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

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) preloaded by a preloading force, a second damping valve (8) having a piston (41) preloaded by a preloading force, and a first multiway valve (6). The amount of oil pushed out by a shift element (24) can be collected in the respective one of the damping valves (7 / 8) depending on the switching position of the multiway valve (6), whereby the damping valve (7 / 8) involved from a certain volume on is located in a final stop position and the shift element (24) can only be pushed out (slow adjustment) by an orifice (36).

Description

TECHNICAL FIELD

[0001] The present invention relates to a valve arrangement for a hydraulic control device of a transmission of a motor vehicle. The invention also targets a hydraulic control device having the valve arrangement, a transmission having the hydraulic control device and a motor vehicle having the transmission. BACKGROUND

[0002] From the prior art, transmissions are known in which the system pressure is guided to the claw by means of a claw valve. However, such transmissions usually do not provide a terminal position damper for reducing the adjustment speed (shortly before the end stop position). As a result, depending on the claw speed, an acoustic problem usually occurs upon insertion of the claw. SUMMARY

[0003] The object of the present invention can be seen in providing a terminal position damper which reduces the noise generation upon insertion of a shift element, in particular a claw.

[0004] According to the invention, a central and internal to the HSG terminal position damper for a plurality of claws is proposed. HSG here stands for hydraulic control device. The terminal position damper can be realized by means of a valve arrangement which enables easier finding of the intermediate position in double-acting claws. In particular, an HSG-integrated damper valve for a terminal position damper of a shift lever or claw clutch is proposed.

[0005] In this sense, according to a first aspect of the invention, a valve arrangement for a hydraulic control device of a transmission of a motor vehicle is proposed. The valve arrangement comprises a first damper valve having a piston preloaded by a preloading force, a second damper valve having a piston preloaded by a preloading force and a first multiplexer valve. The "first" multiplexer valve can be provided next to an optional "second" multiplexer valve which is described further below.

[0006] The first multiplexer valve, in particular the valve slide of the multiplexer valve, can be brought into a first switching position and a second switching position. In the first switching position, the first multiplexer valve supplies the oil pushed out upon actuation of a first shift element of the transmission to the second damper valve. In the second switching position, the first multiplexer valve supplies the oil pushed out upon actuation of the first shift element to the first damper valve.

[0007] The first damping valve is configured to displace a piston of the first damping valve against the pretensioning force into a final stop position when the first multiplex valve is in the second switching position, wherein the piston of the first damping valve releases an interface of the first damping valve such that the oil can overflow via the interface and flow out into the oil tank via the first orifice. Thus, the amount of oil pushed out of the first shift element, e.g. a dog, can be collected in the first damping valve, whereby from a certain volume the first damping valve is in the final stop position and the shift element can only be pushed out (slow adjustment) via the (smaller) first orifice.

[0008] Furthermore, the first damping valve is configured to displace a piston of the first damping valve into an initial position by means of the pretensioning force when the first multiplex valve is in the first switching position. Thus, the previously pressurized piston of the first damping valve can push the oil volume back via the first multiplex valve in the direction of the oil tank by means of the pretensioning force. The first damping valve is then again in its initially pretensioned position.

[0009] The second damping valve is configured to displace a piston of the second damping valve against the pretensioning force into a final stop position when the first multiplex valve is in the first switching position, wherein the piston of the second damping valve releases an interface of the second damping valve such that the oil can overflow via the interface and flow out into the oil tank via the first orifice. Thus, the amount of oil pushed out of the first shift element, e.g. a dog, can also be collected in the second damping valve, whereby from a certain volume the second damping valve is in the final stop position and the shift element can only be pushed out (slow adjustment) via the (smaller) first orifice.

[0010] Furthermore, the second damping valve is configured to displace a piston of the second damping valve into an initial position by means of the pretensioning force when the first multiplex valve is in the second switching position. Thus, the previously pressurized piston of the second damping valve can push the oil volume back via the first multiplex valve in the direction of the oil tank by means of the pretensioning force. The second damping valve is then again in its initially pretensioned position.

[0011] The first shift element can be in particular a shift lever or a dog clutch.

[0012] In one embodiment, the first shift element can be a double-acting dog clutch having a first dog and a second dog. Here, the first multiplex valve can be configured in the first switching position to receive oil at system pressure from the hydraulic control device and to supply 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 to receive oil from a first interface of the dog clutch, which is pushed out by the first dog of the dog clutch upon actuating the second dog, and to supply it to the second damper valve.

[0013] Furthermore, the first multiplex valve can be configured in the second switching position to receive oil at system pressure from the hydraulic control device and to supply it to a first interface of the first shift element for actuating the first shift element such that the first dog of the dog clutch is displaced in a second direction extending opposite to the first direction, and to receive oil from a second interface of the dog clutch, which is pushed out by the second dog of the dog clutch upon actuating the first dog, and to supply it to the first damper valve.

[0014] Furthermore, the first damper valve can accommodate the volume of oil that has been pushed out by the double-acting dog clutch when one of the dogs has carried out a half stroke when the piston of the first damper valve is in the end stop position. Alternatively or additionally, the second damper 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 carried out a half stroke when the piston of the second damper valve is in the end stop position. This embodiment can more easily find a dog position (in a double-acting dog clutch, the intermediate position). In the intermediate position, none of the two dogs of the double-acting dog clutch is engaged.

[0015] In another embodiment, the double-acting dog clutch comprises a hydraulic cylinder having a differential piston. In the case of using a differential piston, different volumes of oil are moved in order to displace the first dog and the second dog. This can be formed by different damper valves. The volume of oil to be collected can then be set by the geometry of the damper valves.

[0016] In one embodiment, the valve arrangement can be connected with a plurality of shift elements. Here, the damping action described above can be transmitted to further shift elements of the transmission, in particular to further claws, by means of at least one further multi-way valve. No further damping valve is required. Thus, the further claws can be pressurized by means of the same damping valves (first and second damping valve) by means of an additional second multi-way valve (and a magnetic valve for actuating the further multi-way valve). Switching between the first shift element (e.g. first dog clutch) and the second shift element (e.g. second dog clutch) is finally only carried out by means of the second multi-way valve. Thus, no additional damping valve has to be installed. In this sense, the valve arrangement comprises in a further embodiment a second multi-way valve, wherein the second multi-way valve is arranged between the first multi-way valve and the first shift element, connects the first multi-way valve with the first shift element in a first switching position, and connects the first multi-way valve with a second shift element of the transmission in a second switching position.

[0017] According to a second aspect of the present application, a hydraulic control arrangement is provided. The hydraulic control arrangement comprises a valve arrangement according to the first aspect of the present application.

[0018] According to a second aspect of the present application, a transmission, in particular an automatic transmission, for a motor vehicle is provided. The transmission comprises a hydraulic control arrangement according to the second aspect of the present application.

[0019] According to a fourth aspect of the present application, a motor vehicle is provided, the motor vehicle comprising a transmission according to the third aspect of the present application. The motor vehicle driven by a motor is for example a car (e.g. a passenger motor vehicle with a weight of less than 3.5 t), a motorcycle, a moped, a motorized bicycle, a bicycle, an electric bicycle or an electric scooter (abbreviation for pedal electric vehicle), a bus (e.g. with a weight of more than 3.5 t) or a lorry. BRIEF DESCRIPTION OF DRAWINGS

[0020] Embodiments of the present application will be elucidated in more detail with the aid of the enclosed schematic drawings, in which equal or similar elements are provided with equal reference numerals. In the drawings:

[0021] Figure 1 A vehicle with an automatic transmission comprising an embodiment of a valve arrangement according to the present application is shown,

[0022] Figure 2 A hydraulic wiring diagram of a valve arrangement for use in an automatic transmission according to Figure 1 the present application is shown,

[0023] Figure 3 A vehicle with an automatic transmission comprising an embodiment of a valve arrangement according to the present application is shown, Figure 2schematic partial longitudinal sectional view of a damping valve of the valve arrangement according to

[0024] Figure 4 a schematic partial longitudinal sectional view of a damping valve according to Figure 3

[0025] Figure 5 a hydraulic wiring diagram of an alternative valve arrangement for use in an automatic transmission according to Figure 1 DETAILED DESCRIPTION

[0026] Figure 1 A motor vehicle 1, in the example shown a passenger motor vehicle (Pkw), is shown. The motor vehicle 1 comprises a combustion engine 2 which drives the motor vehicle 1 by means of an automatic transmission 3 having a hydraulic control device 4 with a valve arrangement 5. Figure 2 Details of the valve arrangement 5 are shown, which comprises a first multi-way valve 6, a first damping valve 7 and a second damping valve 8.

[0027] In the following, the structure of the multi-way valve 6 is described in detail first. Subsequently, the damping valves 7 and 8 and further elements of the valve arrangement 5 are discussed. On this basis, the mode of operation of the valve arrangement 5 in cooperation with the first claw clutch 24 and with the second claw clutch 48 is described. Figure 5

[0028] The first multi-way valve 6 is a switching valve comprising a valve housing 10 and a valve spool 11. The valve spool 11 can be adjusted back and forth within the valve housing 10 along a longitudinal axis L of the first multi-way valve 6 in axial directions x1 (first direction) and x2 (second direction) opposite to each other. The valve spool 11 is pre-tensioned in an initial position (first switching position) shown by means of a return element in the form of a spring element 12. The spring element 12 is arranged in the region of a first end side S1 of the first multi-way valve 6. Figure 2

[0029] ​​​​The first multi-way switching valve 6 has eleven valve rings 9.1 to 9.11 which are arranged at a distance from one another in the longitudinal direction 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 internally hollow and each form a valve recess 13.1 to 13.11 which extends further outwards in the radial direction r of the first multi-way switching valve 6 than the longitudinal bore 14 of the valve housing 10 which extends in the longitudinal direction L of the multi-way switching valve 6. The valve housing 10 also has in the region of each of the valve recesses 13.1 to 13.11 an interface 15.1 to 15.11, respectively, which is connected to the valve recess 13.1 to 13.11 concerned.

[0030] In the region of the first end side S1 there is arranged the first valve ring 9.1, the first valve recess 13.1 and the first interface 15.1. The first interface 15.1 is in the embodiment shown a blind connection or can be connected to an unpressurised oil tank.

[0031] The second valve ring 9.2, the second valve recess 13.2 and the second interface 15.2 are arranged adjacent to one another at a distance in the second direction x2. The second interface 15.2 can in particular be used as an input for oil, so that the second valve recess 13.2 can be filled with oil.

[0032] The third valve ring 9.3, the third valve recess 13.3 and the third interface 15.3 are arranged adjacent to one another at a distance in the second direction x2. The third interface 15.3 can be used as an input for oil, so that the third valve recess 13.3 can be filled with oil. Furthermore, the third interface 15.3 can also be used as an output for oil, so that oil can be discharged from the third valve recess 13.3.

[0033] The fourth valve ring 9.4, the fourth valve recess 13.4 and the fourth interface 15.4 are arranged adjacent to one another at a distance in the second direction x2. The fourth interface 15.4 can in particular be used as an output for oil, so that oil can be discharged from the fourth valve recess 13.4. The fourth interface 15.4 of the first multi-way switching valve 6 is connected to the unpressurised oil tank T by means of the second orifice 46.

[0034] The fifth valve ring 9.5, the fifth valve recess 13.5 and the fifth interface 15.5 are arranged adjacent to one another at a distance in the second direction x2. The fifth interface 15.5 can in particular be used as an output for oil, so that oil can be discharged from the fifth valve recess 13.5.

[0035] Arranged in an adjacent and at a distance in the second direction x2 are a sixth valve ring 9.6, a sixth valve recess 13.6 and a sixth interface 15.6. The sixth interface 15.6 can be used, inter alia, as an input for oil, so that the sixth valve recess 13.6 can be filled with oil. The sixth interface 15.6 is connected in the embodiment shown to a hydraulic line in which the oil is under a system pressure pSys which can be provided by the hydraulic control device 4, inter alia, by means of an additional valve for controlling the pressure.

[0036] Arranged in an adjacent and at a distance in the second direction x2 are a seventh valve ring 9.7, a seventh valve recess 13.7 and a seventh interface 15.7. The seventh interface 15.7 can be used, inter alia, as an output for oil, so that oil can be discharged from the seventh valve recess 13.7.

[0037] Arranged in an adjacent and at a distance in the second direction x2 are an eighth valve ring 9.8, an eighth valve recess 13.8 and an eighth interface 15.8. The eighth interface 15.8 can be used, inter alia, as an output for oil, so that oil can be discharged from the eighth valve recess 13.8. The eighth interface 15.8 of the first multiplex valve 6 is connected by means of a second orifice 46 to the unpressurized tank T.

[0038] Arranged in an adjacent and at a distance in the second direction x2 are a ninth valve ring 9.9, a ninth valve recess 13.9 and a ninth interface 15.9. The ninth interface 15.9 can be used as an input for oil, so that the ninth valve recess 13.9 can be filled with oil. In addition, the ninth interface 15.9 can also be used as an output for oil, so that oil can be discharged from the ninth valve recess 13.9.

[0039] Arranged in an adjacent and at a distance in the second direction x2 are a tenth valve ring 9.10, a tenth valve recess 13.10 and a tenth interface 15.10. The tenth interface 15.10 can be used as an input for oil, so that the tenth valve recess 13.10 can be filled with oil.

[0040] Finally, arranged in an adjacent and at a distance in the second direction x2 in the region of the second end side S2 of the first multiplex valve 6 are an eleventh valve ring 9.11, an eleventh valve recess 13.11 and an eleventh interface 15.11. The eleventh interface 15.11 can be used as an input for oil, so that the eleventh valve recess 13.11 can be filled with oil.

[0041] The valve slide 11 has a piston rod 16. On the piston rod 16, a plurality of pistons 17, 18, 19 and 20 are arranged. Each piston 17, 18, 19 and 20 is here, inter alia, firmly connected with the piston rod 16. The pistons 17, 18, 19 and 20 extend further outwards 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 chosen such that these pistons can move back and forth in the longitudinal direction L, more precisely, inter alia., (largely) in a sealed and frictionless manner, within the longitudinal bore 14 of the valve housing 10. The valve recesses 13.1 to 13.11, in turn, extend further outwards in the radial direction r of the valve slide 11 than the pistons 17, 18, 19 and 20.

[0042] 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 a certain axial spacing from the first piston 17 in the second direction x2. Further, the third piston 19 is arranged adjacent to the second piston 18 and at a certain axial spacing from the second piston 18 in the second direction x2. Finally, the fourth piston 20 is arranged in the region of the second end side S2 adjacent to the third piston 19.

[0043] The first piston 17 is designed pot-like and forms an inner space 21 and an inner pressure face 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 on the inner pressure face 22 of the first piston 17 in the second direction x2. The first valve recess 13.1 is connected with the inner space 21 of the first piston 17 by means of the longitudinal bore 14.

[0044] The first piston 17 seals the first valve recess 13.1 with respect to the second valve recess 13.2 independently of the position of the valve slide 11 with respect to the valve body 10, i.e. in particular in the first switching position and in the second switching position as described below, so that there is no connection between the first valve recess 13.1 and the second valve recess 13.2. Thereby, the first interface 15.1 is also not connected with the second interface 15.2. The feature "connection" is to be understood, inter alia., as meaning that the elements connected with one another accordingly are connected with one another in a hydraulically conductive manner, i.e. oil can flow from one element to the other and vice versa, if appropriate. In contrast, the features "disconnection" or "non-connection" are to be understood, inter alia., as meaning that the elements disconnected from one another accordingly are not connected with one another in a hydraulically conductive manner, i.e. no oil can flow from one element to the other and vice versa, if appropriate.

[0045] In the region of the valve slide 11 by Figure 2In the first switching position, the valve slide 11 is located in the first switching position in a manner pre-tensioned by the spring element 12, in which first switching position the fourth piston 20 is located in the eleventh valve recess 13.11.

[0046] 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 against the fifth valve recess 13.5, such that the fourth valve recess 13.4 is not connected to the fifth valve recess 13.5. Thereby, the fourth interface 15.4 is also not connected to the fifth interface 15.5.

[0047] 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 against the eighth valve recess 13.8, such that the seventh valve recess 13.7 is not connected to the eighth valve recess 13.8. Thereby, the seventh interface 15.7 is also not connected to the eighth interface 15.8.

[0048] 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 to the ninth interface 15.9. The fourth piston 20 also seals the tenth valve recess 13.10 against 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 switching position and in the second switching position, such that there is no connection between the tenth valve recess 13.10 and the eleventh valve recess 13.11. Thereby, the tenth interface 15.10 is also not connected to the eleventh interface 15.11.

[0049] The valve slide 11 can be moved in the first direction xi against the pre-tension of the spring element 12, such that the valve slide 11 moves out of the first switching position according to Figure 2 and occupies the second switching position. To this end, a pilot pressure pmV, which can be provided in particular by a magnetic valve, can be applied at the eleventh interface 15.11. The pilot pressure pmV applies a displacement force acting against the pre-tension to the hydraulically effective end face 23 of the valve slide 11.

[0050] 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.

[0051] 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. Thereby, the eighth interface 15.8 is 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.

[0052] The first multiplex valve 6 is connected to a shift element in the form of a double-acting claw clutch 24, which comprises a first claw K1 and a second claw K2. The double-acting claw clutch 24 can comprise, for example, a double-acting hydraulic cylinder with two opposite piston faces, to which oil is applied, in order to actuate it. The double-acting claw clutch 24 has a first interface 25 and a second interface 26. The first interface 25 of the double-acting claw clutch 24 is connected to the fifth interface 15.5 and the tenth interface 15.10 of the multiplex valve 6. The second interface 26 of the double-acting claw clutch 24 is connected to the second interface 15.2 and the seventh interface 15.7 of the multiplex valve 6.

[0053] The first damper valve 7 has a first interface 27, a second interface 28, a third interface 29, a valve housing 30, a first piston 31 and a return element in the form of a spring element 32. The first interface 27 of the first damper valve 7 is connected to the third interface 15.3 of the first multiplex valve 6. The second interface 27 of the first damper valve 7 is connected to a first orifice 36, which leads to an unpressurized oil tank T. The first piston 31 is designed pot-shaped and forms an inner space 33 and an inner pressure face 34, which extends in the radial direction r of the first damper valve 7. The spring element 32 generates a pretension force acting on the pressure face 34 of the piston 31, so that the piston 31 is pretensioned to the left in the drawing by the spring element 32. The first orifice 36 is connected to the second interface 28 of the first damper valve 7. The third interface 29 of the first damper valve 7 is connected to a second orifice 37, which leads to the unpressurized oil tank T. Figure 2The first damping valve 7 has a first interface 27, a second interface 28, a third interface 29, a valve housing 30, a first piston 31, and a return element in the form of a spring element 32. The first interface 27 of the first damping valve 7 is connected to the first interface 17.1 of the first multi-way valve 6. The second interface 28 of the first damping valve 7 is connected to the first orifice 36, which leads to the unpressurized oil tank T. The piston 31 is designed pot-shaped and forms an inner space 33 and an inner pressure face 34, which extends in the radial direction r of the first damping valve 7. The spring element 32 exerts a pretension on the pressure face 34 of the piston 31, so that the piston 31 is pretensioned in the initial position (see the position shown by Figure 2 The diameter of the first piston 31 is chosen such that the piston 31 can be moved back and forth in the axial bore 35 of the valve housing 30 in the longitudinal direction L, more precisely, in particular (largely) in a sealed and frictionless manner. The inner space 33 of the first piston 31 is connected to the third interface 29 by means of the axial bore 35, which in turn is connected to the unpressurized oil tank T, so that the inner space 33 and the axial bore 35 are vented on the side of the inner space 33.

[0054] The second damping valve 8 can be embodied identically to the first damping valve 7. The second damping valve 8 has a first interface 37, a second interface 38, a third interface 39, a valve housing 40, a second piston 41, and a return element in the form of a spring element 42. The first interface 37 of the second damping valve 8 is connected to the ninth interface 15.9 of the first multi-way valve 6. The second interface 37 of the second damping valve 8 (like the second interface 27 of the first damping valve 7) is connected to the first orifice 36, which leads to the unpressurized oil tank T. The piston 41 is designed pot-shaped and forms an inner space 43 and an inner pressure face 44, which extends in the radial direction r of the second damping valve 8. The spring element 42 exerts a pretension on the pressure face 44 of the piston 41, so that the piston 41 is pretensioned in the initial position (see the position shown by Figure 3 and the position shown by Figure 2 The diameter of the first piston 31 is chosen such that the piston 31 can be moved back and forth in the axial bore 35 of the valve housing 30 in the longitudinal direction L, more precisely, in particular (largely) in a sealed and frictionless manner. The inner space 33 of the first piston 31 is connected to the third interface 29 by means of the axial bore 35, which in turn is connected to the unpressurized oil tank T, so that the inner space 33 and the axial bore 35 are vented on the side of the inner space 33. Figure 2 The second damping valve 8 has a first interface 37, a second interface 38, a third interface 39, a valve housing 40, a second piston 41, and a return element in the form of a spring element 42. The first interface 37 of the second damping valve 8 is connected to the ninth interface 15.9 of the first multi-way valve 6. The second interface 37 of the second damping valve 8 (like the second interface 27 of the first damping valve 7) is connected to the first orifice 36, which leads to the unpressurized oil tank T. The piston 41 is designed pot-shaped and forms an inner space 43 and an inner pressure face 44, which extends in the radial direction r of the second damping valve 8. The spring element 42 exerts a pretension on the pressure face 44 of the piston 41, so that the piston 41 is pretensioned in the initial position (see the position shown by

[0055] If the valve spool 11 of the first multi-way valve 6 is in the position shown by Figure 2In the shown first switching position, oil under system pressure pSys flows through the sixth valve pocket 13.6, the longitudinal bore 14 and the seventh valve pocket 13.7 of the first multi-way valve 6. Since the seventh interface 15.7 of the first multi-way valve 6 is connected with the second interface 26 of the dog clutch 24, oil under system pressure is supplied to the dog clutch 24, which actuates the second dog K2. By actuating or pushing the second dog K2, a corresponding amount of oil is pushed out on the other side by the first interface 25 of the dog clutch 24. This pushed-out oil is guided via the tenth valve pocket 13.10, the longitudinal bore 14 and the ninth valve pocket 13.9 of the first multi-way valve 6 to the first interface 37 of the second damping valve 8. 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 moves the piston 41 of the second damping valve 8 from the Figure 3 the shown initial position to Figure 2 and Figure 4 the shown end stop position, so that oil can overflow through the second interface 38 of the second damping valve 8. In Figure 4 an exemplary oil flow is shown by means of arrows 49.

[0056] The amount of oil pushed out from the first dog K1 is thus collected in the second damping valve 8, whereby the piston 41 of the second damping valve 8 is located in the end stop position from a certain volume and the first dog K1 can only be pushed out (slow adjustment) via the second interface 38 and the (smaller) first orifice 36. The displacement of the piston 41 against the pretension of the spring element 42 of the second damping valve 8 (fast adjustment) is thus less resistant than the push-out into the tank T via the second interface 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 located in the end stop position, the oil has to flow into the tank T through the first orifice 36 (change from fast to slow adjustment). The second damping valve's volume VHub is determined by the Figure 2 The shown displacement VHub can be determined by having the second dog 2 perform half a stroke and then change to a slow displacement. The intermediate position of the second dog K2 (and thus also of the first dog K1) can thus be found more easily. This mode of operation of the second damping valve is active when the second dog K2 is pressurized as described above, i.e. when the valve spool 11 of the first multi-way valve 6 is located in Figure 2 the shown first switching position.

[0057] If the valve spool 11 of the first multi-way valve 6 is located in Figure 2The shown first switching position is displaced into the second switching position described above, then no oil is supplied to the first port 37 of the second damping valve 8 by the first pawl Kl. Instead, the piston 41 of the second damping valve 8 presses the remaining oil via the ninth valve recess 13.9, the longitudinal bore 14 and the eighth valve recess 13.8 of the first multiway valve 6 and via the second orifice 46 by means of the spring force of the spring element 42 into the unpressurized oil tank T until the piston 41 is again in its initial position.

[0058] When the valve spool 11 of the first multiway valve 6 is in the second switching position, oil under system pressure pSys continues to flow through the sixth valve recess 13.6, the longitudinal bore 14 and the fifth valve recess 13.5 of the first multiway valve 6. Since the fifth port 15.5 of the first multiway 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, thereby actuating the first pawl Kl. By actuating or pushing the first pawl Kl, a corresponding amount of oil is pushed out on the other side by means of 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 multiway valve 6 to the first port 27 of the first damping valve 7. The oil builds up pressure in the axial bore 35 and thereby moves the piston 31 of the first damping valve 7 from the initial position into the Figure 2 The shown initial position is displaced into the end stop position (see piston 41 of the second damping valve 8 in Figure 2 The shown position).

[0059] The amount of oil pushed out from the second pawl 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 pawl K2 can only be pushed out (slow adjustment) by means of the (smaller) first orifice 36. The displacement of the piston 31 against the pretension of the spring element 32 thus forms a smaller resistance to oil by being pushed into the unpressurized oil tank T via the second port 28 and the first orifice 36. In other words, the first damping valve 7 collects the outflowing oil of the second pawl K2. Once the piston 31 of the first damping valve 7 is in the end stop position, oil must flow into the oil tank T via the second port 28 and the first orifice 36 (change from fast adjustment to slow adjustment). The displacement of the first damping valve 7 can be determined by having the first pawl Kl perform a half stroke and then switching to slow displacement. The intermediate position of the first pawl Kl (and thus also of the second pawl K2) can thus be found more easily.

[0060] If the valve spool 11 of the first multiway valve 6 is in the Figure 2In the first switching position shown, the first damper valve 7 is supplied with oil from the second jaw K2. The piston 31 of the first damper valve 7 is pressed by means of the spring force of the spring element 32 against the remaining oil via the third valve recess 13.3, the longitudinal bore 14 and the fourth valve recess 13.4 of the first multiway valve 6 and via the second orifice 46 into the unpressurized oil tank T until the piston 31 is again in its initial position shown. Figure 2 In the initial position shown.

[0061] Figure 5 In the first switching position shown, the first damper valve 7 is supplied with oil from the second jaw K2. The piston 31 of the first damper valve 7 is pressed by means of the spring force of the spring element 32 against the remaining oil via the third valve recess 13.3, the longitudinal bore 14 and the fourth valve recess 13.4 of the first multiway valve 6 and via the second orifice 46 into the unpressurized oil tank T until the piston 31 is again in its initial position shown. Figure 2 In the first switching position shown, the first damper valve 7 is supplied with oil from the second jaw K2. The piston 31 of the first damper valve 7 is pressed by means of the spring force of the spring element 32 against the remaining oil via the third valve recess 13.3, the longitudinal bore 14 and the fourth valve recess 13.4 of the first multiway valve 6 and via the second orifice 46 into the unpressurized oil tank T until the piston 31 is again in its initial position shown. Figure 5 In the first switching position shown, the first damper valve 7 is supplied with oil from the second jaw K2. The piston 31 of the first damper valve 7 is pressed by means of the spring force of the spring element 32 against the remaining oil via the third valve recess 13.3, the longitudinal bore 14 and the fourth valve recess 13.4 of the first multiway valve 6 and via the second orifice 46 into the unpressurized oil tank T until the piston 31 is again in its initial position shown. Figure 2 In the first switching position shown, the first damper valve 7 is supplied with oil from the second jaw K2. The piston 31 of the first damper valve 7 is pressed by means of the spring force of the spring element 32 against the remaining oil via the third valve recess 13.3, the longitudinal bore 14 and the fourth valve recess 13.4 of the first multiway valve 6 and via the second orifice 46 into the unpressurized oil tank T until the piston 31 is again in its initial position shown.

[0062] BRIEF DESCRIPTION OF THE DRAWINGS

[0063] K1 first jaw

[0064] K2 second jaw

[0065] K3 third jaw

[0066] K4 fourth jaw

[0067] L longitudinal axis of the first multiway valve

[0068] pMV pilot pressure

[0069] pSys system pressure

[0070] r radial direction of the valve spool

[0071] T unpressurized oil tank

[0072] VHub displacement of the second damper valve

[0073] x longitudinal direction of the piston of the first / second damping valve

[0074] x1 first axial direction

[0075] x2 second axial direction

[0076] 1 motor vehicle

[0077] 2 combustion engine

[0078] 3 automatic transmission

[0079] 4 hydraulic control device

[0080] 5 valve device

[0081] 6 first multi-way valve

[0082] 7 first damping valve

[0083] 8 second damping valve

[0084] 9.1 to 9.11 valve ring

[0085] 10 valve housing

[0086] 11 valve slide

[0087] 12 spring element

[0088] 13.1 to 13.11 valve recess

[0089] 14 longitudinal bore

[0090] 15.1 to 15.11 interface

[0091] 16 piston rod

[0092] 17 first piston

[0093] 18 second piston

[0094] 19 third piston

[0095] 20 fourth piston

[0096] 21 inner space of the first piston

[0097] 22 inner pressure face of the first piston

[0098] 23 hydraulically effective end face

[0099] 24 double-acting dog clutch

[0100] 25 first interface of the dog clutch

[0101] 26 second interface of the dog clutch

[0102] 27 first interface of the first damping valve

[0103] 28 second interface of the first damping valve

[0104] 29 third interface of the first damping valve

[0105] 30 valve housing of the first damping valve

[0106] 31 piston of the first damping valve

[0107] 32 spring element of the first damping valve

[0108] 33 inner space of the first damping valve

[0109] 34 pressure surface of the first damping valve

[0110] 35 axial bore of the valve housing of the first damping valve

[0111] 36 first orifice

[0112] 37 first interface of the second damping valve

[0113] 38 second interface of the second damping valve

[0114] 39 third interface of the second damping valve

[0115] 40 valve housing of the second damping valve

[0116] 41 piston of the second damping valve

[0117] 42 spring element of the second damping valve

[0118] 43 inner space of the second damping valve

[0119] 44 pressure surface of the second damping valve

[0120] 45 axial bore of the valve housing of the second damping valve

[0121] 46 second orifice

[0122] 47 second multi-way valve

[0123] 48 double-acting clutch

[0124] 49 oil flow through the second damping valve

Claims

1. A valve arrangement (5) for a hydraulic control device (4) of a transmission (3) of a motor vehicle (1), the valve arrangement (5) comprising: a first damping valve (7) having a piston preloaded by a preloading force; a second damping valve (8) having a piston preloaded by a preloading force; and a first multiplex valve (6), wherein the first multiplex valve (6) - in a first switching position supplies oil, which is pushed out upon actuation of a first shift element (24) of the transmission (3), to the second damping valve (8); and - in a second switching position supplies oil, which is pushed out upon actuation of the first shift element (24), to the first damping valve (7), wherein the first damping valve (7) is configured to: - when the first multiplex valve (6) is in the second switching position, apply oil contained by the first multiplex valve (6) to the piston of the first damping valve (7) such that the piston of the first damping valve (7) is displaced against the preloading force into a final stop position, wherein the piston of the first damping valve (7) releases an interface of the first damping valve (7) such that the oil can overflow via the interface of the first damping valve and flow out into a tank (T) by means of a first orifice (36); and - when the first multiplex valve (6) is in the first switching position, displace the piston of the first damping valve (7) into an initial position by means of the preloading force, wherein the second damping valve (8) is configured to: - when the first multiplex valve (6) is in the first switching position, apply oil contained by the first multiplex valve (6) to the piston of the second damping valve (8) such that the piston of the second damping valve (8) is displaced against the preloading force into a final stop position, wherein the piston of the second damping valve (8) releases an interface of the second damping valve (8) such that the oil can overflow via the interface of the second damping valve and flow out into the tank (T) by means of the first orifice (36); and - when the first multiplex valve (6) is in the second switching position, displace the piston of the second damping valve (8) into an initial position by means of the preloading force.

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

3. The valve arrangement (5) according to claim 1, wherein the first shift element (24) of the transmission (3) is a dog clutch.

4. The valve arrangement (5) according to claim 3, wherein the dog clutch is a double-acting dog clutch having a first dog (K1) and a second dog (K2), wherein the first multiplex valve (6) in the first switching position is configured to: and - receiving oil at system pressure (pSys) from the hydraulic control device (4) and supplying it to a second interface of the first shift element (24) for actuating the first shift element such that the second dog (K2) is displaced in a first direction; - receive oil, which is pushed out upon actuation of the second dog (K2) by the first dog (K1) of the dog clutch, from a first interface of the dog clutch and supply it to the second damping valve (8), wherein the first multiplex valve (6) in the second switching position is configured to: ​ - receives oil at the system pressure (pSys) from the hydraulic control device (4) and supplies it to a first interface of the first shift element (24) for actuating the first shift element such that a first dog (K1) of the dog clutch is displaced in a second direction extending opposite to the first direction; and - receives oil from a second interface of the dog clutch, which is pushed out by a second dog (K2) of the dog clutch when actuating the first dog (K1), and supplies 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 a volume of oil that has been pushed out by the double-acting dog clutch when one of the dogs (K1 / K2) performs a half stroke when the piston of the first damping valve (7) is in a terminal stop position; and / or wherein the second damping valve (8) is able to accommodate a volume of oil that has been pushed out by the double-acting dog clutch when one of the dogs (K1 / K2) performs a half stroke when the piston of the second damping valve (8) is in a terminal stop position.

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

7. The valve device (5) according to claim 1, comprising a second multi-way valve (47), wherein the second multi-way valve (47): - is arranged between the first multi-way valve (6) and the first shift element (24); - connects the first multi-way valve (6) with the first shift element (24) in a first switching position; and - connects the first multi-way 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 device (5) according to one of claims 1 to 7.

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.

Images