WO2018141499A1

WO2018141499A1 - Hydraulic arrangement and motor-vehicle drive train

Info

Publication number: WO2018141499A1
Application number: PCT/EP2018/050185
Authority: WO
Inventors: Holger Berg; Harald Ihben; Mark Schweiher
Original assignee: GETRAG B.V. & Co. KG
Priority date: 2017-02-01
Filing date: 2018-01-04
Publication date: 2018-08-09
Also published as: DE102017101970A1

Abstract

A hydraulic arrangement (10) for a motor-vehicle drive train (40) which has a first hydraulic consumer (16; 52) and a second hydraulic consumer (18; 44), wherein the first consumer (16; 52) is supplied with a first fluid volume flow (Q1) as required, and wherein the second consumer (18; 44) is supplied with a second fluid volume flow (Q2) as required. The hydraulic arrangement comprises: a fluid supply device (12) which is designed to provide an overall fluid volume flow (QG); a distribution device (14) which is connected to the fluid supply device (12) and which is designed to distribute the overall fluid volume flow (QG), provided by the fluid supply device (12), such that the first consumer (16; 32) is supplied with the first fluid volume flow (Q1) and the second consumer (18; 44) is supplied with the second fluid volume flow (Q2). The distribution device (14) comprises a fluid volume flow limiting valve (30) having a securing member (88) connected to a valve housing (60) and a shut-off element (90) which is lifted in a first valve position (V2) from a valve seat (84) and which, in a second valve position (V1), rests on the valve seat (84). The shut-off element (90) is connected to the securing member (88) by means of at least one elastic radial arm (92).

Description

Hydraulic system and motor vehicle drive train

The present invention relates to a hydraulic system for a motor vehicle drive train having a first hydraulic consumer and a second hydraulic consumer, wherein the first consumer is to be supplied as needed with a first fluid volume flow and wherein the second consumer, if necessary, to provide a second fluid volume flow, wherein the Hydraulic assembly having a fluid supply device which is adapted to provide a total fluid volume flow, and having a distribution device which is connected to the fluid supply device and adapted to divide the provided by the fluid supply device total flow, so that the first consumer with the first fluid volume flow is supplied and the second consumer is supplied with the second fluid volume flow. Furthermore, the present invention relates to a drive train for a motor vehicle, with such a hydraulic arrangement.

Known hydraulic systems of the type described above use as

Distribution device often an electrically operated valve, which is controlled by means of a suitable control, for example by a drive train control unit such as a transmission control unit, to divide the total volume flow suitable. Such an electrically operated valve may be formed, for example, as a directional control valve.

From the document DE 10 2013 1 10 400 A1 it is known to connect a pressure port of a pump to an input of such a directional control valve, and to connect further connections of such a pump, which may for example contain a ring element, with hydraulic control ports of this valve to supply different hydraulic consumers as needed with fluid.

Further, this document discloses, in an internal gear pump with a

pivotable ring element to use this ring element as a valve spool.

Valves that are electrically driven require appropriate output connections to a controller. Pumps having a ring member which is pivotable between two different positions are comparatively expensive and complex to manufacture.

From the document DE 10 2009 023 596 A1 a volume flow control valve of a hydraulic system of a motor vehicle is known. The volume flow control valve disclosed therein should be suitable for blocking a volume flow. In particular, the valve has a control piston for influencing the volume flow, wherein the control piston has a first pressure surface and an opposite second pressure surface, wherein a hydraulic resistance of the first pressure surface downstream and the second pressure surface is connected upstream. The hydraulic resistance is a throttle or has their characteristics. As a result, a temperature compensation should be achievable. From the document US 6,443,183 B1, a check valve with a shut-off member of a sheet-metal disc is known. Furthermore, the document DE 103 10 039 A1 discloses a valve for adjusting a volume flow, with a flap which is pivotable by means of a spindle and has a rigid element and an elastic spring plate.

The document DE 10 201 1 009 214 A1 discloses a further check valve with a spring tongue whose deformation is limited by a stop.

The document US 2014/0216064 A1 discloses a valve element of a

Sheet material.

It is therefore an object of the invention to provide an improved hydraulic arrangement for a motor vehicle drive train, in which two fluid flow rates are as required by means of a distribution device as possible adjustable, in particular two different fluid volume distribution can be realized.

The above object is achieved in the above-mentioned hydraulic arrangement in that the distribution device comprises a fluid flow limiting valve having a valve housing connected to a fastening member and a shut-off, which is lifted in a first valve position of a valve seat and in a second valve position on the valve seat is applied, wherein the shut-off member is connected via at least one elastic radial arm with the fastening member.

Furthermore, the above object is achieved by a drive train for a motor vehicle, wherein the drive train has a hydraulic arrangement of the type according to the invention, wherein the first consumer is preferably an electric machine and / or wherein the second consumer is preferably a wet-running multi-disc clutch assembly.

A fluid volume flow limiting valve is in the simplest case a valve which, up to a certain volume flow limitation value, transmits any fluid volume flows. leaves, however, at least no further increase of the volume flow permits after reaching the limiting value of the volume flow.

The hydraulic arrangement preferably has a first branch, via which the first

Fluid volume flow is guided, and a second branch, via which the second fluid volume flow is guided.

In one case, the distribution device could thus ensure that the total fluid volume flow is divided according to the hydraulic resistances in the branches that lead the first and the second fluid volume flow, wherein in such a branch such a fluid volume flow limiting valve is arranged. As a result, it can be achieved that the volumetric flows divide in accordance with the hydraulic resistances, wherein, however, the ratio of the hydraulic resistances in the two branches changes upon reaching the limiting volumetric flow in the fluid volumetric flow limiting valve, so that a suitable distribution of the Total fluid volume flow is reached.

Of particular preference is when the fluid flow limiting valve is arranged in one of the two branches.

The fluid volume flow control valve is purely hydraulically controlled, so contains no external control, such as an electrical, pneumatic or mechanical control.

The fluid volume flow limiting valve is preferably connected so that it is flowed through by the first or the second fluid volume flow. Furthermore, it is preferred if the hydraulic control of the fluid volume limiting valve takes place via that connection of the fluid volume limiting valve which is connected to the fluid supply device.

The fluid volume flow limiting valve is preferably a

Such a flow control valve, where the flow is limited to a However, when this limiting volume flow or pressure is exceeded, the flow through the fluid volume flow limiting valve is limited to a value that is significantly smaller than the limiting volume flow, and for example can also close completely.

Such valves are also used, for example, for other purposes and are known as "tube place valves". Such Schlauchplatzventile be used, for example, when connecting household appliances to a water supply to a burst of the valve downstream hose and an increase in the volume flow flowing through a complete shutdown or blocking this volume flow to avoid unwanted water leakage over long periods.

In a preferred embodiment, the fluid flow restriction valve may include a main and a sub-fluid path, which is preferably arranged in parallel to the main fluid path. In this case, a spring may preferably hold the valve in an open state at low volume flows, so that the main fluid path and the secondary fluid path are flowed through. With increasing volume flow or pressure, flow forces and dynamic pressure increase, blocking the main fluid path. In this way, the volume flow can be reduced to that consumer, within the path of which such a fluid volume flow limiting valve is arranged, where the volume flow to the other consumer increases.

The secondary fluid path does not necessarily have to be present, but may also not be present, so that the fluid volume flow limiting valve only contains a main fluid path, which is flowed through at low volume flows, and is completely blocked when a limiting volume flow or a restriction dynamic pressure is reached. If a secondary fluid path is present, this can be formed for example by a throttle or a diaphragm. By the measure to connect a valve housing connected to a fastening member and a shut-off member via an elastic radial arm with each other, the fluid volume flow limiting valve can be produced inexpensively.

Preferably, no spring is necessary in the fluid volume flow limiting valve to bias the shut-off member into a valve position. The first valve position preferably results from a position of the shut-off member which it assumes with respect to the fastening member when the elastic radial arm is not elastically deflected. The valve positions are preferably axial valve positions.

In addition, such a valve arrangement has no contamination sensitive

Guide surfaces on, since the shut-off is suspended via the at least one elastic radial arm on the fastening member.

Due to the absence of guide surfaces no gap filtration takes place. It eliminates the risk of sticking. Furthermore, the inertial mass of the Absperrgliedes is relatively low. In addition, the valve assembly can be realized with low friction, whereby a hysteresis between opening and closing of the valve can be significantly reduced.

The task is thus completely solved.

Preferably, the fastening member and / or the shut-off member is designed as a flat annular disk or as a flat circular disk.

The disc shape is preferably installed in the valve housing so that it is aligned transversely to a flow direction through the valve.

Further, it is advantageous if in the shut-off member an opening is formed, which establishes a secondary volume flow through the fluid volume flow limiting valve when the shut-off member is in the second valve position. Thus, in this embodiment, the fluid flow restricting valve includes a main fluid path and a sub-fluid path. In the first valve position, both the main and sub-fluid paths are open. In the second valve position, only the secondary fluid path is opened.

The opening may be formed as a diaphragm. Preferably, the opening is central

Opening formed in the shut-off, which is preferably formed in this case as a flat circular disk.

According to a further preferred embodiment, the obturator and the

Attachment member connected to each other via at least three radial arms.

The three radial arms are preferably evenly distributed over the circumference.

Preferably, the valve assembly has exactly three radial arms.

According to a further preferred embodiment, the radial arms are each connected via a fastening member connecting portion with the fastening member and a shut-off member connecting portion with the shut-off member, wherein the radial arms each tangentially between an associated fastening member connecting portion and an associated Absperrglied connecting portion ,

By this measure, a relatively large length of the radial arm can be realized at a relatively small radial size of the valve assembly.

This allows the use of relatively robust or rigid materials for the

Valve assembly.

Furthermore, it is altogether advantageous if the fastening member, the shut-off member and the at least one radial arm are integrally formed as a valve element. The radial arm is in particular as a solid-state spring or solid-state joint

educated.

It is advantageous if the valve element is designed as a stamped part and / or if the valve element is made of a spring steel.

In this way, the valve element can be produced inexpensively.

Of particular preference it is in the hydraulic arrangement according to the invention, when the fluid flow rate limiting valve is connected such that in the first valve position, a first ratio of first to second fluid volume flow is established, and if in the second valve position, a second ratio of first to second fluid volume flow is set up.

The first and second ratios are different from each other. Preferably, the conditions are such that the one fluid volume flow of the first and second fluid volume flow in the first valve position is greater than the other fluid volume flow, and that it is exactly the other way around in the second valve position, so that the other fluid volume flow is greater than the first-mentioned fluid volume flow.

According to another preferred embodiment, as mentioned above, the

Fluid volume flow limiting valve flowed through by the first fluid volume flow or by the second fluid volume flow.

Overall, it is also advantageous if the shut-off member so in the valve housing

is installed, that it is acted upon in operation by a biasing pressure, wherein the shut-off member is movable when a threshold value of the biasing pressure from the first valve position against elastic deformation of the at least one radial arm in the second valve position, preferably axially movable. The admission pressure may be, for example, a function of the total volume flow and / or be a function of a rotational speed of a pump motor which drives a pump of the fluid supply device.

The admission pressure can act in particular on the shut-off member and the at least one radial arm. When the apply pressure reaches the threshold, the shut-off member is pushed to the second valve position. When the application pressure decreases again, the shut-off member is moved back to the first valve position due to the elastic restoring forces of the radial arm.

In some embodiments, it is advantageous if, when a return from the second valve position to the first valve position is desired, a fluid supply device reduces the apply pressure well below the threshold to cause the obturator to safely re-engage due to the elastic return forces of the radial arm the first valve position comes back.

The distribution device can be realized inexpensively, since only one valve is necessary, which is preferably also purely hydraulically driven and consequently does not occupy an output of a control unit. Also, a pump may be formed in the fluid supply device as a simple pump without ring element or envelope ring. The pump can also be a unidirectional pump. The pump of the fluid supply device is preferably driven by an electric motor.

To open the valve, i. for offsetting from the second valve position to the first valve position, it is advantageous if such an electric motor of a pump of the fluid supply device is stopped or operated backwards.

In the drive train according to the invention, the first load is preferably an electric machine, in particular an electric drive machine that provides drive torque for the motor vehicle. As a rule, this is permanently flowed through, preferably in the first valve position of the fluid volume limiting valve. As long as drive power is required, therefore, the electric machine is cooled with a relatively large volume flow, and a flow of a wet-running multi-plate clutch, which preferably forms the second consumer, is relatively low. During the provision of drive power such a multi-plate clutch assembly is usually closed or opened, so that a high cooling capacity in the multi-plate clutch assembly is not required.

On the other hand, if such a high cooling capacity is required, if so

For example, a gear change takes place in which the multi-plate clutch assembly is operated in the slip, the total volume flow is increased, whereby the fluid volume flow limiting valve is preferably switched from the first valve position to the second valve position, so that now promotes much of the total volume flow to the wet-running multi-disc clutch assembly becomes.

It is therefore particularly advantageous in the drive train according to the invention if the fluid volume flow limiting valve is arranged in that fluid path via which the first fluid volume flow is conducted to the electric machine.

In general, it is also conceivable to arrange such a fluid volume flow limiting valve in the path which is associated with the wet-running multi-disc clutch assembly. In this case, however, a sudden increase in volume flow in the direction of the wet-running multi-disc clutch arrangement can generally not be realized so easily.

The electric machine may preferably be reduced in power or even switched off in phases of such slipping operation of the multi-plate clutch assembly, so that the cooling fluid volume flow required in the electric machine during such periods of time is reduced.

Overall, the hydraulic arrangement is preferably used for cooling or lubricating hydraulic consumers, wherein the first consumer or the second consumer can also be another component of the drive train, such as a stepped transmission, a continuously variable transmission, or even a final drive or the like. It is understood that the above and the still to

explanatory features are usable not only in the combination given, but also in other combinations or alone, without departing from the scope of the present invention.

Embodiments of the invention are illustrated in the drawings and are explained in more detail in the following description. Show it:

Fig. 1 is a schematic representation of an embodiment of a hydraulic arrangement according to the invention;

FIG. 2 shows a schematic illustration of an embodiment of a drive train according to the invention; FIG.

3 is a graph of volumetric flow (for example in l / min) versus a rotational speed of a drive motor of a pump of a fluid supply device;

Fig. 4 is a schematic longitudinal sectional view through an embodiment of a

Fluid volume flow limiting valve for a hydraulic arrangement according to the invention;

5 shows a plan view of a valve element in the form of a stamped part for the fluid volume flow limiting valve of FIG. 4;

FIG. 6 shows a view comparable to FIG. 4 with a representation of the volume flow through the fluid volume limiting valve in the first valve position; FIG. and

Fig. 7 is a comparable to FIG. 6 representation of a flow through the

Fluid volume flow limiting valve in the second valve position. In Fig. 1 is an embodiment of a hydraulic arrangement according to the invention

represented and generally designated 10.

The hydraulic assembly 10 includes a fluid supply device 12 configured to provide a total variable fluid flow Q _G. The hydraulic assembly 10 further includes a distribution device 14 configured to divide the total fluid volume flow Q _G provided by the fluid supply device 12 into a first fluid volume flow Qi for a first hydraulic consumer 16 and a second fluid volume flow Q ₂ for a second hydraulic fluid Consumer 18.

The first hydraulic consumer 16 is preferably an electrical

Driving machine of a motor vehicle drive train. The second hydraulic consumer 18 is preferably a wet-running multi-plate clutch of a drive train of a motor vehicle.

The consumers 16, 18 are shown in Fig. 1 schematically as diaphragms or hydraulic

Resistors shown.

The ratio of the fluid volume flows Qi, Q ₂ depends largely on the hydraulic resistances R _; R ₂ , which are set up in a first fluid path or a second fluid path, in which the fluid volume flows Qi, Q _{2 are} guided.

The fluid supply device 12 preferably has a pump 20, which may be designed as a unidirectional pump, but may also be designed as a bidirectional pump. The pump 20 has a suction port connected to a fluid sump 22 or other low pressure fluid source. Further, the pump 20 includes a pressure port to which the total fluid volume flow Q _{G is} provided. The pump 20 is driven by an electric motor 24 which rotates at a speed n, wherein the speed n can be variably adjusted.

Consequently, the total volume flow Q _{G can be} variably adjusted. In the path leading from the pressure port of the pump 20 to the first hydraulic consumer 16, a fluid flow limiting valve 30 is arranged. This fluid volume flow limiting valve 30 is switched on reaching a limiting volume flow Q _s by the first fluid volume flow from a first valve position to a second valve position.

In the second valve position, the flow through the fluid volume flow limiting valve 30 is limited to a value below that volume flow value which has flowed through the fluid volume flow limiting valve 30 before reaching the limiting volume flow.

Thus, the ratio Q ₁ / Q ₂ may vary from first to second fluid flow alone

be changed by reaching a limiting fluid volume flow, in particular be reversed.

In the first valve position of the fluid volume flow limiting valve 30, therefore, a preferably larger volume flow is provided to the first hydraulic consumer 16, so that Qi> Q ₂ . When the fluid flow restriction valve 30 is in the second valve position, Q ₂ > Qi is preferably valid.

In Fig. 2, a powertrain 40 is shown for a motor vehicle, which includes a first drive motor 42, for example in the form of an internal combustion engine, and a clutch assembly 44, which may be formed as a single or double clutch assembly, but preferably at least one wet-running multi-disc clutch , An output of the clutch assembly 44 is connected to an input of a gear assembly 46. An output of the gear assembly 46 is connected to a differential 48, by means of which drive power can be distributed to driven wheels 50L, 50R.

The powertrain 40 further includes an electric machine 52, referred to as

Drive motor is operable to provide drive power. The drive train 40 further includes a hydraulic arrangement 10, which provides a first cooling fluid volume flow Qi for the electric machine 52, and provides a second fluid volume flow Q ₂ for the wet running multi-plate clutch of the clutch arrangement 44. The hydraulic arrangement 10 preferably corresponds in terms of construction and mode of operation to the hydraulic arrangement 10 described with reference to FIG. 1.

FIG. 3 shows the operation of a fluid flow restricting valve 30 as used in the hydraulic system 10 of FIG. 1. FIG. 3 shows a graph of volumetric flow (for example in l / min) versus the rotational speed n of the electric motor 24 which drives the pump 20.

The total volume flow Q _G increases linearly as the speed n of the pump 20 increases. This representation is idealized. In practice, other characteristics can be set up.

Up to a speed n _s , the total fluid volume flow Q _G by means of

Distributor 14 divided into a first fluid volume flow Qi and a second volume flow Q ₂ , wherein Qi is preferably greater than Q ₂ . When the speed n _{s is} exceeded, the first fluid volume flow Qi exceeds a restriction fluid flow Q _s , causing the fluid flow restriction valve 30 to be switched from the basic valve position to a switching valve position. As a result, the first fluid volume flow Qi is limited, in such a way that the total fluid volume flow Q _{G is} now divided into a smaller first fluid volume flow and a larger second fluid volume flow Q ₂ .

Upon reaching the speed n _s , consequently, the fluid volume flow, the

wet running multi-plate clutch of the clutch assembly 44 is supplied, abruptly increase in order to provide a high cooling capacity in the event of a brief slipping operation.

In the following FIGS. 4 to 7, an embodiment of a fluid volume flow limiting valve is shown, which in terms of construction and operation generally the The above-described fluid flow limiting valve 30 corresponds. The same elements are therefore identified by the same reference numerals. Essentially differences are explained below.

The fluid volume limiting valve 30 shown in FIGS. 4 and 5 has a housing 60. The housing 60 may be part of a powertrain housing. Through the fluid volume flow limiting valve 30 through a volume flow Qi is established.

The housing 60 has a first housing part 62, which is formed concentrically to an axis 64. The first housing part 62 has a disk formed transversely to the axis 64, in the middle of which an inflow opening 66 of the valve 30 is formed. From the circular disk of the first housing part 62, an annular projection extends in the axial direction, so that the first housing part 62 defines a first fluid space 68 radially inside the annular projection.

The housing 60 further includes a second housing part 70. The second housing part 70 has an annular flange 72 which completely overlaps the first housing part 62. The annular flange 72 extends from a housing disc of the second housing part 70, which is arranged concentrically to the axis 64 and aligned transversely thereto. In the housing disc of the second housing part 70, a drain opening 74 is centrally formed.

The valve 30 further includes a valve element 66 which is defined between a radial shoulder 78 of the second housing part 70 and a radial end face 80 of the annular projection of the first housing part 62.

Radially within the radial shoulder 78 of the second housing part 70, a second fluid space 82 is formed. The second fluid space 82 is bounded by an annular surface extending transversely to the axis 64, which is formed around the drainage port 74. This annular surface is designed as a valve seat 84. The valve element 76, which is shown in a plan view in FIG. 5, includes an annular attachment member 88 which is clamped in the assembled state between the annular projection of the first housing part 62 and the second housing part 70. Furthermore, the valve element 76 has a shut-off member 90, which is formed as a circular disk radially within the annular attachment member 88. The blocking member 90 and the fastening member 88 are connected to each other via three radial arms 92.

Each radial arm has a fixing member connecting portion 92a to which the radial arm is connected to the fixing member 88, and a blocking member connecting portion 92b to which the radial arm 92 is connected to the blocking member 90. The radial arms each extend approximately in the tangential direction between an associated attachment member connection portion 92a and an associated obturator connection portion 92b.

Centrally in the shut-off member an opening 94 is formed, which may be realized in the manner of a diaphragm. Between the shut-off member 90, the shut-off member 88 and the radial arms 92 flow openings 96 are further formed, which together form a flow cross-section which is at least 10 times, in particular 20 times, preferably at least 30 times as large as a cross section of the central opening 94th

The valve element 76 is preferably made of spring steel and is preferably formed as a stamped part.

The fastening member, the shut-off member and the radial arms of the valve element 76 are therefore preferably formed integrally with each other.

In Fig. 6, the pressure relief valve of Figures 4 and 5 in the first valve position V _! shown.

The obturator is aligned with the attachment member 88 in a plane transverse to the axis 64. A volume flow flowing in via the inflow opening 66 passes through the flow openings 96 and through the central opening 94 and that towards the outflow opening 74th

Preferably, the cross section of the inflow opening 66 is smaller than or equal to the cross section of the outflow opening 74.

Due to the volume flow Qi acts on the shut-off member 90, an axial pressure in

Fig. 6 is shown at PB. However, the pressure PB is so small at the volume flow Qi that the shut-off member 90 is held in position due to the spring forces of the radial arms 92.

However, when the pressure PB increases, due to a higher inflow

Volume flow Qi, as shown in Fig. 7, this biasing pressure PB, which in this case is above a threshold value (corresponding to PB _S in Fig. 3) deflects the shut-off member 90 in the axial direction relative to the fixing member 88 and pushes the shut-off member 90th Accordingly, fluid can no longer flow through the flow openings 96, which are covered in this case by the valve seat 84.

Consequently, only a relatively small volume flow can flow through the central opening 94 in this state.

The characteristic curve of this volume flow limiting valve of FIGS. 4 to 7 corresponds to FIG

Characteristic Qi of FIG. 3.

Claims

claims

1 . A hydraulic system (10) for a motor vehicle drive train (40) having a first hydraulic consumer (16; 52) and a second hydraulic consumer (18; 44), said first consumer (16; 52) having a first fluid volume flow (Qi) as needed. and wherein the second consumer (18; 44) is to be supplied, as needed, with a second fluid volume flow (Q ₂ ), the hydraulic arrangement comprising: a fluid supply device (12) which is designed to supply a total fluid volume flow (Q _G ) to provide; a distribution device (14) which is connected to the fluid supply device (12) and designed to divide the total fluid volume flow (Q _G ) provided by the fluid supply device (12) so that the first consumer (16; 32) communicates with the first Fluid volume flow (Qi) is supplied and the second load (18; 44) is supplied with the second fluid volume flow (Q ₂ ); characterized in that the distribution means (14) comprises a fluid flow restricting valve (30) having a mounting member (88) connected to a valve housing (60) and a shut-off member (90) disposed in a first valve position (V ^ of a valve seat (84) ) is lifted and in a second valve position (V ₂ ) against the valve seat (84), wherein the shut-off member (90) via at least one elastic radial arm (92) with the fastening member (88) is connected.

2. Hydraulic arrangement according to claim 1, characterized in that the fastening member (88) and / or the shut-off member (90) is designed as a flat annular disk or as a flat circular disk.

3. Hydraulic arrangement according to claim 1 or 2, characterized in that in the shut-off member (90) has an opening (94) is formed, which establishes a blocking volume flow through the fluid flow limiting valve (30) when the shut-off member (90) in the second Valve position (V ₂ ) is located.

4. Hydraulic arrangement according to one of claims 1 - 3, characterized in that the shut-off member (90) and the fastening member (88) via at least three radial arms (92) are interconnected.

5. A hydraulic arrangement according to claim 4, characterized in that the radial arms (92) are each connected via a fastening member connecting portion (92 a) with the fastening member (88) and via a Absperrglied-connecting portion (92 b) with the Absperrglied (90), wherein the radial arms (92) each extend tangentially between an associated fastener link portion (92a) and an associated cutoff link portion (92b).

6. Hydraulic arrangement according to one of claims 1-5, characterized in that the fastening member (88), the shut-off member (90) and the at least one radial arm (92) are integrally formed as a valve element (76).

7. Hydraulic arrangement according to claim 6, characterized in that the valve element (76) is formed as a stamped part and / or the valve element (76) is made of a spring steel.

8. Hydraulic arrangement according to one of claims 1-7, characterized in that the fluid volume flow limiting valve (30) is connected such that in the first valve position (V ^ a first ratio of the first fluid volume flow (Qi) to second fluid volume flow (Q ₂ ) is established and in the second valve position (V ₂ ) a second ratio of the first fluid volume flow (Qi) to the second fluid volume flow (Q ₂ ) is established.

9. Hydraulic arrangement according to one of claims 1-8, characterized in that the shut-off member (90) is installed in the valve housing (60), that it is acted upon in operation by a loading pressure (PB), wherein the obturator (90) at Exceeding a threshold value (PB _S ) of the application pressure (PB) from the first valve position (V ^ against an elastic deformation of the at least one radial arm (92) in the second valve position (V ₂ ) is movable.

10. Drive train (40) for a motor vehicle, with a hydraulic arrangement (10) according to one of claims 1 - 9, wherein the first load is preferably an electric machine (52) and / or wherein the second load is preferably a wet-running multi-plate clutch arrangement (44). is.

1 1. Valve element (76) for a hydraulic arrangement (10), in particular a hydraulic arrangement according to one of Claims 1 to 9, having a fastening element (88) and a blocking element (90) which is connected to the fastening element (88) via at least one elastic radial arm (92). connected is.