阅读说明：本技术 能无级调节的环绕传动装置中的用于压紧盘组的具有蓄压器的流体系统以及能无级调节的环绕传动装置 (Fluid system with a pressure accumulator for pressing a disk stack in a continuously adjustable endless drive and continuously adjustable endless drive ) 是由 莱茵哈德·斯特尔 塞巴斯蒂安·科普夫勒 马库斯·西塞克 马尔科·格雷特 于 2019-02-04 设计创作，主要内容包括：本发明涉及一种用于能无级调节的环绕传动装置(2)的流体系统(1),流体系统具有电动机驱动的第一泵(3)和电动机驱动的第二泵(4),其中,第一泵(3)的第一接口(5)与引至贮存器(6)的管路区段(7)连接并且第一泵(3)的第二接口(8)与对应于环绕传动装置(2)的第一盘组(9)的第一操作装置(10)流体连接并且与第二泵(4)的第一接口(11)流体连接,并且其中,第二泵(4)的第二接口(12)与对应于环绕传动装置(2)的第二盘组(13)的第二操作装置(14)流体连接,其中,第一泵(3)在其第一接口(5)处与蓄压器(15)流体连接。本发明还涉及一种具有该流体系统(1)的能无级调节的环绕传动装置(2)。(The invention relates to a fluid system (1) for a continuously variable transmission (2) having a first motor-driven pump (3) and a second motor-driven pump (4), wherein the first connection (5) of the first pump (3) is connected to a line section (7) leading to a reservoir (6) and the second connection (8) of the first pump (3) is fluidically connected to a first operating device (10) corresponding to a first disk set (9) surrounding the transmission (2) and to a first connection (11) of the second pump (4), and wherein the second connection (12) of the second pump (4) is fluidically connected to a second operating device (14) corresponding to a second set (13) of discs surrounding the transmission (2), wherein the first pump (3) is fluidically connected to the pressure accumulator (15) at a first connection (5) thereof. The invention also relates to a continuously variable adjustable transmission (2) having such a fluid system (1).)

1. A fluid system (1) for a continuously variable adjustable transmission (2), the fluid system has a first motor-driven pump (3) and a second motor-driven pump (4), wherein the first connection (5) of the first pump (3) is connected to a line section (7) leading to a reservoir (6), and the second connection (8) of the first pump (3) is fluidically connected to a first operating device (10) of a first disk set (9) corresponding to the ring gear (2) and to a first connection (11) of the second pump (4), and wherein a second connection (12) of the second pump (4) is fluidically connected to a second operating device (14) of a second disk stack (13) of the ring gear (2), characterized in that the first pump (3) is fluidly connected at its first connection (5) to an accumulator (15).

2. A fluid system (1) according to claim 1, characterized in that a shut-off valve (16) is mounted in a pipe section (7) leading from the first interface (5) of the first pump (3) to the reservoir (6), and that the pressure accumulator (15) is connected to the pipe section (7) at a node area (17) provided between the shut-off valve (16) and the first interface (5) of the first pump (3).

3. A fluid system (1) according to claim 1 or 2, characterized in that a third pump (18) is present, which is connected or connectable with the first interface (5) of the first pump (3) via a line section (7) leading from the first interface (5) of the first pump (3) to the reservoir (6).

4. A fluid system (1) according to claim 3, characterized in that the shut-off valve (16) is mounted between the third pump (18) and the first pump (3) in such a way that it is open when fluid flows from the third pump (18) to the node area (17) and closed when fluid flows from the node area (17) to the third pump (18).

5. A fluid system (1) according to claim 3 or 4, characterised in that the third pump (18) is connected to a cooling and/or lubrication circuit (19) of the surrounding transmission (2).

6. A fluid system (1) according to any one of claims 3 to 5, characterised in that the third pump (18) is configured as a pump with a fixed direction of delivery, wherein an input interface (20) of the third pump (18) is connected with the reservoir (6) and an output interface (21) of the third pump (18) is connected with a line section (7) leading from the first interface (5) of the first pump (3) to the reservoir (6).

7. A fluid system (1) according to claim 6, characterised in that the third pump (18) is operatively connected with its output interface (21) via a valve (22) with a cooling and/or lubricant supply (24).

8. The fluidic system (1) according to any of claims 3 to 5, characterized in that the delivery direction of the third pump (18) is configured to be reversible.

9. A fluid system (1) according to claim 8, characterized in that the third pump (18) is connected with the reservoir (6) by means of a double pressure valve (25).

10. Continuously adjustable ring gear (2) for a drive train of a motor vehicle, having a first disc set (9) and a second disc set (13) and a fluid system (1) according to one of claims 1 to 9, wherein the first operating device (10) is operatively connected to the first disc set (9) and the second operating device (14) is operatively connected to the second disc set (13).

Technical Field

The invention relates to a fluid system for a continuously variable transmission, preferably designed as a hydraulic system, having a first pump driven by an electric motor and a second pump driven by an electric motor, wherein a first connection of the first pump is connected to a (first) line section leading to a reservoir/storage container/oil reservoir, and a second connection of the first pump is connected in a fluid manner to a first actuating device corresponding to a first disk set of the transmission and to a first connection of the second pump, and wherein a second connection of the second pump is connected in a fluid manner to a second actuating device corresponding to a second disk set of the transmission. The fluid system therefore has a (first) pump configured as a pressure pump and a (second) pump configured as a control pump, wherein the first pump provides a minimum pressure during operation at the two actuating devices of the two disk stacks, wherein the second pump sets the transmission ratio continuously around the transmission during operation by pumping fluid back and forth between the first actuating device and the second actuating device. The invention also relates to a continuously variable transmission for a drive train of a motor vehicle having such a fluid system.

Background

Fluid systems of this type and continuously variable transmission systems are known from the prior art. For example, US 6219608B 1 discloses an electronic control system for a transmission of a motor vehicle, which has a continuously variable transmission. Which includes first and second fluid pumps driven by electric motors to compress and modulate a variator surrounding a transmission.

Therefore, embodiments are known from the prior art in which a continuously variable adjustable ring gear (also referred to as CVT gear for short) is actuated by means of an electric pump actuator in the form of a different pump. In particular, the first pump used as a hold-down actuator requires a high current during operation in order to maintain the hold-down force required as a function of the torque and the transmission ratio of the CVT transmission. This continuous current not only causes permanent power consumption and continuous losses from the on-board electrical system of the motor vehicle, but also results in the electric motor of the first pump having to be made larger for thermal reasons and even having to be actively cooled off in order to maintain the continuous current.

Disclosure of Invention

It is therefore an object of the present invention to overcome the disadvantages of the prior art and in particular to provide a fluid system for a continuously variable transmission, which fluid system has a further improved efficiency.

According to the invention, this is achieved in that the first pump is fluidically connected to the pressure accumulator via its first connection.

By means of the pressure accumulator, the first connection of the first pump, which serves as the inlet/suction side, is maintained at a minimum pressure when the operating device is charged to a specific pressure. This entails that the first pump only needs to generate a relatively small pressure difference to generate a certain pressure for pressing the respective operating device and that this relatively small pressure difference must be maintained. In addition, the drive power of the first pump can thereby be further reduced. The current requirements of the fluid system are also reduced. And thus has an advantage in fuel consumption.

Further advantageous embodiments are claimed by the dependent claims and are set forth in detail below.

In order to make the fluid system particularly simple to construct, it is advantageous if a shut-off valve is installed in a (first) line section leading from the first connection of the first pump to the reservoir, and the pressure accumulator is (fluidically) connected to this line section at a node region arranged between the shut-off valve and the first connection of the first pump.

The shut-off valve is expediently designed as a non-return valve, so that the fluid system is particularly cost-effective to implement.

In addition to both the first pump and the second pump, there is advantageously a third pump which is connected or connectable with the first connection of the first pump (depending on the position of the shut-off valve in the case of a shut-off valve) via a (first) line section leading from the first connection of the first pump to the reservoir. This further simplifies the loading of the pressure accumulator.

The third pump is preferably embodied as an electric motor-driven pump, and further preferably as an internal combustion engine-driven pump.

It is also expedient for the shut-off valve to be installed between the third pump and the first pump in such a way that (during operation of the fluid system) the shut-off valve is open when fluid flows from the third pump to the node region and is closed when fluid flows from the node region to the third pump.

If the third pump is also connected to a cooling and/or lubricating circuit surrounding the transmission, cooling or lubrication of the surrounding transmission is provided in a particularly simple manner.

It has proven to be particularly advantageous here if the third pump is designed as a pump with a fixed, i.e. non-adjustable, delivery direction, wherein the inlet connection of the third pump is (fluidically) connected to the reservoir and the outlet connection of the third pump is (fluidically) connected to a (first) line section leading from the first connection of the first pump to the reservoir. The third pump is thus used to guide the fluid from the reservoir to the pressure accumulator over a particularly short path.

In the case of the third pump as a pump with a fixed delivery direction, it is also advantageous if the third pump is (additionally) operatively connected with its output connection via a valve to a cooling and/or lubricant supply for the continuously variable transmission. Furthermore, the valve is preferably designed such that in its initial position it separates the cooling and/or lubricant supply from the third pump and in its second position it connects the cooling and/or lubricant supply to the outlet connection of the third pump. The fluid system is thereby constructed more particularly simply.

Alternatively to the embodiment of the third pump with a fixed delivery direction, it is also expedient for the delivery direction of the third pump to be reversible, i.e. for the third pump to be a reversible pump. Preferably, a third pump with a reversible delivery direction is used in such a way that the third pump delivers fluid in a first rotational/delivery direction to the first pump/accumulator and in a second rotational/delivery direction opposite to the first rotational direction to the cooling and/or fluid supply.

It is also advantageous for the configuration of the fluid system in this case if the third pump is (fluidically) connected to the reservoir by means of a dual-pressure valve.

It should also be mentioned that the first pump and preferably also the second pump are each embodied as a pump/reversible pump whose delivery direction is reversible.

In order to monitor the pressure at the (first) line section between the first connection of the first pump and the reservoir, it is also advantageous to install a pressure sensor in the (first) line section between the first connection of the first pump and the shut-off valve. Further pressure sensors are preferably arranged between the first pump and the second pump and/or between the second pump and the second operating device.

Furthermore, it is advantageous if the second pump is couplable with its second connection via a further valve to the cooling and/or lubricant circuit. This makes it possible to reduce the overpressure particularly easily.

The invention further relates to a continuously variable transmission for a drive train of a motor vehicle, having a first and a second disk stack and a fluid system according to the invention according to at least one of the above-described embodiments, wherein the first actuating device is operatively connected to the first disk stack and the second actuating device is operatively connected to the second disk stack.

In other words, according to the invention, the pre-pressure is thus provided to the electric pump actuator (first pump) for the CVT transmission by means of the pressure accumulator. It is proposed that a pre-pressure is provided by means of the pressure accumulator, in particular on the low-pressure side (first connection) of the pressure actuator (first pump), so that the pressure actuator only has to overcome the pressure difference. The pressure accumulator is preferably loaded to the pre-pressure at a small distance from the further (third) pump, more preferably the cooling oil pump.

Drawings

The invention is explained in detail below on the basis of the drawings showing different embodiments.

In which is shown:

fig. 1 shows a schematic line diagram of a fluid system according to a first exemplary embodiment of the invention, for example for use in a continuously variable transmission, wherein it can be seen that the third pump is embodied as a pump with a fixedly arranged conveying direction,

fig. 2 shows a schematic line diagram of a fluid system according to a second exemplary embodiment of the invention, which is used in a continuously variable transmission, wherein, in contrast to the first exemplary embodiment, a second connection of a second pump of the fluid system can be optionally connected to a cooling and/or lubricating circuit of the transmission via a valve,

fig. 3 shows a schematic line diagram of a fluid system according to a third exemplary embodiment of the invention, for use in a continuously variable transmission, the third pump being embodied as a reversible pump and being coupled to a dual pressure valve in such a way that it is used to supply a cooling and/or lubricant supply, and

fig. 4 shows a schematic circuit diagram of a fluid system according to a fourth exemplary embodiment of the present invention, which is used in a continuously variable transmission, wherein, in contrast to the third exemplary embodiment, a second connection of a second pump of the fluid system can be optionally connected to a cooling and/or lubrication circuit of the transmission via a valve.

The drawings are merely schematic and are provided for understanding the present invention. Like elements are provided with like reference numerals. The different features of the different embodiments can also be freely combined with each other.

Detailed Description

With reference to fig. 1 a fluid system 1 according to a first embodiment of the present invention can be seen. In fig. 1, a fluid system 1 has been installed in a continuously variable transmission 2 in order to operate a transmission of the transmission 2, which transmission is not shown in detail here for the sake of clarity. The continuously variable transmission 2 is inserted into the drive train of the motor vehicle in its operation in a conventional manner. A first disk stack 9 (formed by a disk pair) surrounding the gear unit 2 is connected in a rotationally fixed manner to the drive shaft, while a second disk stack 13 (likewise formed by a disk pair) rotationally coupled to the first disk stack 9 via an endless traction means 26 is connected in a rotationally fixed manner to the driven shaft. Each disk stack 9, 13 therefore has at least one first disk which can be moved relative to a second disk, wherein the relative movement position of the first disk and the second disk can be adjusted by means of the operating device 10, 14 (transmission) of the fluid system 1. The operating devices 10, 14 are not shown in detail in the figures for the sake of clarity, but only their position. The transmission ratio between the drive shaft and the driven shaft can thus be set steplessly as a function of the spacing of the two disks of the respective disk stack 9, 13.

The fluid system 1 generally has a first pump 3 (also referred to as a first pump actuator) driven by an electric motor and a second pump 4 (also referred to as a second pump actuator) driven by an electric motor. Each pump 3, 4 therefore has an electric motor 27a, 27b driving the pump. The first pump 3 and the second pump 4 are each designed as reversible pumps. The second pump 3 is used as a compression pump, i.e. a pump which provides a minimum pressure when the first operating device 10 and the second operating device 14 are in operation. The second pump 4 acts as a regulating pump and thus as a pump for pumping fluid back and forth between the first operating device 10 and the second operating device 14 for regulating the disc pairs of the disc packs 9, 13.

The first connection 5 of the first pump 3 is fluidically connected to a first line section 7, wherein the first line section 7 leads to the reservoir 6. The second port 8 of the first pump 3 is fluidly connected to the second pump 4. For this purpose, a second line section 28 is provided, which fluidly connects the second connection 8 of the first pump 3 directly to the first connection 11 of the second pump 4. At the same time, the first operating device 10 is in fluid connection with the second line section 28. For this purpose, a pressure chamber of the first actuating device 10, which is not shown in any more detail for the sake of clarity, is connected to the second line section 28 via a (second) node region 29. The second connection 12 of the second pump 4 is connected to a second operating device 14, i.e. a pressure chamber of the second operating device 14, which is not shown in detail for the sake of clarity. For this purpose, a third line section 30 is provided between the second connection 12 of the second pump 4 and the second operating device 14.

The respective interfaces 5, 8 of both the first pump 3 and the second pump 4; 11. 12 serve as an inlet/suction side or an outlet/pressure side depending on the conveying direction of the pumps 3, 4. The first pump 3 serves in particular to maintain a minimum pressure of the second line section 28 during operation, the second line section 28 in turn being coupled to the third line section 30 via the second pump 4. If the respective minimum pressure is not reached in the second line section 28 and/or in the third line section 30, the first pump 3 is operated in the first conveying direction, so that the first connection 5 serves as a suction side of the first pump 3 and the second connection 8 serves as a pressure side of the first pump 3. Thus, fluid is pumped from the first pipe section 7 into the second pipe section 28. If a maximum pressure is reached or exceeded in the second line section 28 and/or in the third line section 30, the first pump 3 is deactivated, or even operated in a second conveying direction opposite the first conveying direction, so that the first connection 5 serves as the output side and the second connection 8 as the input side.

When the second pump 4 is operated in the first conveying direction, the first connection 11 serves as a suction side and the second connection 12 as a pressure side, so that fluid is pumped from the second line section 28 into the third line section 30. In a second conveying direction of the second pump 4, which is opposite to the first conveying direction, fluid is pumped from the third line section 30 into the second line section 28. In this case, the first connection 11 serves as a pressure side and the second connection 12 as a suction side.

According to the invention, an accumulator 15 is permanently connected to the first connection 5 of the first pump 3. The pressure accumulator 15 permanently provides a certain fluid pressure (minimum pressure) at the first connection 5. The accumulator 15 is connected to the first pipe section 7 at a (first) node region 17. The pressure accumulator 15 is thereby connected directly and permanently to the first connection 5 of the first pump 3. The first node region 17 is located in the first line section 7 between the shut-off valve 16, which is designed as a non-return valve, and the first connection 5. The shut-off valve 16 is arranged so that it is closed when a specific fluid pressure (maximum pressure) is reached on the first connection 5/accumulator 15 side and is opened when the first connection 5/accumulator 15 side is lower than the specific fluid pressure (minimum pressure).

Furthermore, the first line section 7 is operatively connected to a third pump 18. In this embodiment, the third pump 18 is configured as a motor-driven third pump 18. The third pump 18 is therefore in turn driven by means of the (third) electric motor 27 c. Alternatively, in principle, according to other embodiments, the third pump 18 can also be designed as an internal combustion engine-driven third pump 18. In this further embodiment, the third pump 18 is thus driven by the internal combustion engine of the drive train of the motor vehicle.

In the first embodiment according to fig. 1, the third pump 18 has a fixed delivery direction. A third pump 18 is installed between the reservoir 6 and the first line section 7 and thus serves to convey fluid from the reservoir 6 to the first line section 7. A first port 20 of the third pump 18, which is embodied as a (fixed) inlet port (intake port), is directly fluidically connected to the reservoir 6. A second connection 21 of the third pump 18, which is embodied as a (fixed) outlet connection (pressure connection), is connected to the first line section 7. The second connection 21 of the third pump 18 is connected to the first line section 7 on the side of the shut-off valve 16 facing away from the first node region 17.

The third pump 18 is designed as a coolant/lubricant feed pump and, depending on the position of the shut-off valve 16, can optionally be used as part of a coolant and/or lubricant circuit 19 or for feeding fluid to the pressure accumulator 15 via the shut-off valve 16 during operation. For this purpose, in the first line section 7, on the side of the shut-off valve 16 close to the third pump 18, a further third node region 31 is present, to which a further fourth line section 32 is connected. The fourth line section 32 is coupled to the cooling and/or lubricating device 24 (in the following simply referred to as the supply device 24) of the cooling and/or lubricating circuit 19. The first fluid valve 22 is mounted in the fourth line section 32 between the third node region 31 and the supply device 24. The supply device 24 serves in a conventional manner for cooling and lubricating the respective disk stacks 9, 13 or the transmission and for cooling or lubricating the contact points between the disk stacks 9, 13 and the endless traction means 26. The supply device 24 is also used in general for cooling a starting element of a drive train of a motor vehicle, such as a clutch or a torque converter. This is possible because the thermal time constant of the starting element allows a short interruption of the coolant volume flow. The first fluid valve 22 is used in such a way that it separates the supply device 24 from the second connection 21 of the third pump 18 in its output position (first position) and connects the supply device 24 to the second connection 21 in the second position. Thus, first fluid valve 22 is configured and used in this embodiment such that fluid flow from third pump 18 to supply 24 is released or blocked/interrupted.

In operation, the first fluid valve 22, which is designed as a solenoid valve, is switched on/actuated as a function of the fluid pressure in the pressure accumulator 15/at the first connection 5 of the first pump 3. The third pump 18 is permanently driven. If a minimum pressure is not reached at the first connection 5 of the first pump 3/in the pressure accumulator 15, the first fluid valve 22 is brought into its first position. By the resulting interrupted fluid connection between the second connection 21 of the third pump 18 and the supply device 24, the shut-off valve 16 is released as a result of the further applied pump delivery pressure of the third pump 18. As a result, the pressure at the first connection 5 is increased again with the further supply of the third pump 18 and the pressure accumulator 15 is charged again. If the accumulator 15 is charged to a certain fluid pressure (maximum pressure), the first fluid valve 22 is switched to its second position. Due to the re-established connection between the second connection 21 and the supply device 24, the shut-off valve 16 automatically closes, since the pressure at the supply device 24 is lower than the pressure in the pressure accumulator 15.

Alternatively to this embodiment, according to other embodiments, the first fluid valve 22 is also designed and used in such a way that the volume flow delivered by the third pump 18 is split. The first fluid valve 22 is then used and configured in such a way that the first partial volume flow flows (in the main position of the first fluid valve 22) from the second connection 21 of the third pump 18 to the supply device 24 and the second partial volume flow flows from the second connection 21 (via the open shut-off valve 16) into the pressure accumulator 15/to the first connection 5.

In this way, it is possible to implement the three pumps 3, 4 and 18 in each case preferably at the same nominal power. Thereby further simplifying the construction of the system. In order to monitor the respective pressures in the first, second and third line sections 7, 28 and 30, a pressure sensor 33 is connected in each of the first, second and third line sections 7, 28 and 30. For the first line section 7, the pressure sensor 33 is connected to the first node region 17.

In fig. 2 a second embodiment of a fluid system 1 according to the invention is shown. The second embodiment and the embodiments described below with reference to fig. 3 and 4 are constructed and operate substantially in accordance with the first embodiment, and therefore only the differences from the first embodiment are described below.

In the second exemplary embodiment according to fig. 2, the third line section 30 is fluidically coupled directly to the supply device 24/the cooling and/or lubricant circuit 19 via a further (second) fluid valve 23. For this purpose, a branch line 35 is connected to a fourth node region 34 in the third line section 30, which branch line can be coupled to the feed device 24 via the second fluid valve 23. The second fluid valve 23 is likewise embodied as a solenoid valve. The second fluid valve 23 is constructed and operates substantially in accordance with the first fluid valve 22. In the first position of the second fluid valve 23, the third line section 30 and the second connection 12 of the second pump 4 are disconnected from the cooling and/or lubricating device 24. In the second position of the second fluid valve 23, the third line section 30 is in fluid connection with the supply device 24.

A third embodiment of the fluid system 1 can be seen in connection with fig. 3. The fluid system 1 differs from the first exemplary embodiment in particular in that the third pump 8 is embodied as a reversible pump like the first pump 3 and the second pump 4.

Furthermore, the third pump 18 interacts with a double pressure valve 25. Double pressure valve 25 is connected to reservoir 6 at input 36. The double pressure valve 25 is connected with a first output 37 to the first line section 7. The first outlet 37 is connected to the side of the shut-off valve 16 facing away from the first pump 3 (directly to the first line section 7). The second output 38 of the double pressure valve 25 is connected directly to the fourth line section 32 on the supply device 24 side. The third pump 18 is used in parallel with a double pressure valve 25. The third pump 18 is connected with its second connection 21 to the first line section 7 (in this case via the third node region 31) and with its first connection 20 to the fourth line section 32.

The double pressure valve 25 closes or opens the respective output 37 and 38 depending on the delivery direction of the third pump 18. In the first delivery direction of the third pump 18, the first output 37 is closed and the second output 38 is open, and fluid flows from the reservoir 6 via the input 36, the second output 38, the fourth line section 32, the first connection 20 (input side) of the third pump 18 and the second connection 21 (output side) of the third pump 18 to the shut-off valve 16/the third node region 31. Since the shut-off valve 16 is open in the first delivery direction of the third pump 18, the pressure accumulator 15 is filled again to a specific fluid pressure. In a second conveying direction of the third pump 18, which is opposite to the first conveying direction, the first outlet 37 is open and the second outlet 38 is closed, so that fluid is conveyed via the inlet 36, the first outlet 37, the first line section 7 (on the side of the shut-off valve 16 close to the first node region 17), the second connection 21 (inlet side) of the third pump 18 and the first connection 20 (outlet side) of the third pump 18 into the fourth line section 32 and from there to the supply device 24.

Additionally, in this embodiment, a check valve 39 is installed between the third pump 18 and the supply device 24 (in the fourth line section 32). The check valve 39 is used such that it closes/switches into a closed position in the first conveying direction (fluid flowing from the reservoir 6 into the first connection 20 via the input 36, the second output 38) during operation of the pump 18, so that air is prevented from being sucked in at the supply device 24. In this case, the check valve 39 is arranged outside the part of the fourth line section 32 which directly connects the second outlet 38 to the first connection 20. The non-return valve 39 opens in the second delivery direction of the third pump 18 and enables fluid to flow to the supply device 24 (from the reservoir 6 via the input 36, the first output 37, the second and first connections 21, 20 and the fourth line section 32).

In the fourth embodiment, the additional branch line 35 is connected in common with the second fluid valve 23 to the second pump 4 compared to the third embodiment, further details of which have been described in connection with the second embodiment (compared to the first embodiment).

In other words, according to the invention, it is achieved that a pre-pressure is already provided on the low-pressure side (first connection 5) of the pressure actuator (first pump 3), so that the pressure actuator 3 only has to overcome the pressure difference. For this purpose, according to the invention, an accumulator 15 is suitable, which is loaded to the pre-pressure at a short distance from the other pump (third pump 18) as required. The pump 18 can expediently be a cooling oil pump which is alternately used for cooling/lubricating the transmission and/or the starting elements and for charging the reservoir 15 by means of a suitable line arrangement. Use is made here of the fact that: the thermal time constants of the starting elements, such as clutches, torque converters, etc., generally allow a brief interruption of the cooling oil volume flow.

The first scheme (first and second embodiments) utilizes a cooling oil valve (first fluid valve 22) to temporarily separate the cooling oil pump 18 from the cooling circuit 19 and allow the reservoir 15 to be loaded to the target pressure through the check valve 16. If the cooling valve 22 is open and the cooling oil pump 18 is accordingly in low-pressure operation, the check valve 16 prevents the reservoir pressure from being discharged into the cooling circuit 19. If the cooling oil pump 18 cannot fill the reservoir 15 as provided, the pressure pump (second pump 4) can suck in pressure medium in an emergency via the non-return valve 16 itself, so that the pressure is ensured. Suitably, the accumulator loading status is monitored by means of a pressure sensor 33 for correct operation of the cooling oil and booster pump 18.

The second variant (third and fourth exemplary embodiment) operates in principle on the same principle, but here uses a reversible cooling oil pump 18 with a double pressure valve 25. The cooling oil pump feeds the cooling circuit 19 in one direction of rotation, loads the reservoir 15 in the other direction of rotation, and in both cases draws pressure medium from the oil reservoir 6. In an emergency, the pressure pump 4 draws pressure medium from the oil reservoir 6 when the reservoir 15 is empty.

List of reference numerals

1 fluid system

2-ring transmission device

3 first pump

4 second pump

5 first interface of first pump

6 storage container

7 first pipeline section

8 second interface of first pump

9 first disk group

10 first operating device

11 first interface of second pump

12 second interface of second pump

13 disk stack

14 second operating device

15 pressure accumulator

16 stop valve

17 first node area

18 third pump

19 cooling and/or lubricant circuit

20 first interface of third pump

21 second interface of third pump

22 first fluid valve

23 second fluid valve

24 cooling and/or lubricant supply device

25 double pressure valve

26 circulating traction piece

27a first motor

27b second motor

27c third Motor

28 second pipeline section

29 second node area

30 third pipeline section

31 third node region

32 fourth pipeline section

33 pressure sensor

34 fourth node area

35 branch pipeline

36 input end of double-pressure valve

37 first output end of double-pressure valve

38 second output of the dual pressure valve

39 check valve