Fluid machine

Abstract

The invention relates to a fluid machine (1), having: a first fluid chamber (12), which is at least intermittently fluidically connected to a first fluid port (17) of the fluid machine (1), and a second fluid chamber (13), which is at least intermittently fluidically connected to a second fluid port (18) of the fluid machine (1); a fluid-conveying element (3), which is supported so as to be rotatable about an axis of rotation (5), delimits the first fluid chamber (12) and / or the second fluid chamber (13) at least in certain regions and is provided and designed to convey a fluid from the first fluid chamber (12) in the direction of the second fluid chamber (13); and a control element (19), which bears slidingly against the fluid-conveying element (3) and in which there is formed at least one control recess (22) which is open in the direction of the fluid-conveying element (3), from which control recess a preliminary control recess (28) proceeds in the circumferential direction with respect to the axis of rotation (5), said preliminary control recess being open in the direction of the fluid-conveying element (3) and extending through an edge (31) of the control recess (22). According to the invention, a flow cross-sectional area of the preliminary control recess (28) exhibits different rates of change in different preliminary control recess regions (32, 33, 34) which follow one another in the circumferential direction.

Description

[0001] DESCRIPTION

[0002] Fluid machine

[0003] The invention relates to a fluid machine, with a first fluid chamber which is at least temporarily fluidically connected to a first fluid connection of the fluid machine and with a second fluid chamber which is at least temporarily fluidically connected to a second fluid connection of the fluid machine, and with a fluid conveying element which is mounted so as to be rotatable about an axis of rotation and which delimits the first fluid chamber and / or the second fluid chamber at least in regions and is provided and designed to convey a fluid from the first fluid chamber in the direction of the second fluid chamber, and with a control element which bears slidably against the fluid conveying element and in which at least one control recess which is open in the direction of the fluid conveying element is formed, from which a pilot control recess which is open in the direction of the fluid conveying element and extends through an edge of the control recess extends in the circumferential direction with respect to the axis of rotation.

[0004] For example, the prior art document DE 10 2014 103 959 A1 is known. This describes a motor-pump unit with a multi-part housing, comprising a reversible internal gear unit and an electric motor with a rotor and a stator, which is coupled to the internal gear unit via a shaft rotatably mounted in the housing. The shaft extends axially away from the internal gear unit with one end through the rotor, which is supported by the shaft.A first connection channel and a second connection channel open into a working chamber of the internal gear machine and are connected via check valves arranged in the housing to a leakage channel loop which is fluidly connected to at least one leakage channel which is fluidly connected to the working chamber and which has a leakage shaft channel extending axially through the shaft and a leakage rotor channel which is fluidly connected thereto and extends axially through the rotor and / or a leakage gap channel formed between the rotor and the stator and which is fluidly connected to the leakage shaft channel.

[0005] The object of the invention is to propose a fluid machine that offers advantages over known fluid machines, in particular enabling optimized pressure buildup and pressure reduction in the fluid machine. This is achieved according to the invention with a fluid machine having the features of claim 1. It is provided that a flow cross-sectional area of ​​the pilot control recess has different rates of change in different pilot control recess regions that follow one another in the circumferential direction.

[0006] Advantageous embodiments with useful further developments of the invention are specified in the dependent claims. It should be noted that the exemplary embodiments explained in the description are not limiting; rather, any variations of the features disclosed in the description, the claims, and the figures are feasible.

[0007] The fluid machine represents a fluid conveying device and thus serves to convey a fluid, for example a liquid or a gas. For this purpose, the fluid machine can in principle be designed in any desired manner, provided it has the rotatably mounted fluid conveying element against which the control element slides. This description will primarily focus on the design of the fluid machine as a gear fluid machine, for example, as an internal gear fluid machine or as an external gear fluid machine. However, other embodiments of the fluid machine are also fundamentally feasible. Purely by way of example, reference should be made to a rotary piston fluid machine, for example, a rotary vane fluid machine or a rotary piston fluid machine, as well as an axial piston fluid machine.

[0008] In any case, a rotatably mounted fluid conveying element serves to convey fluid from a first fluid chamber into a second fluid chamber or vice versa. The control element, which slides against the fluid conveying element, serves to seal the first fluid chamber and / or the second fluid chamber. For example, the fluid conveying element and the control element jointly delimit at least one of the fluid chambers or both fluid chambers, at least in some areas. Of course, multiple control elements can also be present, which in this case preferably slide against the fluid conveying element on opposite sides, in particular as viewed in the axial direction with respect to the axis of rotation of the fluid conveying element.In this case, the control elements delimit the first fluid chamber and / or the second fluid chamber on opposite sides as seen in the axial direction, whereas the fluid conveying element delimits the first fluid chamber and / or the second fluid chamber in the radial direction, in particular inwards or outwards. The control recess, which is open in the direction of the fluid conveying element, is formed in the control element. As far as the control recess, at least one control recess or the at least one control recess is mentioned in this description, the statements are always equivalent to one another and can be transferred to one another. Of course, only exactly one control recess can be produced in the control element, but preferably there are several control recesses. In this case, what has been said for the control recess applies to at least some of the control recesses, preferably to all control recesses.

[0009] The control recess is configured in the control element such that it is at least temporarily open toward one of the fluid chambers or at least temporarily in fluid communication with one of the fluid chambers. With the aid of the control recess, a pressure buildup or pressure reduction occurring in the fluid machine, for example, in one of the fluid chambers, can be specifically controlled or adjusted. In particular, the control recess additionally or alternatively achieves an at least partially uniform pressure distribution within one of the fluid chambers.

[0010] In order to be able to adapt the pressure build-up or pressure reduction even better, the pilot control recess extends from the control recess. The pilot control recess extends from the control recess in the circumferential direction, namely with respect to the axis of rotation of the fluid conveying element. It also penetrates the edge of the control recess, which is formed in the control element and delimits the control recess, in particular in the radial direction and / or in the circumferential direction. In other words, the pilot control recess opens into the control recess. The control recess and the pilot control recess are preferably produced by milling and / or stamping. For example, the control recess is produced completely first, in particular with a continuous edge. Only then is the pilot control recess produced in the control element, whereby the edge of the control recess is partially interrupted.

[0011] To achieve a particularly effective pilot control recess, the flow cross-sectional area of ​​the pilot control recess changes in the circumferential direction. The flow cross-sectional area is the area of ​​a flow cross-section of the pilot control recess, which is present in section across the entire pilot control recess. The flow cross-section extends to an orifice, forming the pilot control recess through a side of the control element facing the fluid-conveying element. In particular, the orifice is located in a sealing surface of the control element, with which the control element rests against the fluid-conveying element in a sliding and thus sealing manner, at least temporarily.

[0012] The pilot control recess is divided into several pilot control recess regions, which follow one another in the circumferential direction. The pilot control recess regions are, in particular, directly adjacent to one another. Any number of pilot control recess regions can be present, for example, at least two pilot control recess regions, at least three pilot control recess regions, or at least four pilot control recess regions. At least in immediately consecutive pilot control recess regions, the flow cross-sectional area of ​​the pilot control recess has different rates of change. This means that different rates of change exist in directly adjacent pilot control recess regions, whereas the rates of change in spaced-apart pilot control recess regions can be entirely identical.Preferably, the rates of change have at least the same sign, so that the flow cross-sectional area changes in one direction, for example in the circumferential direction, in the same direction, i.e. becomes either larger or smaller.

[0013] Preferably, the respective rate of change in the pilot control recess regions is constant or at least almost constant across the respective pilot control recess region. This means that the rate of change of the flow cross-sectional area only changes at a transition between the different pilot control recess regions and otherwise remains constant. Of course, it can be provided that this applies only to one or more of the pilot control recess regions, whereas the respective rate of change changes across at least one or more further pilot control recess regions. Thus, overall, it can be provided that the rate of change of the flow cross-sectional area is consistently constant across at least one of the pilot control recess regions, whereas it changes at least in some regions, in particular changes continuously, across at least one other of the pilot control recess regions.If the rate of change changes across the respective pilot control recess area, a constant or at least continuous change in the rate of change is preferably provided in order to achieve a uniform progression of the flow cross-sectional area across the pilot control recess. The rate of change is preferably understood to be an absolute value of the rate of change, i.e., the sign-corrected rate of change.

[0014] With the described design of the fluid machine, the pressure build-up or pressure reduction occurring in the fluid machine can be adjusted very precisely. With previously common control recesses, a very abrupt pressure build-up or pressure reduction occurs, particularly at very low or very high speeds, especially in conjunction with high pressures. This is avoided by the described design of the pilot control recess, thereby achieving a positive impact on the service life of the fluid machine and / or its noise behavior.

[0015] Depending on the direction of rotation of the fluid machine, one of the fluid chambers serves as the suction chamber and the other as the pressure chamber. If the fluid machine is designed as a pump or is operated as a pump, fluid is supplied to the respective suction chamber, which the fluid machine pumps towards the pressure chamber or into the pressure chamber. The suction chamber can accordingly also be referred to as the inlet chamber and the pressure chamber as the outlet chamber; what is crucial is that the fluid is always pumped from the inlet chamber towards the outlet chamber during operation of the fluid machine. The pressure in the inlet chamber is always lower than the pressure in the outlet chamber when the pump is operating. Of course, however, the pressure in the inlet chamber can already be (significantly) greater than ambient pressure.For example, the fluid machine is used to pump pressurized fluid from the inlet chamber towards the outlet chamber.

[0016] If, on the other hand, the fluid machine is designed as a motor or is operated as a motor, fluid is supplied to the pressure chamber, which enters the suction chamber, causing the gears to rotate. In this case, the pressure chamber acts as the inlet chamber and the suction chamber as the outlet chamber; the pressure in the inlet chamber is higher than the pressure in the outlet chamber. This description does not explicitly address the operation of the fluid machine as a motor, but rather explains the fluid machine, its structure and function for operation as a pump. Of course, use as a motor is also possible, and the explanations are analogously applicable to such a design of the fluid machine or such a use.It should be noted that, for the purposes of this description, the suction chamber can also be referred to as a low-pressure chamber, and the pressure chamber as a high-pressure chamber. Analogously, the suction side of the fluid machine corresponds to a low-pressure side, and the pressure side to a high-pressure side. The terms "initially a low pressure" and "high pressure" do not imply a restriction to a specific pressure level; rather, the pressure in the high-pressure chamber or on the high-pressure side is simply relatively higher than the pressure in the low-pressure chamber or on the low-pressure side.

[0017] A further development of the invention provides that the pilot control recess immediately adjacent to the control recess has a smaller flow cross-sectional area and / or a smaller depth than the control recess immediately adjacent to the pilot control recess. If the control recess and the pilot control recess are therefore considered as a single recess, this recess exhibits a sudden change in its flow cross-sectional area or depth at the transition between the control recess and the pilot control recess. More precisely, the flow cross-sectional area or depth becomes smaller at the transition between the control recess and the pilot control recess. For example, the reduction in the flow cross-sectional area is brought about solely by the reduction in depth.Preferably, however, the flow cross-sectional area also decreases apart from the reduction in depth or even without changing the depth, in particular by reducing a distance between pilot control recess walls which delimit the pilot control recess on opposite sides.

[0018] For example, the pilot control recess immediately adjacent to the control recess has a flow cross-sectional area which amounts to at most 30%, at most 20%, or at most 10% of the flow cross-sectional area of ​​the control recess immediately adjacent to the pilot control recess. However, the flow cross-sectional area is particularly preferably smaller, for example, it amounts to at most 5%, at most 2.5%, or at most 1% of the flow cross-sectional area of ​​the control recess immediately adjacent to the pilot control recess. Additionally or alternatively - as already explained - the depth of the pilot control recess immediately adjacent to the control recess is smaller than the depth of the control recess immediately adjacent to the pilot control recess, for example, it amounts to at most 60%, at most 50%, or at most 40% of the latter.Preferably, however, it is even smaller and amounts, for example, to a maximum of 40%, a maximum of 20%, or a maximum of 10% of the depth of the control recess immediately adjacent to the pilot control recess. With the described design of the fluid machine, the aforementioned advantages are achieved in a structurally simple manner, in particular, the optimized pressure build-up and pressure reduction are implemented.

[0019] A further development of the invention provides that the pilot control recess is delimited by a pilot control recess base and by opposing pilot control recess walls. The pilot control recess base delimits the pilot control recess in the axial direction, i.e., in the direction facing away from the fluid conveying element. The pilot control recess walls, however, delimit the pilot control recess in a direction perpendicular thereto, in particular in the radial inward and outward direction and preferably additionally in the circumferential direction, namely at least on one side of the pilot control recess facing away from the control recess. The pilot control recess penetrates the aforementioned sealing surface of the control element, forming the orifice, which is produced on the side of the pilot control recess opposite the pilot control recess base.The pilot control recess walls form an edge of this opening, which is preferably continuous beyond the control recess. The edge of the pilot control recess is therefore only interrupted at its junction with the control recess. This also achieves the aforementioned advantages.

[0020] A further development of the invention provides that in at least one of the pilot control recess regions, the pilot control recess walls run parallel to one another. This means that the pilot control recess walls have a constant distance from one another across the pilot control recess region. If the pilot control recess walls are curved, one of the pilot control recess walls runs, for example, on a shell of a first circular cylinder and a second of the pilot control recess walls runs on the shell of a second circular cylinder, which preferably has the same diameter as the first circular cylinder but is arranged offset therefrom. The parallel course of the pilot control recess walls in the pilot control recess region achieves a comparatively low rate of change in the flow cross-sectional area of ​​this pilot control recess region.Thus, a variation of the change rates of the pilot control recess regions is achieved in a structurally simple manner. A further development of the invention provides that in at least one of the pilot control recess regions, the pilot control recess base runs parallel to an orifice, via which the pilot control recess is open in the direction of the fluid conveying element, such that the depth of the pilot control recess is constant over an extent of the pilot control recess region. This means, in particular, that the pilot control recess base runs parallel to the aforementioned sealing surface, which penetrates the pilot control recess, creating the orifice in the direction of the fluid conveying element. By means of the parallel arrangement of the pilot control recess base with respect to the orifice or the sealing surface, a constant depth of the pilot control recess is achieved in the pilot control recess region.In this way, a low rate of change of the flow cross-sectional area in the respective pilot control recess area can be achieved quite easily.

[0021] A further development of the invention provides that in at least one of the pilot control recess regions, a rate of change other than zero is present due to a change in the distance between the pilot control recess walls over an extent of the pilot control recess region and / or due to a change in the depth of the pilot control recess over an extent of the pilot control recess region. The rate of change other than zero is to be understood as meaning that the flow cross-sectional area of ​​the pilot control recess changes over the corresponding pilot control recess region, i.e., becomes either larger or smaller. This can be achieved by various measures. On the one hand, it is possible to change the distance between the pilot control recess walls or the depth of the pilot control recess, i.e., the distance of the pilot control recess base from the mouth opening or the sealing surface.

[0022] It can be provided that only the distance between the pilot control recess walls changes, whereas the depth of the pilot control recess remains constant across the pilot control recess region. Conversely, it can be provided that the distance between the pilot control recess walls remains constant, but the depth of the pilot control recess changes across the pilot control recess region. Finally, both the distance between the pilot control recess walls and the depth of the pilot control recess can change within or across the pilot control recess region. The change in the distance and the change in the depth preferably occur in such a way that they cause a change in the feedthrough cross-sectional area in the same direction.If changing the distance between the pilot recess walls causes the cross-sectional flow area to increase, the change in depth is also selected to cause such an increase. The opposite is true for a decrease in the cross-sectional flow area. The distance can be changed, for example, by the pilot recess walls converging towards one another so that the distance continuously decreases, namely at a constant rate of change. However, it can also be provided that at least one of the pilot recess walls or both pilot recess walls are curved, namely such that their distance from one another changes. The pilot recess base can also be straight or curved to change the depth. For example, a convex or concave profile of the pilot recess walls and / or the pilot recess base is realized.In the manner described, the advantages already mentioned can be easily achieved.

[0023] A further development of the invention provides that a first rate of change of the flow cross-sectional area is present in a first of the pilot control recess regions adjoining the control recess, and a second rate of change of the flow cross-sectional area is present in a second of the pilot control recess regions adjoining the first pilot control recess region, wherein the second rate of change is greater than the first rate of change. Starting from the control recess, the rate of change of the flow cross-sectional area of ​​the pilot control recess, in particular its absolute value, should initially be greater and then decrease. This means that, starting from the control recess, the flow cross-sectional area of ​​the pilot control recess initially changes less in the first pilot control recess region and then more significantly in the second pilot control recess region.This allows for a highly targeted adjustment of the pressure build-up and / or pressure reduction during operation of the fluid machine.

[0024] A further development of the invention provides that one of the pilot control recess areas is bordered on both sides by another of the pilot control recess areas, wherein the rate of change in the pilot control recess area is greater than in the other pilot control recess areas, in particular by a factor of at least 5, at least 10, or at least 15. In total, there are therefore at least three pilot control recess areas, namely the pilot control recess area and the two other pilot control recess areas. The other pilot control recess areas are arranged on opposite sides of the pilot control recess area and thus accommodate it between them. The other pilot control recess areas directly border the pilot control recess area, i.e., they extend directly from it.

[0025] In the additional pilot control recess regions, the rate of change of the flow cross-sectional area is smaller than the rate of change in the pilot control recess region. The rates of change in the additional pilot control recess regions can be identical or different from one another. Preferably, the rate of change in the pilot control recess region is significantly greater than the rates of change, or each of the rates of change, in the additional pilot control recess regions, preferably by one of the aforementioned factors. This achieves the aforementioned advantages.

[0026] A further development of the invention provides that the rates of change in the further pilot control recess areas are identical or differ from one another by a maximum of 50%, a maximum of 25%, or a maximum of 10%. The rate of change in a first of the further pilot control recess areas thus corresponds to the rate of change in a second of the further pilot control recess areas or deviates from them by a maximum of one of the stated values. The deviation can be upward or downward; for example, a larger rate of change is greater than a smaller rate of change by a maximum of one of the stated values. Conversely, the smaller of the rates of change is smaller than the larger rate of change by a maximum of one of the stated values.Overall, this results in a fluid machine design in which a comparatively large rate of change exists in the pilot control recess area, whereas the rate of change in the additional pilot control recess areas surrounding the pilot control recess area is identical or at least nearly identical. This enables a low-loss flow of the fluid into the pilot control recess area, thus optimizing the pressure buildup or pressure reduction of the fluid during operation of the fluid machine.

[0027] A further development of the invention provides that the control recess is at least temporarily fluidically connected to one of the fluid connections. For example, it is provided that the fluid connection is connected to one of the fluid chambers via the control recess. The fluid connection between the control recess and the fluid connection is not merely indirect via the fluid chamber, but rather the control recess is fluidically provided between the fluid chamber and the fluid connection. Accordingly, in such a configuration, flow into and out of the fluid chamber occurs via the control recess. In a gear fluid machine, in particular an internal gear fluid machine, the fluid flows in and out in the axial direction. This implements efficient flow guidance within the fluid machine.

[0028] A further development of the invention provides that at least one further pilot control recess extends from the control recess in the circumferential direction relative to the rotational axis, said recess opening in the direction of the fluid conveying element and extending through an edge of the control recess. A flow cross-sectional area of ​​the at least one further pilot control recess exhibits different rates of change in different pilot control recess regions that follow one another in the circumferential direction. In addition to the pilot control recess, there is thus the further pilot control recess, which also extends from the control recess and extends through its edge.

[0029] Preferably, the pilot control recess and the further pilot control recess extend from the control recess in the same direction, in particular in the circumferential direction. The pilot control recess and the further pilot control recess are arranged on the same side of the control recess and extend therefrom, in particular in the circumferential direction. The further pilot control recess is designed essentially analogously to the pilot control recess, so reference is made to the relevant explanations. The change rates present in the pilot control recess regions of the further pilot control recess preferably correspond to the change rates of the pilot control recess regions in the pilot control recess; however, they may also differ from these.With the help of the several pilot control recesses, i.e. the pilot control recess and at least one further pilot control recess, the pressure build-up or pressure reduction in the fluid machine can be controlled in a particularly targeted manner.

[0030] A further development of the invention provides that the fluid machine is a gear fluid machine, and the fluid conveying element is a first gear with a first toothing, and the rotational axis is a first rotational axis. In addition to the first gear, there is a second gear rotatably mounted about a second rotational axis and having a second toothing that meshes with the first toothing. The gear fluid machine thus has two gears, namely the first gear and the second gear. The gear fluid machine can, in principle, be designed in any desired manner; in particular, it is designed as an external gear fluid machine or an internal gear fluid machine.

[0031] In the case of an external gear fluid machine, both gears have external teeth that mesh with each other in an engagement region. If the fluid machine is an internal gear fluid machine, the first gear has external teeth and the second gear has internal teeth, or vice versa. In this case, the first gear can also be referred to as a pinion and the second gear as a ring gear. The teeth of the two gears mesh with each other in some areas in the circumferential direction, i.e. they mesh with each other in some areas, namely in an engagement region. Regardless of the design of the fluid machine, the two gears are intended for fluid conveyance and are therefore designed in such a way that they interact during a rotary movement to convey the fluid and in doing so engage or mesh with each other.This means that a rotational movement of the first gear is transmitted directly to the second gear and vice versa, a rotational movement of the second gear is transmitted directly to the first gear.

[0032] Both the first gear and the second gear are preferably arranged in a machine housing of the fluid machine and rotatably mounted therein. The first gear is rotatably mounted about the first axis of rotation, whereas the second gear is rotatably mounted about the second axis of rotation. In the internal gear fluid machine, viewed in cross-section, i.e. in a sectional plane perpendicular to the axes of rotation, the first gear is arranged in the second gear, namely in such a way that the toothing, in particular external toothing, of the first gear meshes or is in engagement with the toothing, in particular internal toothing, of the second gear in the engagement region. In the context of this description, reference is mainly made to the design of the fluid machine as an internal gear fluid machine by way of example.However, the described design of the control element can be used in any fluid machine, and in particular in any gear fluid machine, especially for external gear fluid machines. The explanations are therefore always transferable analogously to a gear fluid machine designed as an external gear fluid machine.

[0033] The engagement area is, for example, fixed to the housing, meaning it does not rotate with the first gear or the second gear. In the engagement area, a tooth of one of the gears engages with a tooth space of the other gear. The tooth space is circumferentially bounded by the teeth of the respective gear. For example, a tooth of the first gear engages with a tooth space of the second gear, or conversely, a tooth of the second gear engages with a tooth space of the first gear.

[0034] The two gears of the fluid machine are arranged between housing walls of the aforementioned machine housing of the fluid machine. For example, the gears are mounted on and / or in the machine housing, in particular on the housing walls. One of the housing walls is therefore located on a first side of the gears, and a second of the housing walls is located on a second side of the gears, opposite the first side in the axial direction, so that the housing walls accommodate the gears between them in the axial direction. For example, a gap remaining between the housing walls and the gears is dimensioned so small that the housing walls ensure sufficient sealing of the fluid space or fluid chambers.

[0035] However, it is particularly preferred for an optional sealing disk to be arranged in the axial direction relative to the first axis of rotation next to the first gear and the second gear, i.e. in particular between one of the housing walls and the gears, which sealing disk rests sealingly against the first gear and the second gear during operation of the fluid machine. For example, viewed in the axial direction, the sealing disk is only present on one side of the first gear and the second gear. However, it is preferably provided that - again viewed in the axial direction - such a sealing disk is arranged on each side of the two gears. In the context of this description, the particularly advantageous case in which multiple sealing disks are present will be explained.However, it goes without saying that the corresponding embodiments can also be used for a design of the fluid machine in which only a single sealing disc is part of the fluid machine.

[0036] The sealing disc is preferably forced in the axial direction towards the gears, for example by pressurisation, i.e. by exposure to a pressurised fluid, so that it bears sealingly against the gears. If there are several sealing discs, they are arranged on both sides of the gears in the axial direction. One of the sealing discs is therefore located on a first side of the gears and a second of the sealing discs is located on a second side of the gears opposite the first side in the axial direction, so that the sealing discs hold the gears between them in the axial direction. The sealing discs are preferably forced towards one another in the axial direction and thus each in the direction of the gears, for example by pressurisation, i.e. by exposure to the pressurised fluid, so that the sealing discs bear sealingly against the gears on opposite sides.The fluid machine is therefore axially compensated or gap-compensated in the axial direction. This ensures particularly high efficiency of the fluid machine.

[0037] The sealing disc is preferably in the form of the control element already described. In other words, the control element is designed as a sealing disc and is therefore located axially adjacent to the gears of the fluid machine. According to the above explanations, it is particularly preferred to use several sealing discs and correspondingly several control elements. These are arranged on opposite sides of the gears and bear against one another in a sealing manner, in particular with their respective sealing surfaces. The control recess and the pilot control recess can be used to particularly advantageously influence the pressure buildup or pressure reduction.

[0038] A further development of the invention provides that the pilot control recess and the at least one further pilot control recess are arranged at a distance from one another in the radial direction, in particular the pilot control recess is arranged in radial direction with respect to the first axis of rotation in overlap with teeth of the first toothing and the further pilot control recess is arranged in radial direction with respect to the second axis of rotation in overlap with teeth of the second toothing. Such a configuration enables particularly targeted adjustment of the pressure build-up and pressure reduction, in particular in the spaces between the teeth of the toothing or toothings. This is achieved by the radially offset arrangement of the pilot control recess and the further pilot control recess. Particularly preferably, the pilot control recess and the at least one further pilot control recess are additionally arranged in at least some regions in the circumferential direction in overlap.This means that a straight line perpendicular to one of the rotational axes intersects both the pilot control recess and the at least one additional pilot control recess. It can also be provided that the pilot control recess at least temporarily overlaps the interdental spaces of the first toothing, and the additional pilot control recess at least temporarily overlaps the interdental spaces of the second toothing, so that fluid can flow between them, for example, from the respective pilot control recess into the respective interdental spaces or vice versa. This, in turn, achieves the aforementioned advantages.A further development of the invention provides that in a first region, seen in the circumferential direction, the first toothing and the second toothing engage with one another and in a second region, tooth tips of the first toothing and the second toothing bear against one another in a sealing manner in order to divide a fluid space present between the first gear and the second gear into a first fluid chamber and a second fluid chamber, or that between the first gear and the second gear, away from the first region, a filler piece is arranged which bears on the one hand against the first toothing and on the other hand against the second toothing in order to divide the fluid space present between the first gear and the second gear into the first fluid chamber and the second fluid chamber.

[0039] In the engagement region, the first toothing and the second toothing cooperate in a sealing manner. On the other side of the engagement region, i.e. preferably on the side diametrically opposite the engagement region with respect to the first axis of rotation and / or the second axis of rotation, a filler piece, for example, is arranged. The filler piece is located between the first gear and the second gear, or in other words between the external toothing of the first gear and the internal toothing of the second gear. The filler piece is thus arranged in a fluid chamber which is delimited in the radially inward direction by the first gear and in the radially outward direction by the second gear, in each case with respect to the first axis of rotation and the second axis of rotation. The filler piece rests on the one hand against the first toothing and on the other hand against the second toothing.More precisely, the filler piece sealingly engages the tooth tips of the first toothing and the tooth tips of the second toothing, dividing the fluid space into a first fluid chamber and a second fluid chamber. Thus, viewed in the circumferential direction, each of the two fluid chambers is bounded on the one hand by the filler piece and on the other hand by the tight meshing of the first toothing and the second toothing in the engagement area.

[0040] The filler piece is preferably designed in several parts and therefore has a plurality of segments. The segments of the filler piece are arranged next to one another in the radial direction, so that a first segment is arranged on the side of a second segment facing the first gear, and conversely the second segment is arranged on the side of the first segment facing the second gear. The first segment lies in sealing contact with the first gear or its external toothing, and the second segment lies in sealing contact with the second gear or the internal toothing of the second gear. The two segments are preferably displaceable relative to one another in the radial direction. Of course, a one-piece filler piece can also be provided. In this case, the internal gear fluid machine is uncompensated in the radial direction.

[0041] Particularly preferably, a gap existing between the segments is subjected to fluid pressure during operation of the fluid machine in such a way that the first segment is pushed towards the first gear and the second segment towards the second gear, so that the segments bear sealingly against the respective gear or the tooth tips of the corresponding toothing. The fluid machine is thus radially compensated or gap-compensated in the radial direction. Each of the segments can be further subdivided into segments. For example, the first segment is one-piece or consists of at least two segments and / or the second segment is one-piece or consists of at least two segments. These segments of the filler piece are also preferably mounted so that they can be displaced relative to one another, i.e. they can be displaced independently of one another. This achieves particularly effective gap compensation.

[0042] As an alternative to the filler piece, on the other side of the engagement region, i.e. again preferably on the side diametrically opposite the engagement region with respect to the first axis of rotation and / or the second axis of rotation, at least one tooth tip of the internal toothing and one tooth tip of the external toothing lie against one another in a sealing manner, in particular with a tip circle surface of the respective tooth delimited by the respective tip circle of the corresponding toothing. In other words, a tip circle surface of the tooth tip of the internal toothing is delimited by the tip circle of the internal toothing and a tip circle surface of the tooth tip of the external toothing is delimited by a tip circle of the external toothing. The tip circle surface of the internal toothing and the tip circle surface of the external toothing now lie against one another in a sealing manner. This in turn divides the fluid space into the first fluid chamber and the second fluid chamber.Each of the two fluid chambers is circumferentially delimited by the tight contact of the tip surfaces and by the tight meshing of the external and internal gears in the engagement area. This type of fluid machine can also be referred to as a gear ring fluid machine.

[0043] A further development of the invention provides that the pilot control recess and the further pilot control recess are arranged on opposite sides of the filler piece, viewed in the radial direction. In this way, the overlap of the respective pilot control recess with the teeth or inter-tooth spaces of the respective toothing is achieved in a simple manner. In particular, the pilot control recess and the further pilot control recess each overlap with the filler piece in the circumferential direction, in particular completely. This means that the pilot control recess lies in an angular range with respect to the first axis of rotation or extends across this, which is completely encompassed by the filler piece. In addition, the further pilot control recess lies in an angular range with respect to the second axis of rotation or extends across this, which is completely encompassed by the filler piece in the circumferential direction.Once again, the advantages described are achieved.

[0044] A further development of the invention provides that the control recess has two recess extensions, each extending from a base recess of the control recess, wherein the recess extensions are arranged on opposite sides of the filler piece as viewed in the radial direction, and the pilot control recess extends from a first of the recess extensions and the further pilot control recess extends from a second of the recess extensions. The recess extensions, together with the base recess, form the control recess; the control recess is therefore composed, in particular exclusively, of the base recess and the two recess extensions. Viewed in section, the recess extensions are connected to one another only via the base recess; apart from the base recess, they are continuously spaced from one another.

[0045] The recess extensions are arranged on opposite sides of the filler piece, so that the first recess extension overlaps the teeth or tooth spaces of the first toothing, and the second recess extension overlaps the teeth or tooth spaces of the second toothing. For example, the recess extensions have a radial extension that corresponds to at least 50%, at least 70%, or at least 90% of the difference between a tip circle and a root circle, or vice versa, of the respective toothing. This means that the respective pilot recess partially, completely, or at least almost completely overlaps the teeth or tooth spaces of the respective toothing in the radial direction.One of the pilot recesses extends from each of the recess extensions, namely the pilot recess from the first recess extension and the further pilot recess from the second recess extension. For example, it is provided that, viewed in the radial direction, the pilot recess is arranged in overlap with a base circle of the first toothing and / or the further pilot recess is arranged in overlap with a base circle of the second toothing. However, it can also be provided that, viewed in the radial direction, the pilot recess is arranged in overlap with the base circle of the first toothing, whereas the further pilot recess is located away from the base circle of the second toothing, i.e., precisely not in overlap.Conversely, it can be provided that, viewed in the radial direction, the pilot control recess is arranged away from the base circle of the first gearing, and the further pilot control recess is arranged in overlap with the base circle of the second gearing. The advantages described are achieved by means of such a design of the fluid machine.

[0046] A further development of the invention provides that a sealing surface is present on the control element in the radial direction between the pilot control recesses, which sealing surface bears sealingly against an end face of the filler piece. The sealing surface of the control element has already been mentioned. The sealing surface is preferably present at least partially between the recess extensions, in particular it extends between the recess extensions up to the base recess. With the sealing surface, the control element lies slidingly or sealingly against the end face of the filler piece and - preferably - also against the end faces of the gears. With the help of the control element or the control elements, at least one of the fluid chambers or both fluid chambers are closed in the axial direction. This enables a high level of efficiency of the fluid machine.

[0047] A further development of the invention provides that the sealing surface is penetrated by a fluid channel which is arranged to overlap with a gap present between segments of the filler piece. Reference has already been made to the gap arranged between the segments. This gap is at least temporarily pressurized with the pressurized fluid so that the segments are forced away from each other in the radial direction and towards the gear teeth. The gap is pressurized via the fluid channel, which is created for this purpose in the control element, namely in such a way that it penetrates the sealing surface. The sealing surface lies sealingly against the segments away from the fluid channel, so that a fluid connection is established between the fluid channel and the gap. This design of the fluid machine enables efficient gap compensation.A further development of the invention provides that, on the side of the control recess facing away from the pilot control recess in the circumferential direction, a control recess extension extends from the control recess, which immediately adjacent to the control recess has a smaller flow cross-sectional area and / or a smaller depth than the control recess immediately adjacent to the control recess extension. The control recess extension is similar to the pilot control recess with regard to the smaller flow cross-sectional area and / or the smaller depth. The control recess extension is preferably arranged such that it overlaps the teeth and inter-tooth spaces of both toothings in the radial direction, namely in particular in the engagement region.

[0048] For example, the control recess extension extends radially outwards as far as a tip circle of the first toothing and / or as far as a root circle of the second toothing. In the radial direction inwards it extends only over part of the difference between the tip circle diameter and the root circle diameter of the respective toothing, i.e. it only partially overlaps the teeth or tooth spaces of the respective toothing in the radial direction, in particular to a maximum of 50%, a maximum of 40% or a maximum of 30%. Particularly preferably it extends in the circumferential direction as far as a point at which the toothings engage with each other to the maximum. In this respect, the control recess extension also serves to set an advantageous behavior of the pressure build-up or pressure reduction.It can be provided that the control recess extension is designed analogously to the pilot control recess, and in this respect, a flow cross-sectional area of ​​the control recess extension has different rates of change in different control recess extension regions that follow one another in the circumferential direction. In this case, the corresponding embodiments for the pilot control recess are analogously applicable to the control recess extension.

[0049] The features and combinations of features described in the description, in particular the features and combinations of features described in the following description of the figures and / or shown in the figures, can be used not only in the respective combination specified, but also in other combinations or on their own, without departing from the scope of the invention. Thus, embodiments are also to be considered encompassed by the invention 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. The invention is explained in more detail below with reference to the starting examples shown in the drawings, without limiting the invention. In the drawings:

[0050] Figure 1 is a schematic representation of a fluid machine which is designed as an internal gear fluid machine and has a control element arranged next to two gears,

[0051] Figure 2 is a schematic representation of the control element,

[0052] Figure 3 is a schematic detailed representation of an area of ​​the control element, as well as

[0053] Figure 4 is a schematic sectional view of a portion of the control element.

[0054] Figure 1 shows a schematic representation of a fluid machine 1, which here is a gear fluid machine, in particular an internal gear fluid machine, and has a machine housing 2 in which a fluid conveying element designed as a first gear 3 and a second gear 4 are rotatably mounted. The first gear 3 is rotatably mounted in the machine housing 2 about a first axis of rotation 5 and the second gear 4 about a second axis of rotation 6. It can be seen that the first axis of rotation 5 and the second axis of rotation 6 are arranged parallel and spaced from one another, so that the first gear 3 and the second gear 4 have different axes of rotation. The first gear 3 has a first toothing 7 designed as an external toothing, and the second gear 4 has a second toothing 8 designed as an internal toothing, which mesh with one another in an engagement region 9, i.e., are in engagement with one another.

[0055] The first gear 3 and the second gear 4 together delimit a fluid chamber 10. The first gear 3 delimits the fluid chamber 10 in the radially inward direction and the second gear 4 in the radially outward direction. The fluid chamber 10 is divided circumferentially into a first fluid chamber 12 and a second fluid chamber 13 by the meshing of the gears 3 and 4 on the one hand and a filler piece 11 on the other. Depending on the direction of rotation of the fluid machine 1, one of the fluid chambers 12 and 13 serves as a suction chamber and another of the fluid chambers 12 and 13 serves as a pressure chamber. The filler piece 11 is designed in several parts and has several segments 14 and 15. Between the segments 14 and 15 there is a gap 16 which can be pressurized with fluid. This fluid loading forces segments 14 and 15 toward the respective gears 3 and 4, respectively. Thus, radial compensation of fluid machine 1 is achieved.Each of the fluid chambers 12 and 13 is fluidly connected to one of several fluid connections 17 and 18, namely the first fluid chamber 12 with the first fluid connection 17 and the second fluid chamber 13 with the second fluid connection 18. The fluid connections 17 and 18 are indicated here merely by way of example.

[0056] A control element 19 slides axially against the first gear 3, i.e., the fluid conveying element, and against the second gear 4, which can also be referred to as a further fluid conveying element. For this purpose, the control element 19 has a sealing surface 20 facing the gears 3 and 4. The sealing surface 20 bears against both the gears 3 and 4 and the filler piece 11. Preferably, the fluid machine 1 has a plurality of control elements 19, which in this case bear against the filler piece 11 on opposite sides of the gears 3 and 4. The following only discusses the control element 19. However, the explanations are of course applicable to each of the plurality of control elements 19.

[0057] The control element 19 can also be referred to as a sealing disc. It ultimately serves to tightly close at least one region of the fluid chamber 10 in the axial direction. The control element 19 is rotatably mounted on the machine housing 2 by means of a bearing pin (not shown here). For this purpose, the bearing pin extends through a bearing pin receptacle 21 of the control element 19, which is present, for example, as a circular through-passage. A control recess 22 is produced in the control element 19, which here is a depression open in the direction of the gears 3 and 4. The control recess 22 has a continuous control recess base 23, which runs uninterrupted across the entire control recess 22, thus continuously delimiting the control recess 22 in the direction away from the gears 3 and 4.

[0058] The control recess 22 is divided into several areas, namely a base recess 24, from which two recess extensions 25 and 26 originate. The recess extensions 25 and 26 are arranged at a distance from one another in the radial direction, with the sealing surface 20 extending between the recess extensions 25 and 26 and running as far as the base recess 24. A fluid channel 27 passes through the sealing surface 20 between the recess extensions 25 and 26, which is fluidically connected to the gap 16 and via which the gap 16 is at least temporarily subjected to a pressurized fluid. The recess extensions 25 and 26 run on opposite sides of the filler piece 11, viewed in the radial direction, namely the recess extension 25 radially on the inside and the recess extension 26 radially on the outside.

[0059] A pilot control recess 28 extends from the control recess 22, which can also be referred to as the first pilot control recess. Additionally or alternatively, a further pilot control recess 29 extends from the control recess 22, which is also referred to as the second pilot control recess. The pilot control recesses 28 and 29 extend from the recess extensions 25 and 26, namely the first pilot control recess 28 extends from the recess extension 25, and the second pilot control recess 99 extends from the recess extension 26. Both pilot control recesses 28 and 29 extend in the same circumferential direction from the control recess 22. Viewed in the radial direction, they overlap with the gears 7 and 8. Via the pilot control recesses 28 and 29, a pressure build-up or pressure reduction in the fluid machine 1 can be influenced and adjusted as desired.

[0060] Optionally, a control recess extension 30 extends from the control recess 22, namely in the circumferential direction on the side of the control recess 22 facing away from the pilot control recesses 28 and 29. The control recess extension 30 has a smaller flow cross-sectional area and / or a smaller depth on its side facing the control recess 22 than the control recess 22 on its side facing the toothed control recess 30.

[0061] Figure 2 shows a schematic detailed representation of the control element 19. It can be seen that the pilot control recesses 28 and 29 each penetrate a control recess edge 31 delimiting the control recess 22. They each have a smaller flow cross-sectional area and / or a smaller depth immediately adjacent to the control recess 22 than the control recess 22 immediately adjacent to the respective pilot control recess 28 or 29. It can also be seen that at least one of the pilot control recesses 28 and 29, in particular both pilot control recesses 28 and 29, each have a plurality of pilot control recess regions 32, 33 and 34 or 35, 36 and 37. Only the first pilot control recess 28 and thus the pilot control recess regions 32, 33 and 34 will be discussed below.However, the explanations are optionally transferable to the second pilot control recess 29 and thus the pilot control recess regions 34, 36, and 37. The pilot control recess 28 is delimited on the side facing away from the gears 3 and 4 by a pilot control recess base 38. In the radial direction and, optionally, in the circumferential direction, it is delimited on opposite sides by spaced-apart pilot control recess walls 39 and 40. A flow cross-sectional area of ​​the pilot control recess 28 now has different rates of change in the different pilot control recess regions 32, 33, and 34. In particular, it is provided that the rate of change in the first pilot control recess region 32 is smaller than that in the second pilot control recess region 33. The rate of change in the third pilot control recess region 34 is also smaller than that in the second pilot control recess region 33.Particularly preferably, the rates of change in the first pilot control recess region 32 and the third pilot control recess region 34 are identical or at least nearly identical. For example, the rate of change in the first pilot control recess region 32 and the third pilot control recess region 34 is zero or at least nearly zero. This is achieved by a parallel extension of the pilot control recess walls 39 and 40 and a constant depth of the pilot control recess 28 in these regions.

[0062] Figure 3 shows a schematic detailed representation of a region of the control element 19, specifically in the region of the first pilot control recess 28. It can be seen that in the first pilot control recess region 32, the pilot control recess walls 39 and 40 run parallel to one another, whereas in the second pilot control recess region 33, they converge in the direction away from the control recess 22, so that the flow cross-sectional area of ​​the pilot control recess 28 decreases at a specific rate of change in these regions. In the third pilot control recess region 34, however, the walls 39 and 40 are again spaced apart from one another by a constant or at least almost constant distance, namely up to an outlet region 41 of the pilot control recess 28.

[0063] Figure 4 shows a sectional view through the control element 19 in the region of the first pilot control recess 28. It can be seen that the depth of the pilot control recess 28 is consistently significantly less than the depth of the control recess 22. In particular, the depth of the pilot control recess 28 immediately adjacent to the control recess 22 is at most 50% as great as the depth of the control recess 22 immediately adjacent to the pilot control recess 28. Accordingly, at a transition between the control recess 22 and the pilot control recess 28, there is a step 42 between the control recess base 23 and the pilot control recess base 38. It can be seen that the depth of the pilot control recess 28 remains constant over the first pilot control recess region 32. In the second pilot control recess region 33, however, the depth decreases in the direction away from the control recess 22.In the third pilot recess region 34, the depth of the pilot recess 28 is either constant or it continues to decrease, but at a smaller rate of change than in the second.

[0064] Pilot control recess area 33. The outlet area 41 merely serves to close off the pilot control recess 28. It has significantly smaller dimensions in the circumferential direction than each of the other pilot control recess areas 32, 33, and 34; for example, its dimensions in this direction amount to at most 20%, at most 10%, or at most 5% of the dimensions of the third pilot control recess area 34.

[0065] With the described configuration of the fluid machine 1 and in particular of the control element 19, the pressure buildup or pressure reduction in the fluid machine 1 can be specifically influenced. This is achieved in particular in such a way that, during operation of the fluid machine 1, the fluid forces acting on its components are reduced compared to a conventional configuration of the control recess 22 and the pilot control recesses 28 and 29, thus resulting in an improvement in the service life of the fluid machine 1 and acoustic advantages.

[0066] LIST OF REFERENCE SYMBOLS

[0067] 1 fluid machine

[0068] 2 machine housings

[0069] 3 1. Gear

[0070] 4 2nd gear

[0071] 5 1. Axis of rotation

[0072] 6 2nd axis of rotation

[0073] 7 1. Gearing

[0074] 8 2. Gearing

[0075] 9 Intervention area

[0076] 10 Fluid chamber

[0077] 11 Filler piece

[0078] 12 1. Fluid chamber

[0079] 13 2. Fluid chamber

[0080] 14 segments

[0081] 15 segments

[0082] 16 gap

[0083] 17 1. Fluid connection

[0084] 18 2. Fluid connection

[0085] 19 Control

[0086] 20 Sealing surface

[0087] 21 Bearing bolt holder

[0088] 22 Control recess

[0089] 23 Reason for tax exemption

[0090] 24 Base recess

[0091] 25 recess extensions

[0092] 26 recess extensions

[0093] 27 Fluid channel

[0094] 28 1. Input tax exemption

[0095] 29 2. Before tax exemption

[0096] 30 Tax relief extension

[0097] 31 Control recess edge

[0098] 32 1. Input tax exemption area 33 2. Input tax exemption area

[0099] 34 3. Input tax exemption area

[0100] 35 1. Input tax exemption area

[0101] 36 2. Input tax exemption area 37 3. Input tax exemption area

[0102] 38 Reason for VAT exemption

[0103] 39 Pre-control recess wall

[0104] 40 Pre-control recess wall

[0105] 41 Run-off area 42 Step

Claims

CLAIMS 1. Fluid machine (1), having a fluid connection (17) of the A fluid machine (1) having a first fluid chamber (12) fluidically connected to a fluid connection (18) of the fluid machine (1) and a second fluid chamber (13) fluidly connected at least temporarily to a second fluid connection (18) of the fluid machine (1), as well as a fluid conveying element (3) rotatably mounted about a rotational axis (5), which at least partially delimits the first fluid chamber (12) and / or the second fluid chamber (13) and is provided and designed to convey a fluid from the first fluid chamber (12) in the direction of the second fluid chamber (13), and a control element (19) slidingly abutting the fluid conveying element (3), in which at least one control recess (22) is formed, which is open in the direction of the fluid conveying element (3), from which a pilot control recess (28) extends in the circumferential direction with respect to the rotational axis (5), which pilot control recess (28) is open in the direction of the fluid conveying element (3) and extends through an edge (31) of the control recess (22), characterized in thatthat a flow cross-sectional area of the pilot control recess (28) has different rates of change in different pilot control recess regions (32, 33, 34) which follow one another in the circumferential direction.

2. Fluid machine according to claim 1, characterized in that the pilot control recess (28) immediately adjacent to the control recess (22) has a smaller flow cross-sectional area and / or a smaller depth than the control recess (22) immediately adjacent to the pilot control recess (28).

3. Fluid machine according to one of the preceding claims, characterized in that the pilot control recess (28) is delimited by a pilot control recess base (38) and by opposite pilot control recess walls (39, 40).

4. Fluid machine according to one of the preceding claims, characterized in that in at least one of the pilot control recess areas (32, 33, 34) the Pilot control recess walls (39, 40) run parallel to each other.

5. Fluid machine according to one of the preceding claims, characterized in that in at least one of the pilot control recess areas (32, 33, 34) of the Pilot control recess base (38) runs parallel to an opening through which the pilot control recess (28) is opened in the direction of the fluid conveying element (3), so that the depth the pilot control recess (28) is constant over an extension of the pilot control recess area (32, 34).

6. Fluid machine according to one of the preceding claims, characterized in that in at least one of the pilot control recess areas (32, 33, 34) a rate of change other than zero due to a change in a distance between the pilot control recess walls (39, 40) over an extension of the pilot control recess region (33) and / or due to a change in the depth of the pilot control recess (28) over an extension of the pilot control recess region (33).

7. Fluid machine according to one of the preceding claims, characterized in that in a first of the pilot control recess areas (32, 33, 34) adjoining the control recess (22), a first rate of change of the Flow cross-sectional area and in a second of the pilot control recess areas (32, 33, 34) adjoining the first pilot control recess area (32) there is a second rate of change of the flow cross-sectional area, wherein the second rate of change is greater than the first rate of change.

8. Fluid machine according to one of the preceding claims, characterized in that a further one of the pilot control recess regions (32, 33, 34) adjoins one of the pilot control recess regions (32, 33, 34) on both sides, wherein the rate of change in the pilot control recess region (33) is greater than in the further pilot control recess regions (32, 34).

9. Fluid machine according to one of the preceding claims, characterized in that the rate of change in the further pilot control recess areas (33, 34) are identical or differ from one another by at most 50%, at most 25% or at most 10%.

10. Fluid machine according to one of the preceding claims, characterized in that the control recess (22) is at least temporarily fluidically connected to one of the fluid connections (17, 18).

11. Fluid machine according to one of the preceding claims, characterized in that from the control recess (22) in the circumferential direction with respect to the axis of rotation (5) at least a further pilot control recess (29) which is open in the direction of the fluid conveying element (3) and extends through an edge (31) of the control recess (22), wherein a flow cross-sectional area of the at least one further pilot control recess (29) has different rates of change in different pilot control recess regions (35, 36, 37) which follow one another in the circumferential direction.

12. Fluid machine according to one of the preceding claims, characterized in that the fluid machine (1) is a gear fluid machine and the fluid conveying element (3) is a first gear (3) with a first toothing (7) and the axis of rotation (5) is a first axis of rotation (5), wherein in addition to the first gear (3) there is a second gear (4) rotatably mounted about a second axis of rotation (6) with a second toothing (8) meshing with the first toothing (7).

13. Fluid machine according to one of the preceding claims, characterized in that the pilot control recess (28) and the at least one further pilot control recess (29) are arranged spaced apart in the radial direction.

14. Fluid machine according to one of the preceding claims, characterized in that in a first region, viewed in the circumferential direction, the first toothing (7) and the second toothing (8) engage with one another and in a second region, tooth tips of the first toothing (7) and the second toothing (8) bear against one another in a sealing manner in order to divide a fluid space (10) present between the first gear (3) and the second gear (4) into a first fluid chamber (12) and a second fluid chamber (13), or in that a filler piece (11) is arranged between the first gear (3) and the second gear (4) away from the first region, which filler piece bears on the one hand against the first toothing (7) and on the other hand against the second toothing (8) in order to divide the fluid space (10) present between the first gear (3) and the second gear (4) into the first fluid chamber (12) and the second fluid chamber (13).

15. Fluid machine according to one of the preceding claims, characterized in that the pilot control recess (28) and the further pilot control recess (29) are arranged on opposite sides of the filler piece (11) as seen in the radial direction.

Images