EP3287637A1 - Vane pump, fluid system and combustion engine - Google Patents

Abstract

A vane pump (12) comprises a stator (16) and a rotor (18) rotatably mounted within the stator (16), the rotor (18) distributing a base (22) and a plurality of over the circumference of the base (22) arranged wings (24) which in a radial direction with respect to a rotational axis (26) of the rotor (18) slidably held in the base body (22) and by means of a biasing member (28) of the rotor (18) against an inner side of the stator (16 ), whereby the wings (24) divide one of the stator (16) and the base body (22) limited delivery chamber (30) into a plurality of pressure chambers. According to the invention, the wings (24) are arranged and designed such that the volumes of at least two pressure chambers, based on the same orientation of these pressure chambers within the delivery chamber (30), are different. This results in an improved smoothness compared to a conventional generic vane pump.

Description

The invention relates to a vane pump with a stator and a rotatably mounted inside the stator rotor, wherein the rotor has a base body and a plurality of distributed over the circumference of the body arranged vanes, which in a radial direction with respect to a rotational axis of the rotor displaceable in the base body held and acted upon by an impingement element of the rotor against an inner side of the stator, whereby the wings subdivide a limited by the stator and the base pumping chamber into several pressure chambers. The invention further relates to a fluid system with such a pump and to an internal combustion engine having such a fluid system.

A lubricant pump in the form of a vane pump is for example from the DE 10 2005 034 712 A1 known. In this, in a conventional manner for vane pumps, a multi-wing rotor rotor mounted eccentrically within a stator, between which a sickle-shaped delivery chamber is formed, which is divided by the wings of the rotor into a plurality of pressure chambers, wherein the sizes of these pressure chambers within a revolution of Rotors initially increase, whereby a negative pressure is generated, which leads to a suction of lubricant through a correspondingly positioned pump inlet, and then reduce again, whereby an overpressure is generated, which leads to the desired delivery of the lubricant to the component to be lubricated. The stator itself is displaceably mounted within a housing of the vane pump, thereby providing the ability to change the size of the pressure chambers when fluidly connected to the pump inlet and the pump outlet. As a result, the delivery rate of the lubricant pump can be influenced.

In the vane pump according to the DE 10 2005 034 712 A1 the wings are integrated into the rotor such that the sizes of the pressure chambers limited by these, with respect to the respective same orientation within the delivery chamber, are substantially equal. This results in that at a constant rotational speed of the rotor, the course of the pressure, ie the gradient of the pressure increase, which leads to the ejection of the fluid to be delivered from a high pressure section of the pumping chamber, and the gradient of the pressure increase subsequent to the pressure increase, for suction of the fluid to be delivered leads to a low pressure section of the pumping chamber, for all of the pressure chambers is substantially identical. This leads to a relatively uniform pulsation of the fluid pressure, which leads on the one hand to a vibration excitation of coming into contact with the fluid components and on the other to a correspondingly widely fluctuating driving resistance of the vane pump for a corresponding drive. These effects of the operation of a vane pump can be summarized as smoothness of the vane pump defined.

From the DE 10 2010 023 068 A1 is a vane pump in the form of a pendulum slide pump is known in which the wings are pivotally mounted on an outer rotor and radially movable in an inner rotor, wherein the arrangement is asymmetrical with respect to the inner rotor. This should be able to achieve increased smoothness of the pendulum slide pump.

The invention had the object to improve a generic vane pump in terms of smoothness.

This object is achieved by means of a vane pump according to the patent claim 1. A fluid system with such a vane pump and an internal combustion engine with such a fluid system are subject matters of claims 9 and 10. Advantageous embodiments of the vane pump according to the invention and thus the fluid system according to the invention and the internal combustion engine according to the invention are objects of the further claims and / or emerge from the following description of Invention.

A generic vane pump comprises a stator and a rotor rotatably mounted within the stator, wherein the rotor has a base body and a plurality of distributed over the circumference of the base body arranged wings, which held in a radial direction with respect to a rotational axis of the rotor slidably in the base body and are acted upon by an impingement element of the rotor against an inner side of the stator, whereby the wings subdivide a limited space of the stator and the main body delivery chamber into a plurality of pressure chambers. According to the invention, such a vane pump is characterized in that the vanes are arranged and designed such that the volumes of at least two, preferably of all, pressure chambers are different with respect to the same orientation of these pressure chambers within the pumping chamber.

The different volumes of the pressure chambers lead to correspondingly different pressure profiles within these pressure chambers over one revolution of the rotor, so that overall a non-uniform pressure pulsation of the fluid conveyed by the vane pump is achieved. As a result, at least an excitation of vibrations of components coming into contact with the fluid can be kept low. Consequently, improved smoothness of a vane pump according to the invention compared to a conventional generic vane pump can result.

By stating that the vanes are "slidably retained in the body in a radial direction with respect to a rotational axis of the rotor," it is not to be understood that the vanes and / or the slidably receiving receptacles of the rotor have an exact radial orientation with respect to the axis of rotation of the rotor must have. Rather, an alignment is sufficient for this purpose, which comprises at least one such exactly radial direction component, wherein an orientation which deviates by a maximum of 20 °, preferably by a maximum of 10 ° from the exact radial orientation, is preferred.

The biasing element is preferably designed such that the wings are acted upon by the latter under elastic prestress against the inside of the rotor.

In principle, the unequal volumes of the pressure chambers can be achieved by different design measures alone or in combination with each other. For example, the wings may be oriented differently with respect to the axis of rotation or have different dimensions in the circumferential direction of the rotor. Preferably, however, it is provided that the circumferential distances between adjacent receptacles for the wings, which are formed in the base body, at least partially and preferably between all adjacent receptacles are different. For the wings or these radially movable recordings of the rotor thus a different pitch over the circumference of the rotor is provided. This represents a structurally particularly simple embodiment, by which the inventively different volumes of individual or all pressure chambers of the vane pump can be realized. In particular, this can also be made possible to design the wings themselves identical, whereby the manufacturing and assembly costs for such a vane pump can be kept low.

In a preferred development of such a vane pump according to the invention, it can also be provided that the maximum difference of the circumferential distances, relative to the angle enclosed by these, is at most 10 ° and preferably at most or as exactly as 7 °. It has been found that thereby the smoothness of the vane pump can be particularly improved because the difference in the circumferential distances and thus the difference in the volumes of the pressure chambers is already large enough to effectively reduce vibration excitation by a more uneven pressure pulsation, this Reduction of vibration excitation only slightly by a deteriorated smoothness of the rotor due to a deteriorated rotational symmetry of the rotor, resulting from the non-uniform distribution of the vanes over the circumference of the rotor, is compensated.

A vane pump according to the invention may preferably be designed such that its delivery rate is also adjustable independently of the rotational speed of the rotor. For this purpose, it can preferably be provided that the rotor is arranged to be displaceable with respect to the delivery space, i. by a relative displacement of stator and rotor, the size and / or the shape of the delivery chamber is changed. For this purpose, it can be particularly preferably provided that the rotor or the stator (directly or indirectly, i.e. with the interposition of at least one further element) with a housing of the vane pump limits a pressure chamber of variable size. The pressure chamber can be provided for introducing a fluid into it, wherein a defined relative arrangement between the stator and the rotor is established as a function of the level of the pressure of the fluid in the pressure chamber.

To form a vane cell pump according to the invention, which in a structurally simple and thus advantageous manner, a control or regulation of the specific delivery rate in response to a pressure of the fluid present in the pressure chamber allows, may preferably be provided that the rotor or the stator so on a spring element is supported, that an increase of the pressure chamber leads to an increasing bias of the spring element. The pressure of the fluid in the pressure space thus operates against a spring element, so that by a relative increase in the pressure, a displacement of the rotor or the stator with respect to the pumping chamber in the direction of increasing or decreasing the capacity can be realized, while a relative reduction of the pressure due then temporarily predominantly restoring force of the spring element leads to such a displacement of the rotor or stator, by which the delivery rate is changed accordingly differently.

A fluid system according to the invention comprises at least one vane pump according to the invention and at least one fluid circuit in which a fluid can be conveyed by means of the vane pump.

An internal combustion engine according to the invention comprises at least one fluid system according to the invention and an internal combustion engine integrated in the fluid circuit of the fluid system.

The fluid system may be, for example, a lubricant system, so that for an internal combustion engine according to the invention preferably a fluid connection between the low pressure section of the delivery chamber of the vane pump and a lubricant reservoir may be provided. Alternatively, the fluid system may be, for example, a cooling system of the internal combustion engine, wherein the fluid to be delivered may then in particular be a cooling fluid.

In a preferred refinement of the fluid system according to the invention, it can be provided that control and, in particular, regulation of the delivery rate of the vane pump can at least also take place by means of a control or regulating device, which can comprise a control valve, by which the pressure of a fluid in a pressure chamber of the vane pump, the rotor or the stator (directly or indirectly) bounded by a housing and having a variable size, is controllable.

Preferably, a self-regulation of the flow rate of the vane pump may be provided by means of the control valve, for which purpose the pressure of the fluid in the pressure chamber by means of the control valve in response to the pressure generated by the vane pump is controlled. For this purpose, the control valve may have a valve body which can be displaced in a valve housing, the valve body defining (directly or indirectly) with the valve housing a control pressure chamber of variable size which conducts fluid directly, or indirectly (ie with the interposition of a functional element influencing a flow of the fluid to a relevant extent) is connected to the high pressure portion of the delivery chamber of the vane pump. In a structurally simple and thus advantageous embodiment of such a control valve can then be provided that the valve body (directly or indirectly) is supported on a spring element such that an increase of the control pressure chamber leads to an increasing bias of the spring element.

Preferably, it may be provided that a fluid connection, via which the pressure chamber of the vane pump, controlled by the control valve, can be acted upon by the delivered fluid, downstream of a functional component influencing the flow of the fluid or the fluid itself, which is in particular a coolant. and / or cleaning device for the fluid can leave the fluid circuit. By a branch of a partial flow of the pumped fluid, by means of which a control or regulation of the delivery rate of the pump should be carried out using the control valve, downstream of such a cooling and / or cleaning device may affect the functionality of the control valve by a high fluid temperature and / or be avoided by contamination of the fluid.

In an internal combustion engine according to the invention, which has such a fluid system, the pressure of the fluid, which is applied to the control pressure chamber of the control valve, in particular be tapped in a fluid passage of the internal combustion engine, because in an operation of the internal combustion engine primarily the required supply of the internal combustion engine with the fluid can be used for the control or regulation of the flow rate of the vane pump.

Alternatively or in addition to a self-regulation of the delivery rate of the vane pump by means of the control valve may also be provided to actively actuate or influence the control valve, which in particular a (more) more accurate adjustment of the delivery to a variable demand of the fluid to be delivered can take place. For this purpose, in a preferred embodiment of the fluid system according to the invention, an actuator can be provided, by means of which the size of the control pressure chamber of the control valve can be changed.

A vane pump according to the invention may furthermore preferably comprise a pressure limiting valve, wherein an inlet of the pressure limiting valve is preferably connected directly to the high pressure section of the delivery chamber in a fluid-conducting manner. By means of such a pressure limiting valve, a limitation of the pressure on the high pressure side of the vane pump can be realized. For this purpose, it can be provided that an outlet of the pressure limiting valve is connected directly or indirectly in a fluid-conducting manner to the low-pressure section of the delivery chamber of the vane pump. Preferably, a discharge of a portion of the fluid via the then opened pressure relief valve in a fluid reservoir and, for example, a lubricant or coolant reservoir, which is fluidly connected to the low pressure section of the delivery chamber of the vane pump, may be provided.

The term "pump" or "vane pump" is according to the invention not only devices for conveying liquids but devices for conveying fluids in total, i. also of gases. Accordingly, it may be a vane pump according to the invention and also a compressor.

The indefinite articles ("a", "an", "an" and "an"), in particular in the patent claims and in the description generally describing the claims, are to be understood as such and not as numerical words. Corresponding to this concretized components are thus to be understood that they are present at least once and may be present more than once.

Fig. 1:

eine schematische Darstellung einer erfindungsgemäßen Brennkraftmaschine;

Fig. 2:

eine Detailansicht einer erfindungsgemäßen Flügelzellenpumpe; und

Fig., 3:

einen Grundkörper eines Rotors der Flügelzellenpumpe gemäß der Fig. 2.

The present invention will be explained in more detail with reference to embodiments shown in the drawings. In the drawings shows:

Fig. 1:

a schematic representation of an internal combustion engine according to the invention;

Fig. 2:

a detailed view of a vane pump according to the invention; and

Fig. 3:

a main body of a rotor of the vane pump according to the Fig. 2 ,

The Fig. 1 shows a schematic representation of an internal combustion engine according to the invention. This includes an internal combustion engine 10 and a fluid system according to the invention with a fluid circuit. The fluid circuit may be, for example, a lubricant circuit which, inter alia, serves to supply the internal combustion engine 10 with lubricant.

In the fluid circuit of the fluid system, a vane pump 12 according to the invention is further integrated, by which a fluid is conveyed in the fluid circuit. For this purpose, the vane pump 12 sucks the fluid from a fluid reservoir 58 and pushes it under increased hydraulic pressure in the downstream of the vane pump 12 arranged portion of the fluid circuit.

The vane pump 12 may according to the Fig. 2 be designed as changeable with respect to the specific delivery rate. For this purpose, this comprises a housing 14, within which a stator 16 which is of annular design in a section is pivotally mounted, wherein the stator 16 defines a cylindrical interior volume within which a rotor 18 is disposed.

In the internal combustion engine according to the Fig. 1 For example, the rotor 18 of the pump 12 is directly driven by the internal combustion engine 10 itself or with the interposition of a transmission. However, there is also the possibility of a different drive of the rotor 18, for example by means of a separate drive motor, which may be formed in particular by an electric motor.

The rotor 18 comprises, in addition to a drive shaft 20, a substantially cylindrical base body 22, which is non-rotatably connected to the drive shaft 20. Distributed over the circumference of the base body 22 are a plurality (seven in this case) of radially and parallel to the axis of rotation 26 of the rotor 18 extending slit-shaped receptacles 38 are provided, in each of which a wing 24 of the rotor 18 in the radial direction with respect to the axis of rotation 26 slidably is arranged. An arranged within the body 22, annular loading element 28, consisting of a relatively highly elastic material, such as an elastomer, acts on the wings 24 of the rotor 18 in the radial outward direction, whereby these with their relative to the spring member 28 distal end faces against the cylindrical inner volume limiting inner wall of the stator 16 are acted upon.

In all possible (pivoting) positions of the stator 16 within the housing 14 (possibly with the exception of a zero position in which the capacity of the vane pump 12 is zero despite a rotating drive of the rotor 16), the axis of rotation 26 of the rotor 18 is decentralized with respect to the longitudinal axis arranged the cylindrical inner volume. Characterized is delimited between the cylindrical inner volume limiting inner wall of the stator 16 and the lateral surface of the base body 22 of the rotor 18 a cross-section sickle-shaped delivery chamber 30 which is divided by means of the blades 24 of the rotor 18 in pressure chambers with cyclically variable size.

In the Fig. 2 an operating position of the vane pump 12 is shown, in which the eccentricity of the rotor 18 with respect to the cylindrical inner volume of the stator 16 is maximum, so that the lateral surface of the base body 22 of the rotor 18 at a peripheral portion of the inner wall of the stator 16 almost contacted. In the Fig. 2 this is the case approximately in that peripheral portion in which the lowermost blade 24 of the rotor 18 is positioned. This peripheral portion and the offset to this peripheral portion by 180 ° arranged circumferential portion represent those areas in which the delivery chamber 30 is basically divided by means of the wings 24 of the rotor 18 in a negative pressure section and an overpressure section.

In a rotary drive of the rotor 18 in a clockwise direction according to the Fig. 2 the section of the delivery chamber 30 shown on the left with respect to these circumferential sections represents the low-pressure section in which the radial width of the delivery chamber 30 increases continuously in the direction of rotation of the rotor 18, whereby in those pressure chambers bounded by the vanes 24 located in the negative-pressure section, a negative pressure is generated, which leads to a suction of fluid via a non-visible fluid inlet, which is arranged in the negative pressure portion of the delivery chamber 30. In contrast, the radial width of the reduced in the Fig. 2 right above pressure section, whereby the pressure of the fluid, which is present in the local pressure chambers, is increased. This leads to a displacement of this fluid over one in the Fig. 2 non-visible fluid outlet, which is arranged in the overpressure section of the delivery chamber 30.

Due to the maximum possible eccentricity of the rotor 18 with respect to the stator 16 according to the

Fig. 2 In the corresponding operating state of the vane pump 12, the respective size change in the negative pressure section and the overpressure section of the delivery chamber 30 is as large as possible. This results in a corresponding manner to a maximum specific delivery rate of the pump 12. In the direction of this position, the stator 16, which is mounted by means of a pivot joint 32 in the housing 14, acted upon by means of a pressure-biased spring element 34.

For a change or reduction of the specific delivery capacity of the stator 16 must under increasing bias of the spring element 34 from in the Fig. 2 pivoted position shown. This is done hydraulically by supplying fluid to a pressure space 36 at a pressure which, taking into account the area over which the pressure is effective, results in a force counteracting the restoring force of the spring element 34 which is temporarily greater than this restoring force. A pivoting of the stator 16 then takes place until an equilibrium of forces between the pressure-related force and the restoring force increasing with increasing prestressing of the spring element 34 is reached again.

A control or regulation of the specific capacity of the vane pump 12 is thus carried out by means of a variable hydraulic pressure in the pressure chamber 36, said hydraulic pressure by means of a corresponding fluid connection in a Section of the fluid circuit is tapped, the upstream or inside of the internal combustion engine 10, for example, in a fluid channel, which is integrated in a cylinder head or a cylinder housing of the internal combustion engine 10, and downstream of a fluid filter 40 is arranged (see. Fig. 1 ). In this case, a supply of fluid is controlled in the pressure chamber 36 by means of a control valve 42 which is integrated in the corresponding fluid connection.

The control valve 42 has a valve body 44 displaceable in the valve body 44 which defines a control pressure chamber 46 of variable size with the valve housing 44, said control pressure chamber 46 via a corresponding portion of the fluid connection with the corresponding portion of the fluid circuit and thus indirectly with the high pressure section of the vane pump 12th connected is. The hydraulic pressure of the fluid in the control pressure space 46 of the control valve 42 generates a force on the valve body, which counteracts a restoring force of a prestressed spring element 48 of the control valve 42. If this hydraulically generated force exceeds the restoring force of the spring element 48 as a result of a delivery of fluid through the vane pump 12 above the demand of the internal combustion engine 48 so that the control valve 42 is switched over, the first pressure chamber 36 is connected to the corresponding section of the fluid circuit. The thus generated relatively high hydraulic pressure in the pressure chamber 36 then leads to a pivoting of the stator 16 within the housing 14 of the vane pump 12 and thus to a reduction in the specific capacity of the vane pump 12 in response to the specific hydraulic pressure in the corresponding section of the fluid circuit , By means of the control valve 42 is thus realized a self-regulation of the specific delivery rate of the pump 12 in response to the hydraulic pressure of the funded by the vane pump 12 fluid.

In order to achieve as exact as possible an adaptation of the absolute delivery rate of the vane pump 12 to the fluid requirement of the internal combustion engine 10 (and possibly other components integrated into the fluid circuit), the control valve 42 can also be switched over by means of an actively activatable actuator 50. In this case, the activation of the actuator 50 can be effected in particular as a function of different (measured or determined in another way) operating parameters of the internal combustion engine by means of a control device, not shown, (in particular a motor control of the internal combustion engine).

In particular after a cold start of the internal combustion engine at relatively low ambient temperatures and consequently at a relatively high viscosity of the fluid (Relevant in particular with a lubricant), it may happen that the vane pump 12 due to a present at short notice or immediately after the cold start drive the engine 10 with relatively high operating speeds and in combination with the set by the spring element 34 position of the stator 16, the due to the relatively poor flowability of the fluid (lubricant) to a high hydraulic pressure in the high pressure section of the vane pump 12 and in the directly adjoining section of the fluid circuit (in particular in the section extending to the fluid filter 40), while the hydraulic pressure in that portion of the fluid circuit in which the fluid connection integrating the control valve 42 extends is significantly lower. This could lead to a relatively high load on the vane pump 12 and the fluid lines in the portion of the fluid circuit immediately adjacent to the vane pump 12 as well as unnecessarily high driving resistance for the internal combustion engine 10 generated by the vane pump 12. Since the hydraulic pressure in the portion of the fluid circuit in which the fluid line which integrates the control valve 42 is significantly lower than in the high-pressure section of the vane pump 12, no suitable regulation of the specific delivery rate of the vane pump 12 can take place via the hydraulic pressure in the pressure space 36 be achieved.

To avoid this disadvantage, a pressure limiting valve 52 is provided in direct and as short as possible a connection to the high pressure section of the delivery chamber 30. In the vane pump 12 according to the Fig. 2 the pressure relief valve 52 is integrated in the housing 14 of the vane pump 12 itself. The pressure limiting valve 52, which is preferably designed in the form of a simple check valve, opens when a limit value of the hydraulic pressure in the high pressure section of the delivery chamber 30 is exceeded, thereby redirecting a portion of the fluid delivered by the vane pump 12 back into the fluid reservoir 58.

The fluid filter 40 of the internal combustion engine according to the Fig. 1 is designed to bypass by means of a bypass 56 controlled via a bypass 56, in order to ensure an uninterrupted and sufficient supply of the internal combustion engine 10 with the fluid, in particular in the case of a blockage of the fluid filter 40.

In order to realize the best possible smoothness for the vane pump 12, the invention provides that the pressure chambers into which the delivery chamber 30 of the Wings 24 is divided, each based on the same orientation within the delivery chamber 30 with identical control position of the stator 16, have different volumes. The volumes of all of the seven pressure chambers are different. This is achieved in the present embodiment, characterized in that the circumferential distances of adjacent receptacles 38, which are formed within the main body 22 of the rotor 18 and which serve to receive a respective wing 24, are different, as in the Fig. 3 is shown. There it is shown that the circumferential distances of the receptacles 38, relative to the angles enclosed by these circumferential distances in each case above the axis of rotation 26, are between a minimum of 48 ° and a maximum of 55 °, with no equal circumferential distances being provided. Concretely, the total of seven circumferential distances are 48 °, 53 °, 49 °, 54 °, 50 °, 55 °, 51 ° (in the order of clockwise from the smallest circumferential distance). The maximum difference between the smallest circumferential distance and the largest circumferential distance, based on the angle enclosed by this, is therefore 7 °.

The different volumes of the pressure chambers lead to correspondingly different pressure profiles within these pressure chambers over one revolution of the rotor 18, so that overall a non-uniform pressure pulsation of the fluid conveyed by the vane pump 12 is achieved. As a result, an excitation of vibrations of components coming into contact with the fluid can be reduced, which results in relatively smooth running of the vane pump 12.

LIST OF REFERENCE NUMBERS

10

internal combustion engine

12

Vane pump

14

casing

16

stator

18

rotor

20

drive shaft

22

Basic body of the rotor

24

wing

26

Rotation axis of the rotor

28

Beaufschlagungselement of the rotor

30

delivery chamber

32

pivot

34

Spring element of the pump

36

pressure chamber

38

Recording of the main body

40

fluid filter

42

control valve

44

valve housing

46

Control pressure chamber

48

Spring element of the control valve

50

actuator

52

Pressure relief valve

54

check valve

56

bypass

58

fluid reservoir

Claims (10)

A vane pump (12) having a stator (16) and a rotor (18) rotatably mounted inside the stator (16), wherein the rotor (18) has a base body (22) and a plurality of circumferentially distributed over the base body (22) Having vanes (24) slidably retained in the body (22) in a radial direction with respect to a rotational axis (26) of the rotor (18) and against an inside of the stator (16) by a biasing member (28) of the rotor (18). whereby the vanes (24) subdivide a delivery space (30) delimited by the stator (16) and the main body (22) into a plurality of pressure chambers, characterized in that the vanes (24) are arranged and configured such that the volumes of at least two pressure chambers, based on the same orientation of these pressure chambers within the delivery chamber (30), are different. Vane pump (12) according to claim 1, characterized in that the volumes of all the pressure chambers are different. Vane pump (12) according to claim 1 or 2, characterized in that the circumferential distances between adjacent receptacles (38) for the wings (24) which are formed in the base body (22) are at least partially different. Vane pump (12) according to claim 3, characterized in that the circumferential distances between all adjacent receptacles (38) are different. Vane pump (12) according to claim 3 or 4, characterized in that the maximum difference of the circumferential distances, based on the angle enclosed by these, at most 10 ° and preferably at most or substantially exactly 7 °. Vane pump (12) according to one of the preceding claims, characterized in that the wings (24) are formed identically. Vane pump (12) according to one of the preceding claims, characterized in that the rotor (18) is arranged displaceable with respect to the delivery chamber (30). Vane pump (12) according to claim 7, characterized in that the rotor (18) or the stator (16) with a housing (14) defines a pressure chamber (38) of variable size. Fluid system with a vane pump (12) according to one of the preceding claims and with a fluid circuit in which a fluid by means of the vane pump (12) is conveyed. Internal combustion engine with a fluid system according to claim 9 and with an internal combustion engine (10) integrated in the fluid circuit.

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