DE102012022086B4 - Hydraulic control device - Google Patents

Abstract

Hydraulic control device (1) for an automated transmission of a motor vehicle, with at least one working cylinder (2, 3, 4, 5, 6, 7), with at least one pressure control valve (VP1 or VP2), with a pressure accumulator (18) and with at least a leakage point (24, 25), a pressure stored in the pressure accumulator (18) being able to be reduced via the leakage point (24, 25), the pressure control valve having a housing (26) with a receptacle (28), and the housing ( 26) has at least three connections, namely a pressure connection (P), a working connection (A) and a tank connection (T), characterized in that the leakage point (24 or 25) is integrated in the pressure control valve (VP1 or VP2), a piston (27) being guided in an axially displaceable manner in the housing (26), the pressure connection (P) being functionally connected to the pressure accumulator (18), the tank connection (T) being functionally connected to a tank (10). , wherein the leakage point (24, 25) is formed on the piston (27) and/or in the housing (26), wherein in a basic position of the piston (27) the leakage point (24, 25) has a fluid connection from the pressure port (P) to the tank connection (T), the piston (27) having at least two annular spaces (30, 31) and a plurality of sealing surfaces (32, 33, 34), the piston (27) sealing with the sealing surfaces (32, 33, 34). is guided in the receptacle (28), a central sealing surface (33) being formed between the two annular spaces (30, 31), this central sealing surface (33) having two sealing partial surfaces (33a and 33b), one sealing partial surface (33a ) has a leakage point (24, 25), with the pressure port (P) and the working port (A) being connected to one another via this leakage point (24, 25) in the normal position of the piston (27), with the working port (A ) and the tank port (T) are connected to one another via the one annular space (31), and in a working position of the piston (27) the leak-free sealing surface area (33b) closes a connection between the working port (A) and the tank port (T).

Description

The invention relates to a hydraulic control device for an automated transmission of a motor vehicle, according to the features of the preamble of patent claim 1.

From the DE 10 2008 037 235 A1 a hydraulic control device with a hydraulic circuit is known. The hydraulic circuit is used to control a friction clutch of an automotive automatic transmission and to control the engagement and disengagement of gear ratios. A fluid flows in the hydraulic circuit. Several working cylinders are provided. A pressure control valve is assigned to each of the working cylinders. The working cylinders are each connected to the pressure control valves via a line. A leakage point is provided in the line, the leakage point being able to be switched on and off with a leakage valve. The leakage is used to improve the control quality of the hydraulic circuit. If the leakage valves and the associated upstream pressure control valve are now open, the pressure from the pressure accumulator can be released via the leakage point.

• Aus der EP 1 439 285 B1 ist eine Nockenwellenverstelleinrichtung für Kraftfahrzeuge bekannt. Die Nockenwellenverstelleinrichtung weist ein Verstellelement auf, das durch einen Proportional-Magnetventil betätigbar ist. Das Proportional-Magnetventil weist ein Gehäuse auf, in dem ein Kolben verschiebbar ist und das mindestens einen Arbeitsanschluss, einen Tankanschluss und einen Druckanschluss aufweist. Über den Druckanschluss ist ein Hydrauliköl zuführbar. Der Kolben weist mindestens einen Durchlass für das Hydrauliköl auf. Der Druckanschluss ist über einen Leckagedurchtritt mit dem Arbeitsanschluss verbunden. Der Leckagedurchtritt kann dabei im Kolben oder im Ventilgehäuse vorgesehen sein. Der Leckagedurchtritt kann eine die Wandung des Kolbens durchsetzende Öffnung sein.

Various valves are also known in the prior art:

• From the EP 1 439 285 B1 a camshaft adjustment device for motor vehicles is known. The camshaft adjustment device has an adjustment element that can be actuated by a proportional solenoid valve. The proportional solenoid valve has a housing in which a piston can be displaced and which has at least one working connection, a tank connection and a pressure connection. A hydraulic oil can be supplied via the pressure connection. The piston has at least one passage for the hydraulic oil. The pressure port is connected to the working port via a leakage passage. The leakage passage can be provided in the piston or in the valve housing. The leakage passage can be an opening passing through the wall of the piston.

From the US 4,537,164A a valve actuating device for an internal combustion engine is known. Hydraulic oil is fed to an actuator system via a slide valve. The spool valve has a bypass for supplying the hydraulic oil to corresponding working cylinders when the spool valve is in a de-energized home position. This improves the response sensitivity of the actuators. The hydraulic oil flowing through the bypass displaces air that is in the connecting lines between the slide valve and the actuator.

In the DE 10 2010 032 657 A1 discloses a hydraulic control device that can be used to control a double clutch transmission of a vehicle. A number of components, in particular a number of safety valves and/or a number of pilot valves, are provided or present for the control.

The hydraulic control device mentioned at the outset is not yet optimally designed. Additional components are required to provide a leakage point in the hydraulic circuit.

The invention is therefore based on the object of designing and developing the hydraulic control device mentioned at the outset in such a way that a leakage point is provided with little effort.

This object on which the invention is based is now achieved by the features of patent claim 1 . The leakage point is integrated in the pressure control valve. This has the advantage that a leakage point is provided with little effort. The pressure control valve has a pressure port, a working port and a tank port, the pressure port being functionally connected to the pressure accumulator. In a basic position, the pressure rain valve provides a leakage point for reducing the accumulator pressure. This has the advantage that in the basic position the pressure oil can be drained from the pressure accumulator into the tank. No additional electric valve is necessary. In one embodiment of the pressure control valve, the pressure connection is directly functionally connected to a corresponding tank line through the leakage point. The leakage point can be formed in particular by a groove or a recess in a housing of the pressure control valve, with a piston being guided in the housing in an axially displaceable manner. Alternatively, the housing can have a narrow ring channel around the piston, so that this ring channel forms a functionally effective leakage point from the pressure connection to the tank line. The pressure control valve is designed such that in the basic position the leakage point connects the pressure port to the working port, with a fluid connection from the working port to the tank port being present in a basic position of the piston. The piston has at least two annular spaces and a plurality of sealing surfaces, the piston being guided in the receptacle with the sealing surfaces in a sealing manner. A central sealing surface is formed between the two annuli, this central sealing surface having two sealing faces. One sealing part surface has a leakage point, with the pressure connection and the working connection being connected to one another via this leakage point in the basic position of the piston. are in the basic position furthermore, the working connection and the tank connection are connected to one another via the one annular space, with the leak-free sealing part surface closing a connection between the working connection and the tank connection in a working position of the piston. This has the advantage that leakage only occurs in the basic position. In the working position of this pressure control valve, a passage between the pressure port and the working port is completely open, but a connection between the working port and the tank port is closed. As a result, leakage occurs only in the basic position and not during operation. There are now different ways of designing and developing the pressure control valve. In a particularly preferred embodiment, the hydraulic circuit is used to control a dual clutch transmission. The double-clutch transmission has two sub-transmissions, each with a friction clutch and multiple gear selectors. Starting from a main pressure line with the pressure accumulator, the hydraulic circuit branches into two hydraulic subsystems, each of which is preceded by a pressure control valve, namely a partial transmission valve. The leakage points are preferably integrated into these two partial transmission valves. Further gear selector valves or clutch selector valves assigned to the respective working cylinder are arranged downstream of these partial transmission valves. The disadvantages mentioned at the outset are therefore avoided and corresponding advantages are achieved.

• 1 in einem schematischen Hydraulikplan eine hydraulische Steuervorrichtung für ein Doppelkupplungsgetriebe,
• 2 in einer schematischen, längs geschnittenen Darstellung ein Druckregelventil, nämlich ein Teilgetriebeventil mit einer Leckagestelle,
• 3 in einem schematischen Querschnitt das Druckregelventil mit der Leckagestelle aus 2,
• 4 in einer schematischen, längs geschnittenen Darstellung eine weitere Ausgestaltung des Druckregelventils,
• 5 in einer schematischen Detaildarstellung das Detail A mit einer zweiten Ausgestaltung der Leckagestelle aus 4,
• 6 in einer schematischen, längs geschnittenen Darstellung das Detail A aus 4 mit einer dritten Ausgestaltung der Leckagestelle,
• 7 in einer schematischen, quer geschnittenen Darstellung das Detail A aus 4 mit der dritten Ausgestaltung der Leckagestelle,
• 8 in einer schematischen, längs geschnittenen Darstellung das Detail A aus 4 mit einer vierten Ausgestaltung der Leckagestelle,
• 9 in einer schematischen, quer geschnittenen Darstellung das Detail A mit der vierten Ausgestaltung der Leckagestelle,
• 10 in einer schematischen, längs geschnittenen Darstellung das Detail A aus 4 mit einer fünften Ausgestaltung der Leckagestelle,
• 11 in einer schematischen, quer geschnittenen Darstellung das Detail A mit der fünften Ausgestaltung der Leckagestelle aus 10,
• 12 in einer schematischen, längs geschnittenen Darstellung das Detail A aus 4 mit einer sechsten Ausgestaltung der Leckagestelle.

There are now a large number of possibilities for designing and developing the hydraulic control device according to the invention. For this purpose, reference may first be made to the patent claims subordinate to patent claim 1. Several preferred configurations of the hydraulic control device are explained in more detail below with reference to the drawing and the associated description. In the drawing shows:

• 1 in a schematic hydraulic diagram, a hydraulic control device for a dual clutch transmission,
• 2 in a schematic, longitudinally sectioned representation of a pressure control valve, namely a partial transmission valve with a leakage point,
• 3 in a schematic cross section, the pressure control valve with the leakage point 2 ,
• 4 in a schematic, longitudinally sectioned representation of a further embodiment of the pressure control valve,
• 5 in a schematic detailed representation, detail A with a second configuration of the leakage point 4 ,
• 6 detail A in a schematic, longitudinally sectioned view 4 with a third embodiment of the leakage point,
• 7 detail A in a schematic, cross-sectional representation 4 with the third configuration of the leakage point,
• 8th detail A in a schematic, longitudinally sectioned view 4 with a fourth embodiment of the leakage point,
• 9 in a schematic, cross-sectional representation, detail A with the fourth embodiment of the leakage point,
• 10 detail A in a schematic, longitudinally sectioned representation 4 with a fifth embodiment of the leakage point,
• 11 in a schematic, cross-sectional representation, detail A with the fifth embodiment of the leakage point 10 ,
• 12 detail A in a schematic, longitudinally sectioned representation 4 with a sixth embodiment of the leakage point.

In 1 a hydraulic control device 1 for an automated transmission of a motor vehicle, not shown in detail, is shown. The automated transmission is designed in particular as a double clutch transmission. The hydraulic control device 1 is appropriately designed and suitable for the dual clutch transmission.

The hydraulic control device 1 has at least one working cylinder 2 . A total of six working cylinders 2 to 7 are shown in the illustration. The working cylinder 2 is used to move a switching device for engaging gears one and three. The working cylinder 3 is used to actuate another switching device for engaging gears seven and five. The working cylinder 4 is used to actuate a first clutch K1 of the dual clutch transmission. The working cylinder 5 is used to actuate a further switching device for engaging gears two and four. The working cylinder 6 is used to actuate a further switching device for engaging the sixth gear and a reverse gear. The working cylinder 7 is used to actuate a second clutch K2 of the dual clutch transmission. Working cylinders two to seven can be actuated hydraulically. The working cylinders 2, 3 and 5 and 6 are designed as double-acting cylinders.

A pump 8 is provided to supply the working cylinders 2 to 7 with a pressure medium, in particular a hydraulic oil. The pump 8 is driven by a motor 9 and pumps it Pressure medium from a tank 10. The tank 10 can also be referred to as a sump. The motor 9 is designed in particular as an electric motor. The pump 8 can have a maximum specific delivery rate. The pump 8 can be designed as an external gear pump. The pump 8 conveys the pressure medium to a filter 11. A spring-loaded check valve 12 is arranged parallel to the filter 11. A branch 13 with a pressure-limiting valve 14 is arranged behind the filter 11 and the check valve 12 . The pressure relief valve 14 opens when a maximum pressure is reached or exceeded. The pressure relief valve 14 is designed as a spring-loaded check valve. The branch 13 opens into the tank 10 again. Furthermore, a further branch 15 is arranged downstream of the filter 11 and the check valve 12, the branch 15 opening into a main pressure line 17 via a further check valve 16.

The hydraulic control device 1 also has a pressure accumulator 18 . The pressure accumulator 18 is associated with the main pressure line 17 . The hydraulic control device 1 also has a pressure gauge 19 . The pressure gauge 19 measures the pressure in the main pressure line 17.

The hydraulic control device 1 has two hydraulic subsystems 19 and 20 . Each subsystem has corresponding ones of the working cylinders 2-7. Working cylinders 2 , 3 and 4 are assigned to subsystem 19 . The working cylinders 5 , 6 , 7 are assigned to the other subsystem 20 . The working cylinders 2 and 3 are each assigned a pressure control valve, namely a gear control valve GSV1 or GSV2. The gear control valves GSV1, GSV2 are assigned to the first subsystem 19. Another pressure control valve, namely a clutch valve KV1, is assigned to the working cylinder 4 . The clutch valve KV1 is assigned to the first subsystem 19 . The gear control valves GSV1, GSV2 and the clutch valve KV1 are designed as three-way valves.

Correspondingly, the working cylinders 5, 6 are each assigned a gear control valve GSV3 and GSV4. A clutch valve KV2 is assigned to the working cylinder 7 . The working cylinders 4, 7 for actuating the two friction clutches K1 and K2 are designed to be single-acting with return stroke springs.

The main pressure line 17 branches via two pressure control valves, namely here via two partial transmission valves VP1, VP2 into the respective subsystems 19, 20. The partial transmission valves VP1, VP2 can be used to depressurize the partial system 19 and the partial system 20 respectively. Both the partial transmission valves VP1 and VP2 and the gear control valves GSV1, GSV2, GSV3, GSV4 and the clutch valves KV1, KV2 are connected to the tank 10 via a tank line 21. The gear control valves GSV1, GSV2 and the clutch valve KV1 are connected to the partial transmission valve VP1 via a partial system pressure line 22. The gear selector valves GSV3, GSV4 and the clutch valve KV2 are connected via a further partial system pressure line 23 to the second partial transmission valve VP2.

During operation, the two partial transmission valves VP1 and VP2 are open. The partial transmission valves VP1, VP2 close either when the ignition is switched off or in the event of a fault in one of the partial systems 19, 20, in which case only the respectively associated partial transmission valve VP1 or VP2 closes. During operation, the pressure in the subsystems 19 and 20 can vary. The subsystem pressure in the subsystem pressure lines 22, 23 each have a specific pressure.

The hydraulic control device 1 has at least one leakage point. In the embodiment shown, two leakage points 24, 25 are provided. A pressure stored in the accumulator 18 can be reduced via these leakage points 24 , 25 . In an alternative embodiment, one or more than two leakage points 24, 25 can be provided.

The leakage points 24 and 25 are integrated in the pressure control valves (VP1 and VP2), preferably the leakage points 24 and 25 are respectively integrated in the partial transmission valves VP1 and VP2, ie in particular one leakage point 24 and 25 per pressure control valve. In the preferred embodiment, the pressure control valves are therefore designed as partial transmission valves VP1, VP2 or, in the preferred embodiment of the hydraulic diagram, are inserted or used as partial transmission valves VP1, VP2. In 1 it can be seen that in a basic position of the partial transmission valves VP1 and VP2, the main pressure line 17 is functionally connected to the tank line 21 via the leakage points 24 and 25, respectively.

In the following, the preferred design of the pressure control valves with the leakage point 24, 25, namely here the partial transmission valves VP1 and VP2 based on the 2 ff. be explained in more detail.

The partial transmission valves VP1, VP2 have a housing 26 with at least three ports, namely a pressure port P, a working port A and a tank port T. The working connection A is arranged between the pressure connection P and the tank connection T. The main pressure line 17 is connected to the pressure port P. The subsystem 19 or the subsystem 20 is connected to the working connection A connected. The pressure port P is functionally connected to the pressure accumulator 18 . The tank connection T is functionally connected to the tank 10 via the tank line 21 .

Within the housing 26, a piston 27 is guided in a receptacle 28 in an axially displaceable manner. The piston 27 can be brought into different switching positions. This allows different connections to be made between the ports. The piston 27 is adjusted by means of an adjusting device 29. The adjusting device 29 is designed as an electromagnetic adjusting device.

The piston 27 has several areas with different diameters. As a result, corresponding control edges are formed. The piston 27 has two annular spaces 30, 31 in particular. The annular spaces 30, 31 are formed or limited by the piston 27 and the receptacle 28. Adjacent to the annular spaces 30, 31, the piston 27 has a plurality of sealing surfaces 32, 33, 34. The sealing surfaces 32, 33, 34 form the corresponding control edges. With the sealing surfaces 32, 33, 34, the piston 27 is guided in the receptacle 28 in a substantially sealing manner.

In the embodiment shown, the leakage point 24 or 25 is formed on the sealing surface 33 between the two annular spaces 30 and 31 . In the illustrated embodiment, the piston 27 is arranged in a basic position. The pressure medium can now flow from the main pressure line 17 through the leakage point 24 or 25 to the working port A. In the embodiment shown, the annular space 31 connects the working port A to the tank port T. As a result, the pressure medium can continue to flow from the working port A to the tank port T. The pressure stored in the pressure accumulator 18 can thus be reduced when the piston 27 is in the basic position. 3 shows the vzw. as a triangular or wedge-shaped groove in the piston 27 designed leakage point 24 or 25.

The sealing surface 33 between the two annular spaces 30 and 31 has two non-connected partial sealing surfaces 33a and 33b. The leakage point 24 or 25 is now formed on the one partial sealing surface 33a. The sealing part surface 33b has no leakage points 24, 25. In the working position of this pressure control valve VP1 or VP2, the partial sealing surface 33b now seals the working port A from the tank port T in a fluid-tight manner. In the working position, the partial sealing surface 33b closes the connection between the working connection A and the tank connection T. In this working position, the annular space 30 with the pressure connection P is fluidically connected with the working connection A. The division of the middle sealing surface 33a into the two partial sealing surfaces 33a, 33b has the advantage that in the working position of this pressure control valve, namely the pressure control valve designed or used here as a partial transmission valve VP1, VP2, no leakage from the pressure port P to the tank port T occurs.

The piston 27 is biased by a spring 35. The spring 35 urges the piston 27 into the basic position. If this pressure control valve VP1 or VP2 is de-energized, the pressure in the pressure accumulator 18 can be reduced as described.

The pressure control valve VP1/VP2 shown also has an outlet 36 on the actuator side of the pressure port P. When the pressure control valve is installed, this outlet 36 is functionally connected to the tank line 21 .

The in the 4 The further configurations of the pressure control valves/partial transmission valves VP1, VP2 shown et seq. have essentially the identical structure of the one shown in FIG 2 shown pressure control valve. Reference is therefore made to the above description in this regard.

in the in 5 In the embodiment shown, the leakage points 24, 25 are each formed in the area of the sealing surface 32 in the housing 26. These leakage points 24, 25 thus connect the pressure port P directly to the outlet 36.

in the in 5 shown embodiment, the housing 26 is machined in such a way that a narrow annular channel 37 is formed around the sealing surface 32 . The ring channel 37 surrounds the piston 27 in particular peripherally. The housing 26 can have a step (not shown in detail) here, so that leakage via the leakage points 24, 25 only occurs when the piston 27 is pushed back completely into the basic position. The axial length of the ring channel 37 is selected such that the entire sealing surface 32 is pushed into the ring channel 37 when the piston 27 is in the basic position. When the piston 27 is moved into the working position, at least part of the sealing surface 32 moves into the area of the receptacle 28 where the ring channel 37 is no longer provided and thereby seals the pressure connection P against the outlet 36 in a fluid-tight manner.

In the 6 and 7 In the embodiment shown, the housing 26 has leakage points 24, 25 in the form of kidney-shaped recesses 38 extending radially outward.

in the in 8th and 9 shown embodiment, the leakage points 24, 25 in the form of grooves in the housing 26 are formed. The grooves 39 essentially have a triangular cross section. The axial length of the recesses 38 or the grooves 39 is chosen so that leakage via the leakage points 24, 25 only occurs when the piston 27 is pushed back completely into the basic position. When the piston 27 is moved into the working position, at least a part of the sealing surface 32 moves into the area of the receptacle 28 where the recesses 38 or the grooves 39 are no longer provided and thereby seals the pressure connection P against the outlet 36 in a fluid-tight manner . in the in 10 and 11 shown embodiment, the housing 26 in turn has an annular channel 40. The annular channel 40 forms the leakage point 24 , 25 . In addition, the piston 27 has flattened key surfaces 41 in the area between the sealing surface 32 and the annular space 30 , which differs from the rest of the cylindrical shape. In the basic position of the piston 27, the leakage points 24, 25 are formed by the wrench flats 41 and the annular channel 40. When the piston 27 is moved into the working position, at least part of the sealing surface 32 moves into the area of the receptacle 28 where the ring channel 40 is no longer provided and thereby seals the pressure connection P against the outlet 36 in a fluid-tight manner.

in the in 12 shown embodiment, the housing 26 in turn has an annular channel 42. The sealing surface 32 of the piston 27 has two partial sealing surfaces 32a and 32b that are not connected to one another. The sealing surface 32b closer to the annular space 30 is provided with two longitudinal grooves 43. In the basic position of the piston 27, the leakage points 24, 25 are formed by the longitudinal grooves 43 in the sealing surface 32b and the annular channel 42. When the piston 27 is moved into the working position, at least part of the sealing surface 32a moves into the area of the receptacle 28 where the ring channel 42 is no longer provided and thereby seals the pressure connection P against the outlet 36 in a fluid-tight manner.

Reference List

1

hydraulic control device

2

working cylinder

3

working cylinder

4

working cylinder

5

working cylinder

6

working cylinder

7

working cylinder

8th

pump

9

engine

10

tank

11

filter

12

check valve

13

branch

14

pressure relief valve

15

branch

16

check valve

17

main pressure line

18

accumulator

19

subsystem

20

subsystem

21

tank line

22

subsystem pressure line

23

subsystem pressure line

24

leak point

25

leak point

26

Housing

27

Pistons

28

Recording

29

adjusting device

30

annulus

31

annulus

32

sealing surface

33

sealing surface

33a

sealing surface

33b

sealing surface

34

sealing surface

35

Feather

36

Sequence

37

ring canal

38

recess

39

groove

40

ring canal

41

wrench flat

42

ring canal

43

groove

GSV1

gear shift valve

GSV2

gear shift valve

GSV3

gear shift valve

GSV4

gear shift valve

KV1

clutch valve

KV2

clutch valve

VP1

Pressure control valve/ partial transmission valve

VP2

Pressure control valve/ partial transmission valve

P

pressure connection

A

working connection

T

tank connection

Claims (6)

Hydraulic control device (1) for an automated transmission of a motor vehicle, with at least one working cylinder (2, 3, 4, 5, 6, 7), with at least one pressure control valve (VP1 or VP2), with a pressure accumulator (18) and with at least a leakage point (24, 25), a pressure stored in the pressure accumulator (18) being able to be reduced via the leakage point (24, 25), the pressure control valve having a housing (26) with a receptacle (28), and the housing ( 26) has at least three connections, namely a pressure connection (P), a working connection (A) and a tank connection (T), characterized in that the leakage point (24 or 25) is integrated in the pressure control valve (VP1 or VP2), a piston (27) being guided in an axially displaceable manner in the housing (26), the pressure connection (P) being functionally connected to the pressure accumulator (18), the tank connection (T) being functionally connected to a tank (10). , wherein the leakage point (24, 25) is formed on the piston (27) and/or in the housing (26), wherein in a basic position of the piston (27) the leakage point (24, 25) has a fluid connection from the pressure port (P) to the tank connection (T), the piston (27) having at least two annular spaces (30, 31) and a plurality of sealing surfaces (32, 33, 34), the piston (27) sealing with the sealing surfaces (32, 33, 34). is guided in the receptacle (28), a central sealing surface (33) being formed between the two annular spaces (30, 31), this central sealing surface (33) having two sealing partial surfaces (33a and 33b), one sealing partial surface (33a ) has a leakage point (24, 25), with the pressure port (P) and the working port (A) being connected to one another via this leakage point (24, 25) in the normal position of the piston (27), with the working port (A ) and the tank port (T) are connected to one another via the one annular space (31), and in a working position of the piston (27) the leak-free sealing surface area (33b) closes a connection between the working port (A) and the tank port (T). Hydraulic control device according to claim 1 , characterized in that the automated transmission is designed as a double-clutch transmission, the hydraulic control device (1) having two subsystems (19, 20) which are each connected via one of the pressure control valves (VP1 or VP2) to the pressure accumulator (18) via a main pressure line (17) can be connected or are connected, the pressure control valves (VP1, VP2) designed or used as partial transmission valves having the leakage points (24, 25). Hydraulic control device according to claim 2 , characterized in that each subsystem (19, 20) has at least one gear selector valve (GSV1, GSV2, GSV3, GSV4) and/or at least one clutch selector valve (KV1, KV2), the gear selector valves (GSV1, GSV2, GSV3, GSV4) and one of the working cylinders (2, 3, 4, 5, 6, 7) is assigned to each of the clutch actuator valves (KV1, KV2). Hydraulic control device according to one of the preceding claims, characterized in that the pressure control valve (VP1, VP2) has an outlet (36), the outlet being connected to a tank (10), the leakage points (24, 25) being arranged or designed in this way are, so that the leakage points (24, 25) connect the pressure connection (P) and the outlet (36) to one another. Hydraulic control device according to claim 4 , characterized in that the receptacle (28) has an annular channel (40, 42) forming the leakage point (24, 25), the annular channel (40, 42) connecting the pressure connection (P) to the outlet (36). Hydraulic control device according to claim 4 or 5 , characterized in that the receptacle (28) has at least one recess (38) or groove (39, 43), the recess (38) or the groove (39, 43) connecting the pressure connection (P) with an outlet (36) connects.

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