DE102017101970A1 - Hydraulic assembly and motor vehicle powertrain - Google Patents

Abstract

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 (Q) as needed. and wherein the second consumer (18; 44) is to be supplied, as needed, with a second fluid volume flow (Q), the hydraulic assembly comprising: a fluid supply means (12) adapted to provide a total fluid volume flow (Q) put; a distribution device (14) which is connected to the fluid supply device (12) and adapted to divide the total fluid volume flow (Q) provided by the fluid supply device (12) so that the first consumer (16; 32) communicates with the first fluid volume flow (Q) is supplied and the second consumer (18; 44) is supplied with the second fluid volume flow (Q). In this case, the distribution device (14) has a fluid volume flow limiting valve (30) that has a valve housing (60) connected to the fastening member (88) and a shut-off member (90) in a first valve position (V) of a valve seat (84) lifted is and in a second valve position (V) against the valve seat (84), wherein the shut-off member (90) via at least one elastic radial arm (92) is connected to the fastening member (88).

Description

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 arrangement 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 arrangements of the type described above often use as distribution device 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 110 400 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 ports of such a pump, which may include, for example, a ring member, with hydraulic control ports of this valve to supply different hydraulic consumers, if necessary, with fluid.

Further, this document discloses, in an internal gear pump with a pivotable ring member, to use this ring member 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 Pat. No. 6,443,183 B1 is a check valve with a shut-off of a sheet metal disc known. Further, the document discloses DE 103 10 039 A1 a valve for adjusting a volume flow, with a flap which is pivotable by means of a spindle and having a rigid element and an elastic spring plate.

The document DE 10 2011 009 214 A1 discloses another check valve with a spring tongue whose deformation is limited by a stop.

The document US 2014/0216064 A1 discloses a valve element made of a sheet metal 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 is up to a certain volume flow limiting value passes any fluid volume flows, however, at least does not allow any further increase in the volume flow from 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, which 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.

It is particularly advantageous if the fluid volume limiting valve is arranged in one of the two branches.

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

The fluid volume flow limiting valve is preferably connected so as to flow through 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 the connection of the fluid volume limiting valve which is connected to the fluid supply device.

The fluid volume flow limiting valve is preferably such a fluid flow limiting valve, in which the flow rate behaves like an open path up to a limiting volume flow and / or pressure at the valve inlet; if this limiting volume flow or pressure is exceeded, the flow through the flow rate valve is exceeded Fluid volume flow limiting valve, however, is limited to a value that is significantly smaller than the limiting volume flow, and can close completely, for example.

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 boundary back 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, since the shut-off member 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 formed as a central opening in the shut-off, which is preferably formed in this case as a flat circular disk.

According to a further preferred embodiment, the shut-off member and the fastening member are 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 to the fastening member via a fastening member connecting portion and to the blocking member via a shut-off member connecting portion, the radial arms each extending tangentially between an associated fastening member connecting portion and an associated locking member 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 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 designed in particular as a solid-state spring or solid-state joint.

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.

It is of particular advantage in the hydraulic arrangement according to the invention if the fluid volume flow limiting valve is connected in such a way that a first ratio of first to second fluid volume flow is set in the first valve position, and if a second ratio of first to second fluid volume flow is established in the second valve position.

The first and second ratios are different. 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 a further preferred embodiment, as mentioned above, the fluid volume flow limiting valve flows through the first fluid volume flow or the second fluid volume flow.

Overall, it is also advantageous if the shut-off member is installed in the valve housing, that it is acted upon by a loading pressure in operation, wherein the shut-off when exceeding 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 is movable, 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. This is usually flowed through permanently, 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 volume 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, that is, 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 now a large part the total volume flow is promoted to the wet-running multi-disc clutch assembly.

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 features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

• 1 eine schematische Darstellung einer Ausführungsform einer erfindungsgemäßen Hydraulikanordnung;
• 2 eine schematische Darstellung einer Ausführungsform eines erfindungsgemäßen Antriebsstranges;
• 3 ein Diagramm von Volumenstrom (beispielsweise in l/min) über einer Drehzahl eines Antriebsmotors einer Pumpe einer Fluidversorgungseinrichtung;
• 4 eine schematische Längsschnittansicht durch eine Ausführungsform eines Fluidvolumenstrombegrenzungsventils für eine erfindungsgemäße Hydraulikanordnung;
• 5 eine Draufsicht auf ein Ventilelement in Form eines Stanzteiles für das Fluidvolumenstrombegrenzungsventil der 4;
• 6 eine der 4 vergleichbare Ansicht mit einer Darstellung des Volumenstroms durch das Fluidvolumenstrombegrenzungsventil in der ersten Ventilstellung; und
• 7 eine der 6 vergleichbare Darstellung eines Volumenstromes durch das Fluidvolumenstrombegrenzungsventil in der zweiten Ventilstellung.

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

• 1 a schematic representation of an embodiment of a hydraulic arrangement according to the invention;
• 2 a schematic representation of an embodiment of a drive train according to the invention;
• 3 a diagram of volume flow (for example in l / min) over a speed of a drive motor of a pump of a fluid supply device;
• 4 a schematic longitudinal sectional view through an embodiment of a fluid flow limiting valve for a hydraulic arrangement according to the invention;
• 5 a plan view of a valve element in the form of a stamped part for the fluid flow rate limiting valve of 4 ;
• 6 one of the 4 comparable view with a representation of the volume flow through the fluid flow rate limiting valve in the first valve position; and
• 7 one of the 6 comparable representation of a volume flow through the fluid volume flow limiting valve in the second valve position.

In 1 an embodiment of a hydraulic arrangement according to the invention is shown and generally designated 10.

The hydraulic system 10 includes a fluid supply device 12 configured to provide a variable total fluid flow Q _G. The hydraulic system 10 further includes a distribution device 14 , which is adapted to that of the fluid supply device 12 divided total fluid flow Q _{G to} be divided, in a first fluid volume flow Q ₁ for a first hydraulic consumer 16 and a second fluid volume flow Q ₂ for a second hydraulic consumer 18 ,

The first hydraulic consumer 16 is preferably an electric drive 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 in 1 shown schematically as diaphragms or hydraulic resistors.

The ratio of the fluid volume flows Q ₁ , Q ₂ is significantly dependent on the hydraulic resistors R ₁ , R ₂ , which are arranged in a first fluid path or a second fluid path, in which the fluid volume flows O ₁ , Q ₂ are performed.

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

Consequently, the total volume flow Q _{G can be} variably adjusted.

In the path from the pressure port of the pump 20 to the first hydraulic consumer 16 leads, is a fluid flow limiting valve 30 arranged. This fluid volume flow limiting valve 30 When a limiting volume flow Q _{S is reached, it is switched} by the first fluid volume flow Q ₁ from a first valve position to a second valve position.

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

Consequently, the ratio Q ₁ / Q ₂ of the first to second fluid volume flow can be changed solely by reaching a limiting fluid volume flow, in particular reversed.

In the first valve position of the fluid flow limiting valve 30 therefore becomes the first hydraulic consumer 16 a preferably larger volume flow is provided so that Q ₁ > Q ₂ . When the fluid flow limiting valve 30 is in the second valve position, preferably Q ₂ > Q ₁ .

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

The powertrain 40 also includes an electric machine 52 which is operable as a drive motor to provide drive power.

The powertrain 40 also includes a hydraulic system 10 that for the electric machine 52 provides a first cooling fluid volume flow Q ₁ , and for the wet-running multi-plate clutch of the clutch assembly 44 provides a second fluid volume flow Q ₂ . The hydraulic system 10 In terms of structure and operation preferably corresponds to the reference to 1 described hydraulic arrangement 10 ,

3 shows the operation of a fluid flow limiting valve 30 as it is in the hydraulic system 10 of the 1 is usable. 3 shows a graph of volume flow (for example in l / min) over the speed n of the electric motor 24 who is the pump 20 drives.

The total volume flow Q _G increases linearly as the speed n of the pump increases 20 to. 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 the distribution device 14 divided into a first fluid volume flow Q ₁ and a second volume flow Q ₂ , wherein Q _{1 is} preferably greater than Q ₂ . When the speed n _{S is} exceeded, the first fluid volume flow Q ₁ exceeds a restriction fluid flow Q _S , which causes the fluid flow restriction valve 30 is switched from the basic valve position to a switching valve position. As a result, the first fluid volume flow Q _{1 is} limited, in such a way that the total fluid volume flow Q _{G is} now divided into a smaller first fluid volume flow Q ₁ and a larger second fluid volume flow Q ₂ .

Upon reaching the speed n _S , consequently, the fluid volume flow of 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 can.

In the following 4 to 7 1, an embodiment of a fluid volume flow limiting valve is shown, which in terms of construction and operation generally the above-described fluid flow limiting valve 30 equivalent. The same elements are therefore identified by the same reference numerals. Essentially differences are explained below.

That in the 4 and 5 shown fluid flow limiting valve 30 has a housing 60 on. The housing 60 can be part of a powertrain housing. Through the fluid flow limiting valve 30 passing a volume flow Q ₁ is established.

The housing 60 has a first housing part 62 on, concentric with an axis 64 is trained. The first housing part 62 has a transverse to the axis 64 trained disc on, in the middle of an inflow opening 66 of the valve 30 is trained. From the circular disk of the first housing part 62 extends in the axial direction of an annular projection, so that the first housing part 62 a first fluid space 68 defined radially within the annular projection.

The housing 60 further includes a second housing part 70 , The second housing part 70 has an annular flange 72 on, the first housing part 62 completely overlaps. The ring flange 72 extends from a housing plate of the second housing part 70 that are concentric to the axis 64 arranged and aligned transversely thereto. In the housing of the second housing part 70 is centrally an outlet 74 educated.

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

Radial within the radial shoulder 78 of the second housing part 70 is a second fluid space 82 educated. The second fluid space 82 is bounded by a transverse to the axis 64 extending annular surface surrounding the drainage hole 74 is formed around. This annular surface is as a valve seat 84 educated.

The valve element 76 , this in 5 shown in plan view, includes an annular attachment member 88 in the assembled state between the annular projection of the first housing part 62 and the second housing part 70 is clamped. Furthermore, the valve element 76 a shut-off 90 on, as a circular disc radially within the annular attachment member 88 is trained. The obturator 90 and the attachment member 88 are over three radial arms 92 connected with each other.

Each radial arm has a fastener connection section 92a on which the radial arm with the attachment member 88 is connected, and a Absperrglied connection section 92b at which the radial arm 92 with the shut-off member 90 connected is. The radial arms each extend approximately in the tangential direction between a associated fastener connection section 92a and an associated obturator connection portion 92b ,

Central in the shut-off is an opening 94 formed, which can be realized in the manner of a diaphragm. Between the obturator 90 , the shut-off element 88 and the radial arms 92 are also flow openings 96 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 94 ,

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

The attachment member, the Absperrglied and the radial arms of the valve element 76 are therefore preferably formed integrally with each other.

In 6 is the pressure relief valve of 4 and 5 shown in the first valve position V ₁ .

The obturator is in a plane transverse to the axis 64 with the attachment member 88 aligned. One over the inflow opening 66 inflowing volume flow Q ₁ passes through the flow openings 96 and through the central opening 94 through and to the drain 74 ,

Preferably, the cross section is the inflow opening 66 smaller than the cross section of the drainage opening 74 ,

Due to the volume flow Q ₁ acts on the shut-off 90 an axial pressure in 6 at PB is shown. However, the pressure PB is so small at the volume flow Q ₁ that the shut-off 90 due to the spring forces of the radial arms 92 is held in position.

However, if the pressure PB increases due to a higher influent flow rate Q _1, as shown in 7 is shown, this biasing pressure PB, which in this case is above a threshold (corresponding to PB _S in FIG 3 ) the obturator 90 in the axial direction relative to the fastening member 88 off and pushes the shut-off 90 against the valve seat 84 , As a result, fluid can no longer pass through the flow openings 96 flow, which in this case from the valve seat 84 are covered.

Consequently, in this state only a relatively small volume flow Q ₁ through the central opening 94 stream.

The characteristic of this flow control valve of the 4 to 7 corresponds to the characteristic Q ₁ of 3 ,

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102013110400 A1 [0004]
• DE 102009023596 A1 [0007]
• US 6443183 B1 [0008]
• DE 10310039 A1 [0008]
• DE 102011009214 A1 [0009]
• US 2014/0216064 A1 [0010]

Claims (11)

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 provided with a first fluid volume flow (Q ₁ and wherein the second consumer (18; 44) is to be supplied, as needed, with a second fluid volume flow (Q ₂ ), the hydraulic assembly comprising: - a fluid supply device (12) adapted to provide 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; the first fluid volume flow (Q ₁ ) is supplied and the second consumer (18; 44) is supplied with the second fluid volume flow (Q ₂ ); characterized in that the distribution means (14) comprises a fluid flow limiting valve (30) having a fastening member (88) connected to a valve housing (60) and a shut-off member (90) disposed in a first valve position (V ₁ ) of a valve seat (90). 84) is raised and in a second valve position (V ₂ ) on the valve seat (84) is applied, wherein the shut-off member (90) via at least one elastic radial arm (92) with the fastening member (88) is connected. Hydraulic arrangement after 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. Hydraulic arrangement after Claim 1 or 2 characterized in that formed in the shut-off member (90) is an opening (94) which establishes a restricted flow rate through the fluid flow restriction valve (30) when the shut-off member (90) is in the second valve position (V ₂ ). 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. Hydraulic arrangement after Claim 4 characterized in that the radial arms (92) are each connected to the attachment member (88) via a fastener link portion (92a) and to the blocker member (90) via a check link connecting portion (92b), the radial arms (92) extending each tangentially between an associated fastener connection portion (92a) and an associated Absperrglied-connecting portion (92b) extend. 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 member (76). Hydraulic arrangement after 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. 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 ₁ ) a first ratio of the first fluid volume flow (Q ₁ ) 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 (Q ₁ ) to the second fluid volume flow (Q ₂ ) is established. Hydraulic arrangement according to one of Claims 1 - 8th Characterized in that the shut-off member (90) is installed in the valve housing (60), that of a pressurization pressure in the mode (PB) is applied, wherein the shutoff member (90) when exceeding a threshold value (PB _S) of the Beaufschlagungsdruckes ( PB) from the first valve position (V ₁ ) against an elastic deformation of the at least one radial arm (92) in the second valve position (V ₂ ) is movable. 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-disc clutch assembly (44). Valve element (76) for a hydraulic arrangement (10), in particular a hydraulic arrangement according to one of Claims 1 - 9 , with a fastening member (88) and a shut-off member (90) which is connected via at least one elastic radial arm (92) with the fastening member (88).

Images