CN113389888A

CN113389888A - Valve device for a hydraulic control device of a transmission of a motor vehicle

Info

Publication number: CN113389888A
Application number: CN202110266678.4A
Authority: CN
Inventors: F·斯塔特; F·兰根巴赫; R·诺瓦克
Original assignee: ZF Friedrichshafen AG
Current assignee: ZF Friedrichshafen AG
Priority date: 2020-03-11
Filing date: 2021-03-11
Publication date: 2021-09-14
Also published as: DE102020203132A1

Abstract

The invention relates to a valve device (5) for a hydraulic control device (4) of a transmission (3) of a motor vehicle (1). The valve device (5) comprises: a first damping valve (7) having a piston (31) which is prestressed by means of a prestressing force; a second damping valve (8) having a piston (41) which is prestressed by means of a prestressing force; and a first multiplex valve (6). The oil quantity pushed out by the shifting element (24) can be collected in a respective one of the damping valves (7/8) depending on the shift position of the multiplex valve (6), whereby the damping valve (7/8) concerned from a certain volume start is in the end stop position and the shifting element (24) can only be pushed out (slowly adjusted) by means of the orifice (36).

Description

Valve device for a hydraulic control device of a transmission of a motor vehicle

Technical Field

The present invention relates to a valve device for a hydraulic control device of a transmission of a motor vehicle. The invention is also directed to a hydraulic control device having the valve device, a transmission having the hydraulic control device, and a motor vehicle having the transmission.

Background

The following transmissions are known from the prior art: in these transmissions, the system pressure is directed to the dogs by a dog valve (Klauenventil). However, such transmissions typically do not provide an end position damper for reducing the speed of adjustment (shortly before the end stop position). Thus, depending on the jaw speed, acoustic problems often arise when the jaws are inserted.

Disclosure of Invention

The objects of the present invention can be seen as: an end position damper is provided which reduces the generation of noise when a shifting element, in particular a pawl, is inserted.

According to the invention, a central end position damper inside the HSG for a plurality of clamping jaws is proposed. The HSG represents a hydraulic control device here. The end position damper can be realized by means of a valve arrangement which makes it easier to find the intermediate position in the double-acting catch. In particular, HSG integrated damping valves for end position dampers of selector levers or claw clutches are proposed.

In this sense, according to a first aspect of the invention, a valve device for a hydraulic control device of a transmission of a motor vehicle is proposed. The valve device includes: a first damping valve having a piston pre-tensioned by a pre-tensioning force; a second damping valve having a piston pre-tensioned by a pre-tensioning force; and a first multiplex valve (Multiplexerventil). The "first" multiplex valve may be disposed next to an optional "second" multiplex valve described further below.

The first multi-way selector valve, in particular a valve slide (ventilschiber) of the multi-way selector valve, can be brought into a first switching position and a second switching position. In the first switching position, the first multiplex valve supplies the second damping valve with oil pushed out when a first shift element of the transmission is actuated. In the second shift position, the first multiplex valve supplies the oil pushed out when the first shift element is actuated to the first damping valve.

The first damping valve is configured to: when the first multiplex valve is in the second switching position, oil contained by the first multiplex valve is applied to the piston of the first damping valve, so that the piston of the first damping valve is displaced to an end stop position against the preload force, wherein the piston of the first damping valve releases a port of the first damping valve, so that the oil can escape via the port and flow out into a tank via a first orifice. Thus, the oil quantity pushed out of the first shifting element (e.g. the dog) can be collected in the first damping valve, whereby the first damping valve is in the end stop position from a certain volume and the shifting element can only be pushed out (slowly adjusted) by the (smaller) first orifice.

Further, the first damping valve is configured to: when the first multiplex valve is located at the first switching position, the piston of the first damping valve is displaced to an initial position by the preload force. The previously pressurized piston of the first damping valve can thus push back the oil volume in the direction of the tank by means of the pretension via the first multi-way switching valve. The first damping valve is then again in its initial position, which is prestressed.

The second damper valve is configured to: when the first multiplex valve is in the first switching position, oil contained by the first multiplex valve is applied to the piston of the second damping valve, so that the piston of the second damping valve is displaced to an end stop position against the preload force, wherein the piston of the second damping valve releases a port of the second damping valve, so that the oil can spill out via the port and flow out into the oil tank through the first orifice. Thus, the oil quantity pushed out of the first shifting element (e.g. the dog) can also be collected in the second damping valve, whereby the second damping valve is in the end stop position from a certain volume and the shifting element can only be pushed out (slowly adjusted) by the (smaller) first orifice.

Further, the second damping valve is configured to: when the first multiplex valve is located at the second switching position, the piston of the second damping valve is displaced to an initial position by the preload force. The previously pressurized piston of the second damping valve can thus push back the oil volume in the direction of the tank by means of the pretension via the first multi-way switching valve. The second damping valve is then again in its initial position, which is prestressed.

The first shifting element can be in particular a shift lever or a dog clutch.

In one embodiment, the first shifting element can be a double-acting dog clutch having a first dog and a second dog. Here, the first multiplex valve may be configured in the first switching position for: receiving oil under system pressure from the hydraulic control device and supplying it to a second interface of the first shift element for actuating the first shift element such that the second dog is displaced in a first direction; and receiving oil pushed out by the first dog of the dog clutch when the second dog is actuated from the first interface of the dog clutch and supplying it to the second damping valve.

Further, the first multiplex valve may be configured, when it is in the second switching position, to: receiving oil at the system pressure from the hydraulic control device and supplying it to a first interface of the first shift element for actuating the first shift element such that a first dog of the dog clutch is displaced in a second direction extending opposite to the first direction; and receiving oil pushed out by a second dog of the dog clutch when the first dog is actuated from a second interface of the dog clutch and supplying it to the first damping valve.

Furthermore, when the piston of the first damping valve is in the end stop position, the first damping valve can accommodate the volume of oil that has been pushed out by the double-acting dog clutch when one of the dogs has performed a half stroke. Alternatively or additionally, the second damping valve can also accommodate the volume of oil that has been pushed out by the double-acting dog clutch when one of the dogs has performed a half stroke when its piston is in the end stop position. This embodiment makes it easier to find the dog position (intermediate position in double-acting dog clutches). In the neutral position, none of the two pawls of the double-acting pawl clutch is engaged.

In another embodiment, the double-acting dog clutch comprises a hydraulic cylinder with a differential piston. In the case of using a differential piston, different amounts of oil are moved in order to displace the first and second pawls. This can be formed by different damping valves. The volume of oil to be collected can then be set by the geometry of the damping valve.

In one embodiment, the valve device can be connected to several shifting elements. In this case, the damping effect can be transmitted to further shift elements of the transmission, in particular to further dogs, by means of at least one further multiplex valve. No other damper valve is required. Thus, additional jaws can be pressurized by means of an additional second multiplex valve (and a magnetic valve for actuating the additional multiplex valve) by means of the same damping valve (first damping valve and second damping valve). Finally, only the first shifting element (e.g., the first dog clutch) and the second shifting element (e.g., the second dog clutch) are shifted by means of the second multiplex valve. Therefore, it is not necessary to install an additional damping valve. In this sense, the valve arrangement comprises in a further embodiment a second multiplex valve, wherein the second multiplex valve: is arranged between the first multiplex valve and the first shift element; connecting the first multiplex valve with the first shifting element in a first shift position; and in a second shift position, the first multiplex valve is connected to a second shifting element of the transmission.

According to a second aspect of the present invention, a hydraulic control device is provided. The hydraulic control apparatus includes a valve apparatus according to the first aspect of the invention.

According to a second aspect of the invention, a transmission, in particular an automatic transmission, for a motor vehicle is provided. The transmission includes the hydraulic control apparatus according to the second aspect of the invention.

According to a fourth aspect of the invention, there is provided a motor vehicle comprising a transmission according to the third aspect of the invention. Motor vehicles driven by a motor are for example cars (e.g. passenger cars weighing less than 3.5 t), motorcycles, mopeds, bicycles, electric bicycles or electric scooters (acronyms for pedal-powered vehicles), buses or trucks (e.g. weighing more than 3.5 t).

Drawings

Embodiments of the invention will be explained in more detail below with the aid of schematic drawings, in which identical or similar elements are provided with the same reference symbols. In the drawings:

fig. 1 shows a vehicle having an automatic transmission, which includes an embodiment of a valve device according to the invention,

figure 2 shows a hydraulic wiring diagram for a valve device used in the automatic transmission according to figure 1,

fig. 3 shows a schematic, partial longitudinal section of a damping valve for the valve device according to fig. 2, with the piston slide of the damping valve in a prestressed initial position,

FIG. 4 shows a schematic partial longitudinal section of the damping valve according to FIG. 3, with the piston slide of the damping valve in the end stop position, an

Fig. 5 shows a hydraulic connection diagram for an alternative valve device for use in the automatic transmission according to fig. 1.

Detailed Description

Fig. 1 shows a motor vehicle 1, in the example shown a passenger motor vehicle (Pkw). The motor vehicle 1 comprises a combustion-powered engine 2 which drives the motor vehicle 1 by means of an automatic transmission 3 having a hydraulic control device 4 with a valve device 5. Fig. 2 shows a detail of the valve arrangement 5, which comprises a first multiplex valve 6, a first damping valve 7 and a second damping valve 8.

The structure of the multiplex valve 6 is first described in detail below. The damping

valves

7 and 8 and the other elements of the valve device 5 are discussed subsequently. On this basis, the mode of operation of the valve device 5 in conjunction with the first dog clutch 24 and with the second dog clutch 48 (fig. 5) is described.

The first multiplex valve 6 is a selector valve including a valve housing 10 and a valve slider 11. The valve slide 11 can be adjusted back and forth in the valve housing 10 along the longitudinal axis L of the first multiplex valve 6 in mutually opposite axial directions x1 (first direction) and x2 (second direction). The valve slide 11 is prestressed in the initial position (first switching position) shown in fig. 2 by means of a restoring element in the form of a spring element 12. The spring element 12 is arranged in the region of the first end side S1 of the first multiplex valve 6.

The first multiple switch valve 6 has eleven valve rings 9.1 to 9.11 arranged at a distance from one another along the longitudinal axis L. The valve rings 9.1 to 9.11 can be formed by a valve housing 10. The valve rings 9.1 to 9.11 are designed to be hollow on the inside and form valve recesses 13.1 to 13.11, respectively, which extend further outward in the radial direction r of the first multiple-way valve 6 than the longitudinal bores 14 of the valve housing 10, which extend in the longitudinal direction L of the multiple-way valve 6. The valve housing 10 also has a connection 15.1 to 15.11 in the region of each of the valve recesses 13.1 to 13.11, which is connected to the valve recess 13.1 to 13.11 concerned.

In the region of the first end side S1, a first valve ring 9.1, a first valve recess 13.1 and a first connection 15.1 are arranged. The first connection 15.1 is blind-connected in the exemplary embodiment shown or can be connected to an unpressurized tank.

The second valve ring 9.2, the second valve recess 13.2 and the second connection 15.2 are arranged adjacent to one another and at a distance in the second direction x 2. The second port 15.2 can serve in particular as an oil inlet, so that oil can fill the second valve recess 13.2.

A third valve ring 9.3, a third valve recess 13.3 and a third port 15.3 are arranged adjacent to one another and at a distance in the second direction x 2. The third connection 15.3 can be used as an oil inlet, so that oil can fill the third valve recess 13.3. Furthermore, the third connection 15.3 can also be used as an oil outlet, so that oil can be drained from the third valve recess 13.3.

A fourth valve ring 9.4, a fourth valve recess 13.4 and a fourth port 15.4 are arranged adjacent to one another and at a distance in the second direction x 2. The fourth port 15.4 can serve in particular as an oil outlet, so that oil can be drained from the fourth valve recess 13.4. The fourth port 15.4 of the first multiplex valve 6 is connected via the second port 46 to the unpressurized tank T.

The fifth valve ring 9.5, the fifth valve recess 13.5 and the fifth connection 15.5 are arranged adjacent to one another and at a distance from one another in the second direction x 2. The fifth port 15.5 can serve in particular as an oil outlet, so that oil can be drained from the fifth valve recess 13.5.

The sixth valve ring 9.6, the sixth valve recess 13.6 and the sixth connection 15.6 are arranged adjacent to one another and at a distance from one another in the second direction x 2. The sixth port 15.6 can serve in particular as an oil inlet, so that oil can fill the sixth valve recess 13.6. The sixth connection 15.6 is connected in the exemplary embodiment shown to a hydraulic line, in which the oil is at a system pressure pSys that can be provided by the hydraulic control device 4, in particular by means of an additional valve for controlling the pressure.

The seventh valve ring 9.7, the seventh valve recess 13.7 and the seventh port 15.7 are arranged adjacent to one another and at a distance in the second direction x 2. The seventh connection 15.7 can serve in particular as an oil outlet, so that oil can be drained from the seventh valve recess 13.7.

The eighth valve ring 9.8, the eighth valve recess 13.8 and the eighth connection 15.8 are arranged adjacent to one another and at a distance from one another in the second direction x 2. The eighth connection 15.8 can serve in particular as an oil outlet, so that oil can be drained from the eighth valve recess 13.8. The eighth port 15.8 of the first multiplex valve 6 is connected to the unpressurized tank T via the second port 46.

A ninth valve ring 9.9, a ninth valve recess 13.9 and a ninth connection 15.9 are arranged adjacent to one another and at a distance from one another in the second direction x 2. The ninth connection 15.9 can be used as an oil inlet, so that oil can fill the ninth valve recess 13.9. Furthermore, the ninth connection 15.9 can also be used as an oil outlet, so that oil can be drained from the ninth valve recess 13.9.

A tenth valve ring 9.10, a tenth valve recess 13.10 and a tenth connection 15.10 are arranged adjacent to and at a distance in the second direction x 2. The tenth connection 15.10 may serve as an oil inlet, so that oil may fill the tenth valve recess 13.10.

Finally, an eleventh valve ring 9.11, an eleventh valve recess 13.11 and an eleventh connection 15.11 are arranged adjacent to one another and at a distance in the second direction x2 in the region of the second end side S2 of the first multiplex valve 6. The eleventh connection 15.11 can serve as an oil inlet, so that oil can fill the eleventh valve recess 13.11.

The valve slide 11 has a piston rod 16. A plurality of

pistons

17, 18, 19 and 20 are arranged on the piston rod 16. The

respective piston

17, 18, 19 and 20 is in this case firmly connected to the piston rod 16. The

pistons

17, 18, 19 and 20 extend further outward in the radial direction r of the valve slide 11 than the piston rod 16. The diameters of the

pistons

17, 18, 19 and 20 are selected such that they can be moved back and forth in the longitudinal direction L within the longitudinal bore 14 of the valve housing 10, to be precise in particular (to a large extent) in a sealed and friction-free manner. The valve recesses 13.1 to 13.11 in turn extend further outward in the radial direction r of the valve slide 11 than the

pistons

17, 18, 19 and 20.

Here, the first piston 17 is arranged in the region of the first end side S1. Furthermore, the second piston 18 is arranged adjacent to the first piston 17 and at an axial distance from the first piston 17 in the second direction x 2. Further, the third piston 19 is arranged adjacent to the second piston 18 and at an axial distance from the second piston 18 in the second direction x 2. Finally, a fourth piston 20 is arranged adjacent to the third piston 19 in the region of the second end side S2.

The first piston 17 is pot-shaped and forms an inner space 21 and an inner pressure surface 22, which extends in the radial direction r (and thus transversely to the longitudinal direction L). The spring element 12 generates a pretensioning force acting in the second direction x2 on the inner pressure surface 22 of the first piston 17. The first valve recess 13.1 is connected to the interior 21 of the first piston 17 via the longitudinal bore 14.

The first piston 17 seals the first valve recess 13.1 relative to the second valve recess 13.2 independently of the position of the valve slide 11 relative to the valve body 10 (i.e. in particular in the first switching position and in the second switching position described below), so that there is no connection between the first valve recess 13.1 and the second valve recess 13.2. As a result, the first interface 15.1 is also not connected to the second interface 15.2. The feature "connected" is to be understood in particular as: the elements which are connected to one another are correspondingly connected to one another in a hydraulically guided manner, i.e. oil can flow from one element to the other and vice versa, as appropriate. Conversely, the feature "disconnected" or "not connected" can be understood in particular as: accordingly, elements which are disconnected from one another are not connected to one another in a hydraulically guided manner, i.e. no oil can flow from one element to the other and vice versa, as appropriate.

In a first switching position of the valve slide 11, which is illustrated in fig. 2, the valve slide 11 is in a first switching position, in which the fourth piston 20 is located in the eleventh valve recess 13.11, biased by the spring element 12.

In the first switching position, the second piston 18 releases the connection between the third valve recess 13.3 and the fourth valve recess 13.4. Thereby, the third interface 15.3 is connected to the fourth interface 15.4. In the initial position, the second piston 18 also seals the fourth valve recess 13.4 with respect to the fifth valve recess 13.5, so that the fourth valve recess 13.4 is not connected to the fifth valve recess 13.5. The fourth interface 15.4 is thus also not connected to the fifth interface 15.5.

In the first switching position, the third piston 19 releases the connection between the sixth valve recess 13.6 and the seventh valve recess 13.7. Thereby, the sixth interface 15.6 is connected to the seventh interface 15.7. In the initial position, the third piston 19 also seals the seventh valve recess 13.7 with respect to the eighth valve recess 13.8, so that the seventh valve recess 13.7 is not connected to the eighth valve recess 13.8. The seventh interface 15.7 is thus also not connected to the eighth interface 15.8.

In the first switching position, the fourth piston 20 releases the connection between the ninth valve recess 13.9 and the tenth valve recess 13.10. Thereby, the tenth interface 15.10 is connected with the ninth interface 15.9. The fourth piston 20 also seals the tenth valve recess 13.10 relative to the eleventh valve recess 13.11 independently of the position of the valve slide 11 relative to the valve body 10 (i.e. in particular in the first and second switching positions), so that there is no connection between the tenth valve recess 13.10 and the eleventh valve recess 13.11. The tenth interface 15.10 is thus also not connected to the eleventh interface 15.11.

The valve slide 11 can be moved in the first direction x1 against the prestress of the spring element 12, so that the valve slide 11 moves out of the first switching position according to fig. 2 and assumes the second switching position. In this connection, a pilot pressure pmV (oil pressure), which can be provided in particular by a magnetic valve, can be applied at the eleventh connection 15.11. The pilot pressure pmV exerts a displacement force acting against the pretension force on the hydraulically effective end face 23 of the valve slide 11.

In the second switching position, the second piston 18 closes the connection between the third valve recess 13.3 and the fourth valve recess 13.4. Thereby, the third interface 15.3 is disconnected from the fourth interface 15.4. Instead, the second piston 18 releases the connection between the fifth valve recess 13.5 and the sixth valve recess 15.6. Thereby, the fifth interface 15.5 is connected to the sixth interface 15.6. Furthermore, the first piston 17 releases the connection between the second valve recess 13.2 and the third valve recess 13.3 in the second switching position. Thereby, the second interface 15.2 is connected to the third interface 15.3.

Furthermore, the fourth piston 20 closes the connection between the ninth valve recess 13.9 and the tenth valve recess 13.10 in the second switching position. Thereby, the ninth interface 15.9 is disconnected from the tenth interface 15.10. Instead, the third piston 19 releases the connection between the eighth valve recess 13.8 and the ninth valve recess 13.9 in the second switching position. The eighth interface 15.8 is thereby connected to the ninth interface 15.9. Furthermore, the third piston closes the connection between the sixth valve recess 13.6 and the seventh valve recess 13.7 in the second switching position. Thereby, the sixth interface 15.6 is disconnected from the seventh interface 15.7.

The first shift switch 6 is connected to a shifting element in the form of a double-acting dog clutch 24, which comprises a first dog K1 and a second dog K2. For actuating the double-acting dog clutch 24, it may, for example, comprise a double-acting hydraulic cylinder having two opposite piston faces, to which oil is applied. The double-acting dog clutch 24 has a first connection 25 and a second connection 26. The first connection 25 of the double-acting dog clutch 24 is connected to the fifth connection 15.5 and the tenth connection 15.10 of the multiplex valve 6. The second port 26 of the double-acting dog clutch 24 is connected to the second port 15.2 and the seventh port 15.7 of the multiplex valve 6.

The first damping valve 7 has a first port 27, a second port 28, a third port 29, a valve housing 30, a first piston 31 and a restoring element in the form of a spring element 32. The first port 27 of the first damping valve 7 is connected to the third port 15.3 of the first multiplex valve 6. The second connection 27 of the first damping valve 7 is connected to a first port 36 which leads to the unpressurized tank T. The first piston 31 is pot-shaped and forms an inner space 33 and an inner pressure surface 34, which extends in the radial direction r of the first damping valve 7. The spring element 32 generates a preload force on the pressure surface 34 of the piston 31, so that the piston 31 is preloaded into the initial position shown in fig. 2. In the initial position, the piston 31 of the first damping valve 7 disconnects the first connection 27 from the second connection 28. If the piston 31 of the first damping valve 7 has been displaced from the initial position into the end stop position (see the position of the piston 41 of the second damping valve 8 shown in fig. 2), the piston 31 of the first damping valve 7 releases the connection between the first connection 27 and the second connection 28. The diameter of the first piston 31 is selected such that the piston 31 can be moved back and forth in the longitudinal direction L within the axial bore 35 of the valve housing 30, to be precise in particular (to a large extent) in a sealed and friction-free manner. The interior 33 of the first piston 31 is connected via an axial bore 35 to a third connection 29, which is in turn connected to an unpressurized tank T, so that the interior 33 and the axial bore 35 are vented on the side of the interior 33.

The second damping valve 8 can be implemented identically to the first damping valve 7. The second damping valve 8 has a first port 37, a second port 38, a third port 39, a valve housing 40, a second piston 41 and a restoring element in the form of a spring element 42. The first port 37 of the second damping valve 8 is connected to the ninth port 15.9 of the first multiplex valve 6. The second connection 37 of the second damping valve 8 (like the second connection 27 of the first damping valve 7) is connected to a first port 36 which leads to the unpressurized tank T. The piston 41 is pot-shaped and forms an inner space 43 and an inner pressure surface 44, which extends in the radial direction r of the second damping valve 8. The spring element 42 generates a preload force acting on the pressure surface 44 of the piston 41, so that the piston 41 is preloaded in the initial position (see fig. 3 for this purpose and the position of the piston 31 of the first damping valve 7 shown in fig. 2). In the initial position, the piston 41 of the second damping valve 8 disconnects the first connection 37 from the second connection 38. Fig. 2 shows the piston 41 of the second damping valve 8 in its end stop position. In the end stop position, the piston 41 of the second damping valve 8 releases the connection between the first connection 37 and the second connection 38. The diameter of the piston 41 is selected such that the piston 41 can be moved back and forth in the longitudinal direction x within the axial bore 45 of the valve housing 40, to be precise in particular (to a large extent) in a sealed and friction-free manner. The interior 43 of the piston 41 is connected via an axial bore 45 to a third port 39, which is in turn connected to an unpressurized tank T, so that the interior 43 and the axial bore 45 are vented on the side of the interior 43.

If the valve slide 11 of the first multiple switching valve 6 is in the first switching position shown in fig. 2, oil at a system pressure pSys (of a few bar, for example) flows through the sixth valve recess 13.6, the longitudinal bore 14 and the seventh valve recess 13.7 of the first multiple switching valve 6. Since the seventh connection port 15.7 of the first multiplex valve 6 is connected to the second connection port 26 of the dog clutch 24, oil under system pressure is supplied to the dog clutch 24, so that the second dog K2 is actuated. By actuating or pushing the second pawl K2, a corresponding amount of oil is pushed out on the other side by the first connection 25 of the dog clutch 24. This pushed-out oil is led to the first port 37 of the second damping valve 8 via the tenth valve recess 13.10, the longitudinal bore 14 and the ninth valve recess 13.9 of the first multiplex valve 6. From there, the oil enters the axial bore 45 of the valve housing 40 of the second damping valve 8. The oil builds up a pressure in the axial bore 45 and thereby displaces the piston 41 of the second damping valve 8 from the initial position shown in fig. 3 into the end stop position shown in fig. 2 and 4, so that the oil can escape through the second connection 38 of the second damping valve 8. An exemplary oil flow is illustrated in fig. 4 by means of arrows 49.

The oil quantity pushed out of the first catch K1 is therefore collected in the second damping valve 8, whereby the piston 41 of the second damping valve 8 is in the end stop position from a certain volume and the first catch K1 can only be pushed out (slowly adjusted) by means of the second connection 38 and the (smaller) first orifice 36. Thus, the displacement of the piston 41 against the pretensioning force of the spring element 42 of the second damping valve 8 (quick adjustment) creates less resistance to oil than pushing out into the unpressurized tank T by means of the second connection 38 and the first orifice 36. In other words, the second damping valve 8 collects the outflowing oil of the first dog K1. Once the piston 41 of the second damping valve 8 is in the end stop position, the oil must flow into the tank T through the first orifice 36 (transition from fast to slow regulation). The displacement VHub of the second damping valve shown in fig. 2 can be determined by half-stroking the second catch 2 and subsequently changing to a slow displacement. Therefore, the middle position of the second jaw K2 (and thus also the first jaw K1) can be found more easily. This mode of operation of the second damping valve is active when the second pawl K2 is pressurized as described above, i.e. in particular when the valve slide 11 of the first multiplex valve 6 is in the first switching position shown in fig. 2.

If the valve slide 11 of the first multiple-way switching valve 6 is displaced from the first switching position shown in fig. 2 into the second switching position described above, oil is no longer supplied to the first connection 37 of the second damping valve 8 by the first catch K1. Instead, the piston 41 of the second damping valve 8 presses the remaining oil by means of the spring force of the spring element 42 via the ninth valve recess 13.9, the longitudinal bore 14 and the eighth valve recess 13.8 of the first multiplex valve 6 and via the second orifice 46 into the unpressurized tank T until the piston 41 is again in its initial position.

When the valve slide 11 of the first multi-way valve 6 is in the second switching position, oil at the system pressure pSys (of a few bar, for example) continues to flow through the sixth valve recess 13.6, the longitudinal bore 14 and the fifth valve recess 13.5 of the first multi-way valve 6. Since the fifth port 15.5 of the first multiplex valve 6 is connected to the first port 25 of the dog clutch 24, oil under system pressure is supplied to the dog clutch 24, so that the first dog K1 is actuated. By actuating or pushing the first pawl K1, a corresponding amount of oil is pushed out on the other side by the second port 26 of the dog clutch 24. This pushed out oil is guided via the second valve recess 13.1, the longitudinal bore 14 and the third valve recess 13.3 of the first multiplex valve 6 to the first connection 27 of the first damping valve 7. The oil builds up a pressure in the axial bore 35 and thereby displaces the piston 31 of the first damping valve 7 from the initial position shown in fig. 2 to the end stop position (see the position shown in fig. 2 of the piston 41 of the second damping valve 8).

The oil quantity pushed out of the second catch K2 is thus collected in the first damping valve 7, whereby the piston 31 of the first damping valve 7 is in the end stop position from a certain volume and the second catch K2 can only be pushed out (slowly adjusted) by the (smaller) first orifice 36. Thus, the displacement of the piston 31 against the prestress of the spring element 32 results in less resistance to oil than pushing into the unpressurized tank T by means of the second connection 28 and the first orifice 36. In other words, the first damping valve 7 collects the outflowing oil of the second dog K2. As soon as the piston 31 of the first damping valve 7 is in the end stop position, oil must flow into the tank T through the second connection 28 and the first orifice 36 (change from quick to slow regulation). The displacement of the first damping valve 7 can be determined by half-stroking the first catch K1 and subsequently switching to a slow displacement. Therefore, the intermediate position of the first dog K1 (and thus also the second dog K2) can be found more easily.

If the valve slide 11 of the first multiplex valve 6 is in the first switching position shown in fig. 2, oil is no longer supplied by the second claw K2 to the first connection 27 of the first damping valve 7. Instead, the piston 31 of the first damping valve 7 presses the remaining oil by means of the spring force of the spring element 32 via the third valve recess 13.3, the longitudinal bore 14 and the fourth valve recess 13.4 of the first multiplex valve 6 and via the second orifice 46 into the unpressurized tank T until the piston 31 is again in its initial position shown in fig. 2.

Fig. 5 shows the valve arrangement according to fig. 2, wherein a second multiple-way switching valve 47 (reversing valve) is connected between the first multiple-way switching valve 6 and the first shifting element 24. In the first shift position shown in fig. 5, the first shifting element 24 is connected to the first multiplex valve 6, as shown in fig. 2 and described above. In the second shift position, the second multiplex valve 47 can be connected to the second shifting element 48, as has already been described above in connection with the first shifting element 24. In the illustrated exemplary embodiment, the second shifting element 48 is likewise a double-acting dog clutch having a third dog K3 and a fourth dog K4. The valve slide of the second multiplex valve 47 can be moved from the first switching position into the second switching position against the prestress of the spring element. In this connection, a pilot pressure pmV2 (oil pressure), which can be provided in particular by a magnetic valve, can be applied to the valve slide of the second multiplex valve 47. The pilot pressure pmV2 in this case exerts a displacement force acting against the pretensioning force on the hydraulically effective end face of the valve slide of the second multiplex valve 47.

List of reference numerals

K1 first jaw

K2 second jaw

K3 third jaw

K4 fourth jaw

L longitudinal axis of first multiple switch valve

pMV pilot pressure

pSys System pressure

radial direction of the slide block of the gamma valve

T-unpressurized oil tank

Displacement of VHub second damping valve

x longitudinal direction of piston of first/second damping valve

x1 first axial direction

x2 second axial direction

1 Motor vehicle

2 combustion power engine

3 automatic transmission

4 hydraulic control device

5-valve device

6 first multi-way change-over valve

7 first damping valve

8 second damping valve

9.1 to 9.11 valve rings

10 valve housing

11 valve slider

12 spring element

13.1 to 13.11 valve recess

14 longitudinal bore

15.1 to 15.11 interface

16 piston rod

17 first piston

18 second piston

19 third piston

20 fourth piston

21 inner space of first piston

22 internal pressure surface of the first piston

23 hydraulic effective end face

24 double-acting dog clutch

First interface of 25 claw clutch

Second interface of 26-claw clutch

27 first port of first damping valve

28 second port of first damping valve

29 third port of first damping valve

30 valve housing of first damping valve

31 piston of first damping valve

32 spring element of first damping valve

33 inner space of first damping valve

34 pressure surface of the first damping valve

35 axial bore of a valve housing of a first damping valve

36 first orifice

37 first port of second damping valve

38 second port of second damping valve

39 third port of second damping valve

40 valve housing of second damping valve

41 piston of second damping valve

42 spring element of a second damping valve

43 inner space of second damping valve

44 pressure surface of the second damping valve

45 axial bore of valve housing of second damping valve

46 second orifice

47 second multiple switching valve

48 double-acting clutch

49 oil flow through the second damping valve

Claims

1. A valve device (5) for a hydraulic control device (4) of a transmission (3) of a motor vehicle (1), said valve device (5) comprising: a first damping valve (7) having a piston (31) that is prestressed by means of a prestressing force; a second damping valve (8) having a piston (41) that is prestressed by means of a prestressing force; and a first multiplex valve (6),

wherein the first multiple switching valve (6)

-in a first switching position, supplying the second damping valve (8) with oil pushed out upon actuation of a first shifting element (24) of the transmission (3); and is

-supplying oil pushed out upon actuation of the first shift element (24) to the first damping valve (7) in a second shift position,

wherein the first damping valve (7) is configured for:

-when the first multiplex valve (6) is in the second switching position, applying oil contained by the first multiplex valve (6) to the piston (31) of the first damping valve (7) such that the piston (31) of the first damping valve (7) is displaced against the pretensioning force to an end stop position, wherein the piston (31) of the first damping valve (7) releases a port (28) of the first damping valve (7) such that the oil can escape via the port (28) and flow out into a tank (T) by means of a first orifice (36); and is

-displacing a piston (31) of the first damping valve (7) to an initial position by means of the pretension when the first multiplex valve (6) is in the first switching position,

wherein the second damping valve (8) is configured for:

-when the first multiplex valve (6) is in the first switching position, applying oil contained by the first multiplex valve (6) to the piston (41) of the second damping valve (8) such that the piston (41) of the second damping valve (8) is displaced against the pretensioning force to an end stop position, wherein the piston (41) of the second damping valve (8) releases a port (38) of the second damping valve (8) such that the oil can escape via the port (38) and flow out into the tank (T) via the first orifice (36); and is

-displacing the piston (41) of the second damping valve (8) to an initial position by means of the pretension when the first multiplex valve (6) is in the second switching position.

2. The valve arrangement (5) according to claim 1, wherein the first shifting element of the transmission (3) is a shift lever.

3. The valve device (5) as claimed in claim 1, wherein the shifting element (24) of the transmission (3) is a dog clutch (24).

4. The valve device (5) according to claim 3,

wherein the dog clutch (24) is a double-acting dog clutch (24) having a first dog (K1) and a second dog (K2),

wherein the first multiplex valve (6) is configured in the first switching position for:

-receiving oil at system pressure (pSys) from the hydraulic control device (4) and supplying it to a second interface (26) of the first shift element (24) for actuating the first shift element such that the second dog (K2) is displaced in a first direction; and is

-receiving oil from a first interface (25) of the dog clutch (24) pushed out by a first dog (K1) of the dog clutch when actuating the second dog (K2) and supplying it to the second damping valve (8),

wherein the first multiplex valve (6) is configured in the second switching position for:

-receiving oil at the system pressure (pSys) from the hydraulic control device (4) and supplying it to a first interface (25) of the first shift element (24) for actuating the first shift element such that a first dog (K1) of the dog clutch (24) is displaced in a second direction extending opposite to the first direction; and is

-receiving oil from a second interface (26) of the dog clutch (24) pushed out by a second dog (K2) of the dog clutch (24) when actuating the first dog (K1) and supplying it to the first damping valve (7).

5. The valve device (5) according to claim 4,

wherein the first damping valve (7) is able to accommodate the volume of oil that has been pushed out by the double-acting dog clutch (24) when one of the dogs (K1/K2) has performed half a stroke when the piston (31) of the first damping valve (7) is in an end stop position; and/or

Wherein the second damping valve (8) can accommodate a volume of oil that has been pushed out by the double-acting dog clutch (24) when one of the dogs (K1/K2) has performed a half stroke when the piston (41) of the second damping valve (8) is in an end stop position.

6. The valve device (5) according to claim 1, wherein the shifting element (24) of the transmission (3) is a double-acting dog clutch (24) comprising a hydraulic cylinder with a differential piston.

7. The valve device (5) according to claim 1, comprising a second multiplex valve (47), wherein the second multiplex valve (47):

-is arranged between the first multiplex valve (6) and the first shift element (24);

-connecting the first multiplex valve (6) with the first shift element (24) in a first shift position; and is

-connecting the first multiplex valve (6) with a second shift element (48) of the transmission (3) in a second switching position.

8. A hydraulic control device (4) comprising a valve arrangement (5) according to one of the preceding claims.

9. A transmission (3) for a motor vehicle (1), the transmission (3) comprising a hydraulic control device (4) according to claim 8.

10. A motor vehicle (1) comprising a transmission (3) according to claim 9.