher efficiency than other systems.

[0069] A further development of the invention provides that at least one of the following substances or a mixture containing at least one of the following substances is used as the fluid: water, ammonia, and alcohol. In principle, any substance can be used as the fluid, as long as it is liquid within the intended operating temperature range and can withstand superheating. Water, ammonia, and alcohol have proven to be particularly suitable. These substances can be used as the fluid in pure form, except for unavoidable impurities, or as components of the mixture. The fluid can therefore be, for example, a water-ammonia mixture or a water-alcohol mixture.

[0070] The features and combinations of features described in the description, in particular those described in the following figure description and / or shown in the figures, can be used not only in the combinations specified, but also in other combinations or individually, without departing from the scope of the invention, in particular the scope of the claims. Thus, embodiments that are not explicitly shown or explained in the description and / or the figures, but which emerge from or can be derived from the explained embodiments, particularly within the scope of the claims, are also to be considered as encompassed by the invention.

[0071] The invention is explained in more detail below with reference to the exemplary embodiments shown in the drawing, without limiting the invention. Figure 1 shows a schematic longitudinal sectional view of a fluid energy machine arrangement in a first embodiment with several fluid energy machines that are connected by a common machine shaft for drive purposes.

[0072] Figure 2 shows a schematic cross-sectional representation of one of the fluid energy machines.

[0073] Figure 3 shows a schematic representation of an area of ​​the fluid energy machine arrangement, in which valves of the fluid energy machines and several cam rings with multiple cam tracks are visible.

[0074] Figure 4 shows a schematic sectional view of the fluid energy machine arrangement in a second embodiment.

[0075] Figure 5 shows a schematic representation of the fluid energy machine arrangement in a third embodiment, wherein the rotors of the fluid energy machine arrangement are in a first position.

[0076] Figure 6 shows a schematic representation of the third embodiment of the fluid energy machine arrangement with rotors arranged in a second position.

[0077] Figure 7 shows a detailed sectional view of the fluid energy machine arrangement in its third embodiment, as well as

[0078] Figure 8 shows a further detailed sectional view of the fluid energy machine arrangement in the third embodiment.

[0079] Figure 1 shows a schematic longitudinal section of a first embodiment of a fluid energy machine arrangement 1. The fluid energy machine arrangement 1 comprises several fluid energy machines 2 and 3, which are connected by a common machine shaft 4. The fluid energy machines 2 and 3 are identical in construction, so the following discussion focuses primarily on fluid energy machine 2. The descriptions are always transferable to fluid energy machine 3. The fluid energy machine 2 has an outer rotor 5, which is rotatably mounted about an outer rotor axis 6, namely with respect to a machine housing 7 of the fluid energy machine arrangement 1. Furthermore, the fluid energy machine 2 has an inner rotor 8, which is rotatably mounted about an inner rotor axis 9, again with respect to the machine housing 7.The inner rotor axis of rotation 9 is different from the outer rotor axis of rotation 6, so that there is an eccentric bearing arrangement between the outer rotor 5 and the inner rotor 8.

[0080] The illustration shows an embodiment in which the inner rotor 5 is arranged directly on the machine shaft 4 and rotatably mounted on the machine housing 7 via the shaft. For this purpose, the machine shaft 4 is rotatably mounted in and on the machine housing 7 by means of several inner rotor bearings 10. The outer rotor 5 is supported by bearing ring projections 11, which extend from opposite sides of the outer rotor 5 and project in opposite directions axially with respect to the axes of rotation 6 and 9. The bearing ring projections 11 are located on side walls 12, which together with an outer rotor ring 13 form the outer rotor 5. In the embodiment shown here, the side walls 12 and the outer rotor ring 13 are made of multiple parts and rigidly attached to one another. Alternatively, a single-piece design of the side walls 12 and the outer rotor ring 13 made of a single material is, of course, possible.

[0081] The bearing ring projections 11 are in contact with bearing points 14 formed on the machine housing 7, for example, on annular projections of the machine housing 7. An outer rotor bearing 15 is arranged between each bearing ring projection 11 and the bearing points 14, by means of which the respective bearing ring projection 11, and thus the outer rotor 5, is rotatably mounted on and in the machine housing 7. In the illustrated embodiment, the inner rotor bearings 10 and the outer rotor bearings 15 are designed as rolling bearings. At a minimum, the inner rotor bearings 10 and the outer rotor bearings 15 are designed and configured to absorb radial forces. Preferably, they are also designed to absorb axial forces. In particular, the outer rotor bearings 15 counteract any displacement of the side walls 12 in the axial direction outwards, i.e., away from each other. This ensures very good sealing of the fluid power machine 2.

[0082] The inner rotor 8 engages radially from the inside between the side walls 12, so that it bears against both sides of the side walls 12 continuously and without interruption in the circumferential direction. This creates a fluid chamber 18 between an inner circumferential surface 16 of the outer rotor 5 and an outer circumferential surface 17 of the inner rotor 8. This chamber is bounded radially outwards by the inner circumferential surface 16, radially inwards by the outer circumferential surface 17, and axially on both sides by the side walls 12. The inner rotor 8 bears radially against the outer rotor 5 with its outer circumferential surface 17, specifically against its inner circumferential surface 16. This forms a sealing point 19, so that the fluid chamber 18 is interrupted in the circumferential direction. Additionally, a piston component 20 is located in the fluid chamber 18, which is radially displaceable inwards on the inner rotor 8 and radially rests against the outer rotor 5.Furthermore, the piston component 20 rests against the side walls 12 on both sides in the axial direction. The piston component 20 is permanently in contact with one of the side walls 12 and with a second side wall 12. This divides the fluid chamber 18 into two fluid chambers 21 and 22 between the sealing point 19 and the piston component 20, with fluid chamber 21 being shown here only as an example.

[0083] The outer rotor 5 is arranged in a fluid collection chamber 23, which is permanently connected to a fluid connection 24 of the fluid power machine 2 or a fluid connection 24 of the fluid power machine assembly 1. The fluid collection chamber 23 is bounded axially on both sides by housing side walls 25 of the machine housing 7, which are connected to each other via a shell section 26 of the machine housing 7. Radially outward, the fluid collection chamber 23 is bounded by the shell section 26, and radially inward by the outer rotor 5, in particular by the outer rotor ring 13. Fluid can be supplied to or extracted from the fluid power machines 2 and 3 via the fluid collection chamber 23. In particular, the fluid collection chamber 23 serves to collect and / or stabilize the fluid.

[0084] The machine shaft 4 is designed, at least in part, as a hollow shaft, thus having a cavity 27. Fluid can be supplied to or withdrawn from the fluid energy machines 2 and 3 via the cavity 27. The fluid energy machines 2 and 3 described here are considered power machines and convert internal energy and / or thermal energy contained in the fluid into mechanical energy, which they provide via the machine shaft 4. Alternatively, the fluid energy machines 2 and 3 can also be designed as working machines. In this case, the descriptions can be applied analogously.

[0085] An inner rotor fluid channel 28 is formed within the inner rotor 8. This channel opens into the fluid chamber 18, specifically into the first fluid chamber 21. It is also fluidically connected to the cavity 27, or rather, opens radially into it. A valve 29 is arranged within the inner rotor fluid channel 28, serving to adjust the flow cross-section of the inner rotor fluid channel 28. Here, the valve 29 is designed as a control valve and has a valve body 30 that is axially displaceable within a valve receptacle 31 of the inner rotor 8. The valve receptacle 31 preferably extends completely through the inner rotor 8 in the axial direction. It is bounded radially by a wall, which serves as a valve seat and interacts with the valve body 30 to adjust the flow cross-section.Depending on the position of the valve body 30 in the axial direction with respect to the inner rotor 8, a specific flow cross-section is present through the inner rotor fluid channel 28.

[0086] The valve body 30 is coupled or operatively connected via an actuating element 32 to a cam ring 33 and another cam ring 47. The cam ring 33 has a cam track 34, and the other cam ring 47 has a further cam track 48. The actuating element 32 bears against both cam tracks 34 and 48, at least temporarily, in a sliding manner. The cam ring 33 and the cam ring 47 each completely and continuously encircle the outer rotor axis of rotation 6. Viewed in the circumferential direction, the cam tracks 34 and 48 each have different axial projections, so that when the inner rotor 8 rotates, the actuating element 32 is displaced by the cam tracks 34 and 48 to different degrees in the axial direction. The valve body 30 is displaced accordingly in the axial direction. Preferably, the valve body 30 is forced towards the cam rings 33 and 47 by means of a spring 35.The spring 35 ensures that the actuating element 32 is always in contact with one of the cam tracks 34 and 48 or one of the cam rings 33 and 47.

[0087] With reference to the fluid energy machine arrangement 1 shown here, comprising fluid energy machines 2 and 3, it should be noted that the fluid energy machine arrangement 1 can, of course, include any number of fluid energy machines 2 and 3, i.e., for example, only a single fluid energy machine 2 or 3. If, as here, several fluid energy machines 2 and 3 are present, they are preferably arranged offset from each other in the circumferential direction. Accordingly, the fluid energy machine 3 also has a valve 29, which, however, is arranged offset by, for example, 180° with respect to the inner rotor axis of rotation 9 relative to the valve 29 of the fluid energy machine 2.

[0088] Each of the fluid energy machines 2 and 3 has two side walls 12, with one of the side walls 12 located between the fluid energy machines 2 and 3 serving as a common side wall, thus forming one side wall 12 for each of the fluid energy machines 2 and 3. The bearing arrangement for the outer rotors 5 of the fluid energy machines 2 and 3 is also common. The previously mentioned bearing ring projections 11 are only present on the outer side walls 12, and not on the common side wall 12 located between the rotors 5 and 8, respectively. This reduces the complexity of the bearing arrangement for the outer rotors 5 of the fluid energy machines 2 and 3.

[0089] Figure 2 shows a schematic cross-sectional view of the fluid energy machine 3. The design can be applied analogously to the fluid energy machine 2. It can be seen that the piston component 20 is rotatably mounted on the inner rotor 8 about a piston component rotation axis 36. A spring element 37 engages the piston component 20, which pushes the piston component 20 towards the outer rotor 5, in particular against the inner circumferential surface 16 of the outer rotor 5. For example, the spring element 37 engages the outer rotor 5 in an outer rotor fluid passage opening 38. The outer rotor fluid passage opening 38 extends radially through the outer rotor 5, in particular through the outer rotor ring 13. A fluid connection between the fluid chamber 22 and the fluid collection chamber 23 is established via the outer rotor fluid passage opening 38.

[0090] To ensure free rotation of the outer rotor 5 and the inner rotor 8, a piston receiving chamber 39 is provided in the inner rotor 8. In at least one position of the piston component 20, it is completely enclosed within the piston receiving chamber 39, so that it does not protrude beyond the outer circumferential surface 17. It can be seen that the inner rotor fluid channel 28 opens into the fluid space 18, specifically into the fluid chamber 21, at a distance from the piston receiving chamber 39. This results in a comparatively small dead space and thus high efficiency.

[0091] The outer rotor 5 and the inner rotor 8 are directly coupled to each other via a drive mechanism, namely, they rotate synchronously. This means that the coupling between the outer rotor 5 and the inner rotor 8 is designed such that the angular velocities of the outer rotor 5 and the inner rotor 8 are identical regardless of their angular position, in particular over a complete revolution. Coupling projections 40, which engage positively in coupling recesses 41, serve to couple the outer rotor 5 and the inner rotor 8. The coupling projections 40 are, for example, in the form of rolling bearings, such as ball bearings or roller bearings. The coupling projections 40 bear against the guide walls 42 that define the coupling recesses 41, at least temporarily. Preferably, the coupling recesses 41 have a non-circular cross-section.For this purpose, they consist of round core recesses 43 and several compensating recesses 44. The compensating recesses 45 extend radially outwards from the core recesses 43, so that the respective guide wall 42 is also located further outwards in the radial direction than away from the compensating recesses 44.

[0092] Preferably, the compensating recesses 44 are diametrically opposed to each of the coupling recesses 41. The compensating recesses 44 are arranged offset between the coupling recesses 41. This ensures that at least one of the coupling projections 40, and preferably several of the coupling projections 40, always bears against the guide walls 42. However, it can be provided that at least temporarily one of the coupling projections 40 is spaced away from the wall of the coupling recess 41 that receives it (not shown here). This prevents an over-constraint of the positive-locking connection between the outer rotor 5 and the inner rotor 8.

[0093] To achieve a good sealing effect at the sealing point 19 between the outer rotor 5 and the inner rotor 8, elastic seals 45 are provided on one of the rotors 5 and 8, in the embodiment shown here on the outer rotor 5. These seals are only partially characterized. The seals 45 are arranged in sealing receptacles 46 and project beyond or protrude from these receptacles at least temporarily in the direction of the inner rotor 8. Due to their elastic design, the seals 45 are deformable and are compressed at least temporarily by the interaction of the outer rotor 5 and the inner rotor 8, with the strongest compression occurring in the area of ​​the sealing point 19.

[0094] For example, the seals 45 are arranged equidistantly to each other in the circumferential direction, particularly only over a first partial area of ​​the respective rotor 5 or 8. It is provided, for instance, that in a second partial area, which accommodates the outer rotor fluid passage opening 38 in the circumferential direction, no seals 45 are present, but rather that this is only the case away from the outer rotor fluid passage opening 38. Due to the synchronous coupling of the outer rotor 5 and inner rotor 8, the inner circumferential surface 16 and the outer circumferential surface 17 roll against each other, in particular without slippage or sliding. Accordingly, the wear of the seals 5 is extremely low, and a long service life of the fluid energy machine arrangement 1 is achieved. Figure 3 shows a schematic representation of a region of the fluid energy machine arrangement 1.The figure shows one of the housing side walls 25 with the fluid connection 24 arranged therein. Also visible are the cam rings 33 and 47 with their cam tracks 34 and 48, on which the actuating elements 32 of the valves 29 slide. It is clear that the valves 29 of both fluid energy machines 2 and 3 are actuated by the same cam rings 33 and 47. It is possible that both actuating elements 32 slide on the same cam tracks 34 and 48. However, it is also possible that each actuating element 32 is assigned a separate cam track 34 of the cam ring 33 and / or a separate cam track 48 of the cam ring 34. At least one of the cam rings 33 and 47 is adjustable in the circumferential direction; preferably, both cam rings 33 and 47 are adjustable. By adjusting the cam ring 33 or 47, or the cam rings 33 and 47, a variable expansion ratio is achieved.Accordingly, the fluid energy machine arrangement 1, or its fluid energy machines 2 and 3, can be operated with a particularly high efficiency.

[0095] Figure 4 shows a schematic sectional view of the fluid energy machine arrangement 1 in a second embodiment. This is fundamentally similar to the first embodiment, so reference is made to the corresponding descriptions, and only the differences will be discussed below. These differences lie in the fact that the valves 29 have actuating elements 32 on both sides when viewed axially, which are arranged on opposite sides of the respective valve body 30. This means that the valves 29 can be moved back and forth axially by means of their actuating elements 32. The spring 35 present in the first embodiment is accordingly omitted. As already explained, in addition to the cam ring 33, a further cam ring 47 with the further cam track 48 is present. However, the cam rings 33 and 47 are arranged axially on opposite sides of the fluid energy machines 2 and 3.The valves 29 of the two fluid energy machines 2 and 3 are therefore actuated - as in the embodiment described above - by the same cam rings 33 and 47 or their cam tracks 34 and 48, but are not deflected in the same actuation direction, but in opposite directions.

[0096] It can be seen that the valves 29 and the actuating elements 32 each bear against the cam rings 33 and 47 via a compensating element 49. The compensating elements 49 are each arranged in a compensating chamber 50 and are axially displaceable. The compensating elements 49 are each supported against the actuating elements 32 by an elastic damping element 51, so that they act with clearance in the axial direction against the respective actuating element 32. The cam rings 33 and 47 are independently adjustable in the circumferential direction. Accordingly, the opening and closing times of the valves 29 are also independently adjustable, thus achieving a variable expansion ratio.

[0097] Figure 5 shows a schematic representation of the fluid energy machine arrangement 1 in a third embodiment, with the outer rotor 5 and the inner rotor 8 in a first position. Only one of the fluid energy machines 2 and 3 is shown; however, the explanations are of course applicable to any number of fluid energy machines 2 and 3. For the fluid energy machine arrangement 1 of the third embodiment, reference is made to the preceding descriptions, particularly with regard to the first embodiment, and the differences are discussed below. These differences lie, firstly, in the fact that the piston component 20 is mounted on the inner rotor 8 in a linearly displaceable manner, namely by a corresponding design of the piston receiving chamber 39.In particular, the piston component 20 is arranged in the piston receiving chamber 39 such that, viewed tangentially, it abuts the walls bounding the piston receiving chamber 39 on opposite sides. It can be seen that the wall 53 is formed, at least in part, by a linear guide projection 54. The linear guide projection 54 is a projection of the inner rotor 8 and extends, at least partially, through the fluid chamber 80 in the direction of the outer rotor 5.

[0098] The distance between the linear guide projection 54 and the outer rotor 5 depends on the rotational angle of the outer rotor 5 and the inner rotor 8. To prevent a collision between the linear guide projection 54 and the outer rotor 5, a guide recess 55 is provided in the outer rotor 5, more precisely in the outer rotor ring 13. The linear guide projection 54 engages in this recess, at least temporarily. The piston component 20 is preferably mounted on the wall 52, particularly on the linear guide projection 54, via a rolling bearing 56. For example, the rolling bearing 56 is rotatably mounted on the piston component 20 and bears against the wall 53 or the linear guide projection 54 with its outer circumferential surface. This results in low-wear mounting.

[0099] Preferably, a driver 57 is provided in the piston receiving chamber 39. This driver is connected to the outer rotor 5, preferably rigidly. In particular, the driver 57 extends from the side wall 12, which is rigidly connected to the outer rotor ring 13. The piston component 20 is supported on the driver 57, for example via the spring element 37. However, it can also be provided, as shown here, that the spring element 37 and the driver 57 engage the piston component 20 separately. Furthermore, it can be seen that the valve body 30 of the control valve 29 is rotatably mounted about a valve body axis of rotation 58 in the inner rotor 8, more precisely in the valve receptacle 31. The valve body 30 has a flow channel 59, which interacts with the inner rotor 8 to adjust the flow cross-section of the inner rotor fluid channel 28.For this purpose, the inner rotor fluid channel 28 runs through the valve receptacle 31, so that the flow cross-section of the inner rotor fluid channel 28 depends on a rotational angle of the valve body 30 with respect to the valve body rotation axis 58.

[0100] A drive element 60 is arranged eccentrically to the valve body's axis of rotation 58 on the valve body 30. This drive element extends axially through the valve body 30 with respect to the valve body's axis of rotation 58 and has one of the coupling projections 40 at at least one of its ends. The valve body 30 is thus drive-connected to the outer rotor 5, in particular the side wall 12, via the drive element 60. A rotational movement of the outer rotor 5 and the inner rotor 8 relative to each other causes a rotational movement of the valve body 30 with respect to the valve body's axis of rotation 58.

[0101] Figure 6 shows a schematic representation of the third embodiment of the fluid energy machine arrangement 1, in which the outer rotor 5 and the inner rotor 8 are in a second position. It can be seen that the linear guide projection 54 now engages in the guide recess 55. In particular, the linear guide projection 54 extends completely through the outer rotor 5, more precisely the outer rotor ring 13, in the radial direction. For example, as shown here, it projects radially beyond the outer rotor ring 13.

[0102] Figure 7 shows a detailed sectional view of the fluid energy machine arrangement 1 in its third embodiment. The valve 29 and the inner rotor fluid channel 28 are particularly visible. It can be seen that the valve body 30 has a bearing journal 61, which is rotatably mounted in the inner rotor 8 about the valve body's axis of rotation 58 by means of a rolling bearing 62. It is further evident that the drive element 60 is arranged eccentrically with respect to the valve body's axis of rotation 58. The drive element 60 is rotatably mounted on the outer rotor 5, specifically on the side wall 12, via rolling bearings 63, about an axis of rotation 64. Depending on the angular position of the outer rotor 5 and the inner rotor 8 relative to each other, the valve body 30 has a corresponding angular position with respect to the valve body's axis of rotation 58.Depending on this rotation angle position, there is a certain overlap of the flow channel 59 with the inner rotor fluid channel 28, resulting in a certain flow cross-section.

[0103] Figure 8 shows a further detailed sectional view of the fluid energy machine arrangement 1 in its third embodiment. It can be seen that the valve body 30 has a base body 65 in which the flow channel 59 is open at the edges. Viewed axially with respect to the valve body's axis of rotation 58, the flow channel 59 is bounded on opposite sides by walls 66, which are preferably integrally formed and made of the same material as the base body 65. In the radial direction, the flow channel 59 is at least partially open at the edges, extending through an outer circumferential surface 67 of the valve body 30. Also visible are the coupling projections 40, which are rotatably mounted on the outer rotor 5 or the side wall 12 by means of a rolling bearing 68. They are also arranged on the inner rotor 8, in particular by means of another rolling bearing (not shown) which is also rotatably mounted on it.Such a design of the fluid energy machine arrangement 1 enables extremely low-maintenance, preferably maintenance-free, operation.

[0104] REFERENCE MARK LIST

[0105] 1 Fluid energy machine arrangement

[0106] 2 Fluid energy machine

[0107] 3 Fluid energy machine

[0108] 4 machine shaft

[0109] 5 Outer rotor

[0110] 6 Outer rotor pivot axis

[0111] 7 machine housings

[0112] 8 inner rotor

[0113] 9 Inner rotor axis

[0114] 10 inner rotor bearings

[0115] 11 Bearing ring projection

[0116] 12 side wall

[0117] 13 Outer rotor ring

[0118] 14 storage location

[0119] 15 outer rotor bearings

[0120] 16 Inner perimeter area

[0121] 17 External perimeter area

[0122] 18 Fluid space

[0123] 19 Sealing point

[0124] 20 Piston component

[0125] 21 Fluid chamber

[0126] 22 Fluid chamber

[0127] 23 Fluid collection chamber

[0128] 24 Fluid connection

[0129] 25 Case side panel

[0130] 26 Coat section

[0131] 27 Cavity

[0132] 28 Inner rotor fluid channel

[0133] 29 valve

[0134] 30 valve bodies

[0135] 31 Valve mount

[0136] 32 Actuator 33 Cam ring

[0137] 34 cam track

[0138] 35 spring

[0139] 36 Piston component rotation axis

[0140] 37 Spring element

[0141] 38 Outer rotor fluid passage opening

[0142] 39 Piston mounting chamber

[0143] 40 coupling advantage

[0144] 41 Coupling recess

[0145] 42 guide wall

[0146] 43 Core cavity

[0147] 44 Compensation exemption

[0148] 45 Seal

[0149] 46 Seal receptacle

[0150] 47 Cam ring

[0151] 48 cam track

[0152] 49 Compensating element

[0153] 50 Compensation Chamber

[0154] 51 Damping element

[0155] 52 Wall

[0156] 53 Wall

[0157] 54 Linear guide projection

[0158] 55 Guide recess

[0159] 56 rolling bearings

[0160] 57 drivers

[0161] 58 Valve body axis of rotation

[0162] 59 Flow channel

[0163] 60 Drive component

[0164] 61 bearing journals

[0165] 62 rolling bearings

[0166] 63 rolling bearings

[0167] 64 Rotation axis

[0168] 65 Basic bodies

[0169] 66 Wall 67 External perimeter area

[0170] 68 rolling bearings

Claims

39 REQUIREMENTS 1. Fluid energy machine (2, 3), comprising an outer rotor (5) rotatably mounted about an outer rotor axis of rotation (6) and an inner rotor (8) rotatably mounted about an inner rotor axis of rotation (9) different from the outer rotor axis of rotation (6), the inner rotor being arranged in a rotor receptacle of the outer rotor (5) and bearing with an outer circumferential surface (17) at a sealing point (19) against an inner circumferential surface (16) of the outer rotor (5) which defines the rotor receptacle, wherein a fluid space (18) is located between the outer circumferential surface (17) of the inner rotor (8) and the inner circumferential surface (16) of the outer rotor (5), which is emptied into a first fluid chamber (21) by a piston component (20) which is displaceably mounted on the inner rotor (8) and sealingly abuts the outer rotor (5) or is displaceably mounted on the outer rotor (5) and sealingly abuts the inner rotor (8). and a second fluid chamber (22) is subdivided, characterized bythat the outer rotor (5) and the inner rotor (8) are coupled to each other in a drive-related manner so that the angular velocity of the outer rotor (5) and the angular velocity of the inner rotor (8) are constantly the same.

2. Fluid energy machine according to claim 1, characterized in that the outer rotor (5) and the inner rotor (8) are arranged between the fluid chamber (18) in the axial direction with respect to the outer rotor axis of rotation (6) and / or the inner rotor axis of rotation (9) on opposite side walls (12), wherein the outer rotor (5) or the inner rotor (8) is rigidly connected to the side walls (12) and the other of the rotors (5, 8) abuts the side walls (12) in a sealing manner.

3. Fluid energy machine according to one of the preceding claims, characterized in that the drive coupling of the outer rotor (5) and the inner rotor (8) is implemented by means of a gear drive or a traction drive or coupling projections (40) extend from at least one of the side walls (12) which engage in coupling recesses (41) of the outer rotor (5) or the inner rotor (8) in a form-fitting manner.

4. Fluid energy machine according to one of the preceding claims, characterized in that the coupling recesses (41) have a non-circular cross-section and are composed of round core recesses (43) and compensation recesses (44) adjoining the core recesses (43) in a radial direction with respect to the outer rotor axis of rotation (6) and / or the inner rotor axis of rotation (9). 40 5. Fluid energy machine according to one of the preceding claims, characterized in that the compensation recesses (44) are arranged such that a first coupling projection (40) is spaced apart from a first guide wall (42) which limits a first coupling recess (41) in a radial direction to the outside, while a second coupling projection (40) abuts a second guide wall (42) which limits a second coupling recess (41) in a radial direction to the outside.

6. Fluid energy machine according to one of the preceding claims, characterized in that an inner rotor fluid channel (28) is provided in the inner rotor (8), which opens into the fluid space (18) and in which a valve (29) provided and designed for adjusting a flow cross-section of the inner rotor fluid channel (28) is arranged, wherein the valve (29) is a control valve.

7. Fluid energy machine according to one of the preceding claims, characterized in that an actuating element (32) of the control valve (29) for adjusting the flow cross-section cooperates with a cam track (34) of a cam ring (33), that the valve (29) is a check valve, or that a valve body (30) of the control valve (29) is rotatably mounted about a valve body rotation axis (58) in the inner rotor (8) and is drive-connected to at least one of the coupling projections (40).

8. Fluid energy machine according to one of the preceding claims, characterized in that the cam ring (33) is adjustable for adjusting the flow cross-section.

9. Fluid energy machine according to one of the preceding claims, characterized in that the cam ring (33) is part of several cam rings (33, 47), each of the cam rings (33, 47) having a cam track (34, 48) which interacts with the actuating element (32) or with several actuating elements (32) of the valve (29) to adjust the flow cross-section of the control valve (29).

10. Fluid energy machine according to one of the preceding claims, characterized in that the rotatable mounting of the valve body (30) is implemented by means of a bearing journal which projects in the axial direction with respect to the valve body rotation axis (58) on opposite sides beyond a base body of the valve body (30), and / or 41 that a drive component is attached to the valve body (30) eccentrically to the valve body axis of rotation (58). (60) is arranged on which at least one coupling projection (40) is arranged.

11. Fluid energy machine according to one of the preceding claims, characterized in that the rotatably mounted valve body (30) has a flow channel (59) which is limited in the axial direction with respect to the valve body rotation axis (58) on opposite sides of walls (66) of the valve body (30) and extends in the radial direction through an outer circumferential surface (67) of the valve body (30) in certain areas.

12. Fluid energy machine according to one of the preceding claims, characterized in that the piston component (20) is subjected to spring force or magnetic force by means of a spring element (37) or a magnet arrangement in the direction of the inner rotor (8) or the outer rotor (5).

13. Fluid energy machine according to one of the preceding claims, characterized in that the piston component (20) is located in at least one position at least partially in a piston receiving chamber (39) produced in the inner rotor (8) and extending through the outer circumferential surface (17) of the inner rotor (8), wherein the inner rotor fluid channel (28) opens into the fluid space (18) at a distance from the piston receiving chamber (39).

14. Fluid energy machine according to one of the preceding claims, characterized in that a driver (57) connected to the outer rotor (5) is arranged in the piston receiving chamber (39), on which the piston component (20) is supported in a radial direction with respect to the outer rotor axis of rotation (6) or the inner rotor axis of rotation (9).

15. Fluid energy machine according to one of the preceding claims, characterized in that the piston component (20) is supported in a tangential direction with respect to the outer rotor axis of rotation (6) or the inner rotor axis of rotation (9) on a linear guide projection (54) of the inner rotor (8), which engages in a guide recess (55) of the outer rotor (5) in at least one position of outer rotor (5) and inner rotor (8) relative to each other.

16. Fluid energy machine according to one of the preceding claims, characterized in that seals (45) are provided on the outer rotor (5) and / or the inner rotor (8). are arranged in a radially sealing position against the other of the rotors (5, 8).

17. Fluid energy machine according to one of the preceding claims, characterized in that the seals (45) are provided in sealing receptacles (46) which are manufactured in the outer rotor (5) and / or the inner rotor (8), wherein the seals (45) project from the sealing receptacles (46) into the fluid space (18) at least temporarily in order to seal against the outer rotor (5) or the inner rotor (8).

18. Fluid energy machine arrangement (1), comprising several fluid energy machines (2, 3) coupled to a common machine shaft (4) for drive purposes, in particular fluid energy machines (2, 3) each according to one or more of the preceding claims, wherein each of the fluid energy machines (2, 3) has an outer rotor (5) rotatably mounted about an outer rotor axis of rotation (6) and an inner rotor (8) rotatably mounted about an inner rotor axis of rotation (9) different from the outer rotor axis of rotation (6), which is arranged in a rotor receptacle of the outer rotor (5) and bears with an outer circumferential surface (17) at a sealing point (19) against an inner circumferential surface (16) of the outer rotor (5) which defines the rotor receptacle, wherein a fluid space (18) is provided between the outer circumferential surface (17) of the inner rotor (8) and the inner circumferential surface (16) of the outer rotor (5),the piston component (20) is movably mounted on the inner rotor (8) and sealingly in contact with the outer rotor (5) or movably mounted on the outer rotor (5) and sealingly in contact with the inner rotor (8), divided into a first fluid chamber (21) and a second fluid chamber (22), characterized in that the outer rotor (5) and the inner rotor (8) are coupled to each other in a drive-related manner so that the angular velocity of the outer rotor (5) and the angular velocity of the inner rotor (8) are constantly the same.

19. Drive device with a fluid circuit in which a fluid pump, a fluid heater and a fluid energy machine (2, 3) according to one or more of claims 1 to 12 are provided.

20. Method for operating a fluid energy machine (2, 3), in particular a fluid energy machine (2, 3) according to one or more of claims 1 to 12, wherein the fluid energy machine (2, 3) has an outer rotor (5) rotatably mounted about an outer rotor axis of rotation (6) and an inner rotor (8) rotatably mounted about an inner rotor axis of rotation (9) different from the outer rotor axis of rotation (6), which is mounted in a rotor receptacle of the The outer rotor (5) is arranged and its outer circumferential surface (17) abuts a sealing surface (19) against an inner circumferential surface (16) of the outer rotor (5) that defines the rotor mount, wherein a fluid chamber (18) is located between the outer circumferential surface (17) of the inner rotor (8) and the inner circumferential surface (16) of the outer rotor (5), which is divided into a first fluid chamber (21) and a second fluid chamber (22) by a piston component (20) that is movably mounted on the inner rotor (8) and sealingly abuts the outer rotor (5) or movably mounted on the outer rotor (5) and sealingly abuts the inner rotor (8), and wherein at least one of the fluid chambers (21, 22) is supplied with a fluid at least temporarily, characterized in that the outer rotor (5) and the inner rotor (8) are coupled to each other in a drive-related manner so that an angular velocity the angular velocity of the outer rotor (5) and the angular velocity of the inner rotor (8) are constant throughout.

Images