Torque transmission device for a motor vehicle, clutch or brake device for a motor vehicle, and electric drive axle for an electric motor vehicle

Abstract

comprising a torque transmission device (1) for a motor vehicle: - a friction device (2) for transmitting torques, - a piston device (3) for closing and opening the friction device (2), - wherein the piston assembly (3) comprises a first and a second piston part (4, 5), - wherein the friction device (2) in conjunction with the piston device (3) forms a pressure chamber (D) such that the piston device (3) is movable in the axial direction (A) due to a pressurized fluid in the pressure chamber (D), where - the torque transmission device (1) has an adjusting device (8) with which the piston device (3) can be extended in the axial direction (A) according to wear of the friction device (2), - characterized in that each piston part (4, 5), viewed in the axial direction (A), has a first and second axial end, - wherein the first axial ends of the two piston parts (4, 5) are in contact opposite each other and / or in contact with each other, - wherein the first axial ends have at least a first contact section (12, 13) of the first and / or second piston part (4, 5) with a guide geometry (10, 11), - wherein the second axial ends have a first distance (X) in the axial direction (A) from each other, and - wherein the two piston parts (4, 5) or their first contact sections (12, 13) are designed such that after a relative rotation of one piston part (4; 5) relative to the other piston part (5; 4) the second axial ends have a second distance (Y) to each other in the axial direction (A).

Description

[0001] The invention relates to a torque transmission device for a motor vehicle and a clutch or brake device for a motor vehicle.

[0002] It is known that multi-disc brakes, used, for example, as vehicle / wheel brakes, require more discs compared to clutch applications. This is due to the higher torques involved compared to clutch applications.

[0003] Due to the increased number of lamellae, the additional actuation distance required to close the torque transmission device also increases when wear occurs. This principle is applied in the design of torque transmission devices, ensuring that safety-relevant aspects, such as correct actuation time or consistent actuation distance, are met even under wear.

[0004] Furthermore, a friction clutch with a wear adjustment device is known, for example, from EP 3 271 600 B1. With the aid of such a wear adjustment device, the actuation time or actuation travel can be kept virtually constant over the service life of a clutch under wear conditions. The friction clutch presented in EP 3 271 600 B1 is a single-plate dry clutch or a dual clutch, which serves to interrupt the torque flow from a motor vehicle engine to at least one input shaft of a motor vehicle transmission.

[0005] Further reference is made to DE 10 2017 003 623 A1, DE 198 10 940 A1, WO 2008 / 067 955 A1 and DE 10 2016 012 865 A1 as further state of the art.

[0006] Against this background, the object of the invention is to provide a torque transmission device for a motor vehicle, a clutch or brake device for a motor vehicle, and an electric drive axle for an electric motor vehicle, which can be manufactured cost-effectively and with minimal material usage and / or which is equipped with compensation for wear occurring in order to minimize changes in the actuation path and / or the actuation time in the event of wear.

[0007] This problem is solved by the features of the independent patent claims. Further advantageous developments are the subject of the dependent claims.

[0008] A first aspect of the present invention comprises a torque transmission device for a motor vehicle. The torque transmission device can, for example, be designed as a wet-running torque transmission device. That is, the torque transmission device can be fluid-cooled or oil-cooled.

[0009] The torque transmission device has a friction device for transmitting torques and a piston device, such as a ring piston or a central release bearing, for closing and opening the friction device.

[0010] The piston assembly comprises a first and a second piston part, which can be coaxially aligned. The two piston parts can be movable relative to each other. The second piston part can seal against the friction device or its first lamellar carrier to form a pressure chamber between the piston assembly and the friction device. Furthermore, the second piston part can have a guide that engages in a guide of the friction device or in a guide of the first lamellar carrier. This allows the piston assembly to be arranged in a rotationally secure manner against the friction device or its first lamellar carrier.

[0011] Furthermore, the friction device in conjunction with the piston device forms a pressure chamber, so that the piston device can be moved in the axial direction due to a pressurized fluid in the pressure chamber.

[0012] Furthermore, the torque transmission device features an adjustment mechanism that allows the piston assembly to be extended axially in accordance with wear of the friction element. This ensures that the operating conditions for the torque transmission device remain nearly constant even in the event of wear. Consequently, it is possible to maintain the actuation time and / or stroke of the torque transmission device at a nearly constant rate throughout its service life, thus guaranteeing its reliability.

[0013] Furthermore, the adjusting device can be located between the first and second piston sections of the piston assembly. This allows the piston assembly to be adapted to wear, a change in actuation time, or a change in the actuation stroke of the friction device.

[0014] Furthermore, the adjusting device can include an energy storage device that applies a force to the first and second piston sections in the circumferential and / or tangential direction. This energy storage device can be designed as a spring, a compression spring, or a tension spring. The energy storage device allows the actuation stroke to be adjusted according to the wear occurring, for example, by rotating the two piston sections relative to each other in opposite directions.

[0015] Furthermore, the adjusting device can have a first guide geometry and a second guide geometry. The first and second guide geometries can be geometrically complementary. The first and / or second guide geometry can also be in the form of a ramp, a curve (such as a parabola), or steps. This allows the adjusting device to change its extent or length in the axial direction.

[0016] Furthermore, it is possible that the first piston part has at least one contact section which forms and / or has the first guide geometry.

[0017] The second piston part can have at least one contact section which forms and / or has the second guide geometry.

[0018] Furthermore, the first and second piston parts and / or at least the at least one contact section with their guide geometries can be touching or in contact with each other.

[0019] Furthermore, according to the invention, each piston part, viewed in the axial direction, has a first and a second axial end. The first axial ends of the two piston parts are in contact opposite each other and / or in contact with each other.

[0020] Furthermore, the first axial ends have at least one contact section of the first and / or second piston part with a guide geometry.

[0021] Furthermore, the second axial ends exhibit a first axial distance from each other. Additionally, the two piston parts or their contact sections are designed such that, after a relative rotation of one piston part relative to the other, the second axial ends exhibit a second axial distance from each other. This second distance can be greater than the first. Consequently, the two piston parts or their contact sections can be designed such that a relative rotation of one piston part relative to the other increases the axial distance between the second axial ends. In other words, a relative rotation of the piston parts can cause the piston assembly to lengthen axially.

[0022] Furthermore, the piston assembly can include a return spring, a first stop element on the friction device, and a pressure pot. The return spring can generate a greater force in the axial direction than an energy storage device of the adjusting mechanism. This prevents unwanted relative rotation in the circumferential and / or tangential direction between the first and second piston sections of the piston assembly.

[0023] The pressure pot can be arranged between the friction device and the first piston part of the piston device, so that a contact force from the piston device can be transferred to the friction device by means of the pressure pot.

[0024] The return spring can be clamped between the first stop part, which can be fixed to the friction device, and the pressure pot in order to return the piston device to a starting position after a pressure drop in the pressure chamber, in which the friction device can be open.

[0025] The pressure pot can be designed to move and / or carry a sensor plate of a wear detection system of the torque transmission device in an axial direction, whereby the wear detection system can be moved from the piston device around the wear of the friction device.

[0026] Furthermore, the pressure pot can be designed similarly to an annular disk with a recess in the axial direction to accommodate the first and second piston parts. The recess can have a base and side walls. Alternatively, the recess can be designed as a pocket for receiving the two piston parts. The pocket can be designed such that it can accommodate at least one piston part in the axial direction.

[0027] In addition, the pressure pot can have a first leg that is arranged further outwards in the radial direction than the receiver and / or with the help of which a leg of a wear detection device of the torque transmission device can be moved.

[0028] Furthermore, the pressure pot can have a second leg that is positioned further inwards in a radial direction than the receptacle.

[0029] The legs of the pressure pot can be oriented in the same direction or aligned in the same way. Similarly, the legs of the pressure pot and the base of the receptacle can be oriented in the same direction or aligned in the same way. This simplifies manufacturing, for example, in a deep-drawing process.

[0030] Furthermore, the torque transmission device can include a wear detection system to detect the wear of the friction device.

[0031] The wear detection system can be designed to allow the adjusting device to readjust the detected wear in the axial direction.

[0032] Furthermore, the wear detection system can have a first and a second adjusting ring, which can be coaxially aligned. The two adjusting rings can be movable relative to each other. The second adjusting ring can be formed by a first lamellar carrier of the friction device.

[0033] Furthermore, the wear detection system can include an energy storage device that applies a force to the first and second adjusting rings in the circumferential and / or tangential direction. This energy storage device can be designed as a spring, a compression spring, or a tension spring. The energy storage device can be used to detect wear on the friction mechanism and / or to adjust the piston mechanism.

[0034] Furthermore, the wear detection system can have a first guide geometry and a second guide geometry, whereby the first and second guide geometries can be geometrically complementary. The first and / or second guide geometry can also be in the form of a ramp, a curve (such as a parabola), or a step.

[0035] Furthermore, it is conceivable that the first adjusting ring has at least one contact section which forms and / or has the first guide geometry.

[0036] It may also be provided that the second adjusting ring has at least one contact section which forms and / or has the second guide geometry.

[0037] The first and second adjustment rings can touch or contact each other.

[0038] Furthermore, it is conceivable that each adjusting ring, viewed in the axial direction, has a first and a second axial end. The first axial ends of the two adjusting rings can be in contact opposite each other and / or in contact with each other.

[0039] Furthermore, the first axial ends can have at least one contact section of the first and / or second adjusting ring with a guide geometry.

[0040] It is also possible that the second axial ends have a first distance from each other in the axial direction.

[0041] Furthermore, it may be provided that the two adjusting rings or their contact sections are designed such that, after a relative rotation of one adjusting ring with respect to the other adjusting ring, the second axial ends have a second distance to each other in the axial direction.

[0042] The second distance can be greater than the first. Consequently, the two adjusting rings or their contact sections can be designed such that a relative rotation of one adjusting ring relative to the other increases the distance between the second axial ends in the axial direction. In other words, a relative rotation of the adjusting rings can cause the wear detection area to lengthen in the axial direction. This lengthening can correspond to the detected wear.

[0043] In addition, the wear detection system can include a preload spring, a second stop part on the friction device, and a sensor plate.

[0044] The preload spring can be clamped between the second stop element, which may be fixed to the friction device, and the sensor plate. The preload spring can also generate a greater axial force than the energy storage device of the wear sensor, thus preventing unwanted relative rotation in the circumferential and / or tangential direction between a first and a second adjusting ring of the wear sensor.

[0045] The sensor plate can be L-shaped in half-section. Furthermore, the sensor plate can have a leg against which a first leg of a pressure pot of the piston assembly can be abutted.

[0046] As a result, the adjusting device of the piston assembly or its piston parts can offer the possibility of readjusting itself to compensate for the detected wear.

[0047] The following is an example of how the torque transmission device works.

[0048] As mentioned previously, the preload spring of the wear sensor can generate a greater force in the axial direction than the energy storage device of the wear sensor. This prevents relative rotation in the circumferential and / or tangential direction between a first and a second adjusting ring.

[0049] Furthermore, the return spring of the adjusting device can generate a greater force in the axial direction than the energy storage of the adjusting device, so that a relative rotation in the circumferential direction and / or in the tangential direction between the first and second piston parts can be prevented.

[0050] In the open state of the friction device or torque transmission device, in which no torque can be transmitted, the first leg of the pressure pot and the leg of the wear sensor can be spaced apart axially and not touch. In the case of a new torque transmission device, both legs also do not touch in the closed state of the torque transmission device or friction device, in which torque can be transmitted.

[0051] As wear of the friction device begins, the piston device or its pressure pot moves further in the axial direction to achieve the same effect as with a new torque transmission device.

[0052] In this case, and when closing the torque transmission device or in its closed state, the first leg of the pressure pot and the leg of the wear detection can touch in the axial direction.

[0053] If, in the closed state, the wear of the friction device and the travel of the piston assembly for closing the torque transmission device exceed the axial distance between the first leg of the pressure pot and the leg of the wear sensor, then, when the torque transmission device closes, the first leg of the pressure pot moves the leg of the wear sensor axially with it. Consequently, the sensor plate can be displaced or shifted axially by the wear of the friction device.

[0054] This prevents the preload spring of the wear sensor from acting on the energy storage device of the wear sensor, thus allowing a relative rotation in the circumferential and / or tangential direction between a first and a second adjusting ring of the wear sensor. The relative rotation, caused by the energy storage device, between the first and second adjusting rings can continue until the first adjusting ring again makes contact with or strikes the sensor plate and / or the axial force of the preload spring of the wear sensor exceeds the axial force of the energy storage device of the wear sensor.

[0055] Because the wear sensor can extend axially using the guide geometries, the position of the first adjusting ring, and thus of the stop it forms for the pressure pot or its first leg, can also change axially. Consequently, when the torque transmission device is open, the pressure pot can be retracted less in the opposite direction due to the wear of the friction element.

[0056] Consequently, the return spring can generate a lower axial force than the energy storage device of the adjusting mechanism. Thus, a relative rotation, generated by the adjusting mechanism, in the circumferential and / or tangential direction between the first and second piston sections of the piston assembly can be enabled by the energy storage device and the guide geometries. This relative rotation, caused by the energy storage device, between the first and second piston sections can continue until the first piston section again contacts or strikes the pressure pot and the axial force of the return spring exceeds the axial force of the energy storage device.

[0057] Furthermore, the friction device may comprise a first lamellar carrier and first lamellae, which can be arranged on the lamellar carrier in a rotationally fixed but axially displaceable manner. The first lamellar carrier may be a housing or be designed as such. The first lamellae may be made of steel.

[0058] Furthermore, the friction device can comprise a second lamellar carrier and second lamellars, which can be arranged on the lamellar carrier in a rotationally fixed but axially displaceable manner. The second lamellars can be designed as friction lamellae. The second lamellar carrier can also have a hub for a shaft. The hub can have a profile for frictional and / or positive locking.

[0059] Furthermore, it is possible that the first and second lamellar carriers are arranged coaxially.

[0060] The first and second lamellae can also be arranged alternately in the axial direction.

[0061] The piston device can be designed to decrease and increase the distance between the first and second lamellae in the axial direction.

[0062] Furthermore, the friction device may include a pressure plate for generating counter-pressure for the piston assembly and / or an adjusting disc for setting an axial tolerance of the friction device. The pressure plate and / or the adjusting disc may be attached to the friction device or to its first lamellar carrier and / or fixed in the axial direction.

[0063] A second aspect of the present invention comprises a clutch or brake device for a motor vehicle.

[0064] It is expressly pointed out that the features of the torque transmission device, as mentioned under the first aspect, can be used individually or in combination in the clutch or brake device.

[0065] In other words, the features relating to the torque transmission device mentioned above under the first aspect of the invention can also be combined with further features under the second aspect of the invention.

[0066] A clutch or brake device for a motor vehicle has a torque transmission device according to the first aspect, as well as a shaft which may be arranged on the friction device or its second lamellar carrier.

[0067] A third aspect of the present invention comprises an electric drive axle for an electric motor vehicle.

[0068] It is expressly pointed out that the features of the torque transmission device, as mentioned under the first aspect, can be used individually or in combination with each other in the electric drive axle.

[0069] The features of the clutch or brake device for a motor vehicle, as mentioned under the second aspect, can also be applied individually or in combination to the electric drive axle.

[0070] An electric drive axle for an electric motor vehicle has an electric drive, such as an electric motor or an electric machine, and a torque transmission device according to the first aspect.

[0071] Alternatively, an electric drive axle for an electric motor vehicle includes an electric drive, such as an electric motor or electric machine, and a clutch or brake device for a motor vehicle according to the second aspect.

[0072] The invention is explained in more detail below using an exemplary embodiment and the accompanying drawings. These schematically show: Fig. 1 a sectional view of a torque transmission device; Fig. 2 a spatial view of an adjusting device of the torque transmission device in a first state; Fig. 3 a partially shown side view on Fig. 2; Fig. 4 a spatial view of an adjusting device of the torque transmission device in a second state; Fig. 5 a partially shown side view on Fig. 4; Fig. 6 a partially shown side view of a wear detection system of the torque transmission device in a first state; Fig. 7 a partially shown side view of a wear detection of the torque transmission device in a second state; Fig. 8 a force-displacement diagram of a prior art torque transmission device; and Fig. 9 a force-displacement diagram of the torque transmission device Fig. 1.

[0073] In the following description, the same reference symbols are used for the same objects.

[0074] Fig. Figure 1 shows a sectional view of a torque transmission device 1 for a motor vehicle.

[0075] A more detailed illustration shows Fig. 1 a torque transmission device 1 which has a friction device 2 for transmitting torques.

[0076] Furthermore, the torque transmission device 1 has a piston assembly 3, such as a ring piston, for closing and opening the friction device 2.

[0077] The piston assembly 2 has a first and a second piston part 4, 5, which are coaxially aligned. The second piston part 5 abuts the friction assembly 2, or rather its first lamellar carrier 32, in a sealing manner to form a pressure chamber D between the piston assembly 3 and the friction assembly 2.

[0078] As can further be seen, the second piston part 5 has a guide 6 which engages in a guide 7 of the friction device 2 or in a guide 6 of the first lamellar carrier 32. This ensures that the piston device 2 is arranged in a rotationally secure manner on the friction device 2 or on its first lamellar carrier 32.

[0079] As already indicated, the friction device 2 in conjunction with the piston device 3 forms a pressure chamber D, so that the piston device 3 can be moved in axial direction A due to a pressurized fluid in the pressure chamber D.

[0080] Furthermore, the torque transmission device 1 has an adjusting device 8 with which the piston device 3 can be extended in axial direction A according to wear of the friction device 2.

[0081] More precisely, the adjusting device 8 is formed between the first and second piston parts 4, 5 of the piston assembly 3. The adjusting device 8 includes an energy storage element 9 which exerts a force on the first piston part 4 and the second piston part 5 in the circumferential direction U and / or in the tangential direction T. The energy storage element 9 is designed as a spring, a compression spring, or a tension spring.

[0082] According to Fig. 1 The adjusting device 8 has a first guide geometry 10 and a second guide geometry 11, which are geometrically complementary.

[0083] The first and second guide geometries 10, 11 are designed in the form of a ramp. However, a design in the form of a curve, such as a parabola, or a step-like design is also conceivable.

[0084] Fig. 2 and Fig. Figure 3 shows the piston assembly 3 including the adjusting device 8. Specifically, it shows Fig. 2 a spatial view of the adjusting device 8 of the torque transmission device 1 in a first state, wherein Fig. 3 a partially shown side view on Fig. 2 shows.

[0085] The first piston part 4, which in comparison to Fig. Figure 1 is simplified to show several first contact sections 12 which form and / or have the first guide geometry 10.

[0086] According to the Fig. 2 and Fig. 3 The second piston part 5 has several first contact sections 13, which form and / or have the second guide geometry 11. The first and second piston parts 4, 5, or at least the first contact sections 12, 13, with their guide geometries 10, 11, are in contact with each other.

[0087] In other words, each piston part 4, 5, viewed in the axial direction A, has a first and a second axial end. The first axial ends of the two piston parts 4, 5 are in contact opposite each other. Furthermore, the first axial ends have the first contact sections 12, 13 of the first and second piston parts 4, 5, respectively, with a guide geometry 10, 11.

[0088] According to Fig. 3 the second axial ends maintain a first distance X in axial direction A to each other.

[0089] Fig. 4 and Fig. Figure 5 shows a spatial view of the adjusting device 8 of the torque transmission device 1 in a second state, as well as a partially shown side view. Fig. 4.

[0090] To avoid unnecessary repetition, reference is made to the explanations regarding the Fig. 2 and Fig. 3 referenced, which are applicable here by analogy. The differences to the Fig. 2 and Fig. 3 are explained below.

[0091] This shows Fig. 4 and Fig. 5 compared to the Fig. 2 and Fig. 3, that the two piston parts 4, 5 or their first contact sections 12, 13 are designed such that after a relative rotation of one piston part 5 relative to the other piston part 4 the second axial ends have a second distance Y in axial direction A to each other.

[0092] Here, the second distance Y is from Fig. 5 greater than the first distance X from Fig. 3. Consequently, the two piston parts 4, 5 or their first contact sections 12, 13 are designed such that a relative rotation of one piston part 5 relative to the other piston part 4 increases the distance between their second axial ends in axial direction A. In other words, a relative rotation of the piston parts 4, 5 causes the piston assembly 3 to lengthen in axial direction A.

[0093] Out of Fig. Figure 1 also shows that the piston assembly 3 has a return spring 14, a first stop part 15 on the friction device 2 and a pressure pot 16.

[0094] The return spring 14 generates a greater force in the axial direction A than the energy storage device 9 of the adjusting device 8, so that an unwanted relative rotation in the circumferential direction U and / or in the tangential direction T between the first and second piston part 4, 5 of the piston device 3 can be prevented.

[0095] Furthermore, it shows Fig. 1, that the return spring 14 is clamped between the first stop part 15, which is fixed to the friction device 2, and the pressure pot 16 in order to return the piston device 3 to a starting position in which the friction device 2 is open after a pressure drop in the pressure chamber D.

[0096] The pressure pot 16 is arranged between the friction device 2 and the first piston part 4 of the piston device 3, so that a contact force of the piston device 3 can be transferred to the friction device 2 by means of the pressure pot 16.

[0097] Furthermore, the pressure pot 16 is designed to move and / or carry a sensor plate 30 of a wear detection device 20 of the torque transmission device 1 in axial direction A, whereby the wear detection device 20 can be moved by the piston device 3 around the wear of the friction device 2.

[0098] According to Fig. The pressure pot 16 is designed similarly to an annular disk with a receptacle 17 in the axial direction A to receive the first and second piston parts 4, 5 in the receptacle 17. As can be seen, the receptacle 17 has a bottom and side walls.

[0099] Furthermore, the pressure pot 16 has a first leg 18, which is arranged further outwards in the radial direction R than the receptacle 17 and with the help of which a leg 31 of a wear detection 20 of the torque transmission device 1 can be moved.

[0100] The pressure pot 16 also has a second leg 19, which is arranged further inwards in the radial direction R than the receptacle 17.

[0101] Accordingly Fig. 1. Legs 18 and 19 are oriented in the same direction or aligned in the same way. Furthermore, legs 18 and 19 and the base of the recording 17 are oriented in the same direction or aligned in the same way.

[0102] As already indicated, the torque transmission device 1 has a wear detection device 20 for detecting the wear of the friction device 2.

[0103] The wear detection device 20 is designed to allow the adjusting device 8 to adjust the detected wear in axial direction A.

[0104] Furthermore, it shows Fig. 1, that the wear detection device 20 has a first and a second adjusting ring 21, 22 which are coaxially aligned. The second adjusting ring 22 is formed by the first lamellar carrier 32 of the friction device 2.

[0105] Furthermore, the wear detection device 20 has an energy storage element 23 which applies a force to the first adjusting ring 21 and the second adjusting ring 22 in the circumferential direction U and / or in the tangential direction T. The energy storage element 23 is designed as a spring, a compression spring, or a tension spring.

[0106] Fig. Figure 6 shows a partially depicted side view of the wear detection device 20 in a first state, whereas Fig. Figure 7 shows a partially depicted side view of the wear detection system 20 in a second state.

[0107] This is based on the Fig. 6 and Fig. Figure 7 shows that the wear detection device 20 has a third guide geometry 24 and a fourth guide geometry 25, which are geometrically complementary. The third and fourth guide geometries 24 and 25 are designed in the form of a ramp. However, it is also possible that they are designed in the form of a curve, such as a parabola, or as steps.

[0108] Furthermore, they show Fig. 6 and Fig. 7, that the first adjusting ring 21 has several second contact sections 26 which form and / or have the third guide geometry 24. The second adjusting ring 22 also has several second contact sections 27 which form and / or have the fourth guide geometry 25.

[0109] In this case, the first and second adjusting rings 21, 22 are touching or in contact with each other.

[0110] Furthermore, each adjusting ring 21, 22, viewed in axial direction A, has a first and second axial end, wherein the first axial ends of the two adjusting rings 21, 22 are in contact opposite each other and / or are in contact with each other.

[0111] The first axial ends also feature the second contact sections 26, 27 of the first and second adjusting rings 21, 22 with a guide geometry 24, 25.

[0112] According to Fig. 6 the second axial ends maintain a first distance X in axial direction A to each other.

[0113] According to Fig. 7 the two adjusting rings 21, 22 or their second contact sections 26, 27 are designed such that after a relative rotation of one adjusting ring 22 relative to the other adjusting ring 21 the second axial ends have a second distance Y in axial direction A to each other.

[0114] Here, the second distance Y is from Fig. 7 greater than the first distance X from Fig. 6. Consequently, the two adjusting rings 21, 22, or their second contact sections 26, 27, are designed such that a relative rotation of one adjusting ring 22 relative to the other adjusting ring 21 increases the distance between their second axial ends in the axial direction A. In other words, a relative rotation of the adjusting rings 21, 22 causes the wear detection element 20 to lengthen in the axial direction A.

[0115] Furthermore, it is assumed that Fig. 1 shows that the wear detection 20 comprises a preload spring 28, a second stop part 29 on the friction device 2 and a sensor plate 30.

[0116] The preload spring 28 is clamped between the second stop part 29, which is fixed to the friction device 2, and the sensor plate 30.

[0117] The preload spring 28 generates a greater force in the axial direction A than the energy storage device 23 of the wear detection device 20, so that an unwanted relative rotation in the circumferential direction U and / or in the tangential direction T between a first and a second adjusting ring 21, 22 of the wear detection device 20 can be prevented.

[0118] According to Fig. 1 The sensor plate 30 is L-shaped in half-section and has a leg 31 against which the first leg 18 of the pressure pot 16 can abut.

[0119] As a result, the adjusting device 8 of the piston device 3 or its piston parts 4, 5 opens up the possibility of readjusting itself to compensate for the detected wear.

[0120] As already mentioned, the preload spring 28 of the wear detection 20 generates a greater force in the axial direction A than the energy storage 23 of the wear detection 20, which prevents a relative rotation in the circumferential direction U and / or in the tangential direction T between a first and a second adjusting ring 21, 22.

[0121] Furthermore, the return spring 14 of the adjusting device 8 generates a greater force in the axial direction A than the energy storage device 9 of the adjusting device 8, so that a relative rotation in the circumferential direction U and / or in the tangential direction T between the first and second piston part 4, 5 can be prevented.

[0122] When open - see below. Fig. 1 - The first leg 18 of the pressure pot 16 and the leg 31 of the wear detector 20 are spaced apart in axial direction A and do not touch. In the case of a new torque transmission device 1, both legs 18, 31 do not touch even when the torque transmission device 1 is closed.

[0123] Only when wear of the friction device 2 begins must the piston device 3 or its pressure pot 16 be moved further in axial direction A by the wear of the friction device 2 in order to achieve the same braking effect as is achieved with a new torque transmission device 1.

[0124] In this case, and when closing the torque transmission device 1 or in its closed state, the first leg 18 of the pressure pot 16 and the leg 31 of the wear detection device 20 can touch in axial direction A.

[0125] If, in the closed state, the wear of the friction device 2 and the travel distance of the piston device 3 for completely closing the torque transmission device 1 exceed the value specified in Fig. Given the axial distance A shown in Figure 1 between the first leg 18 of the pressure pot 16 and the leg 31 of the wear detector 20, when the pressure pot closes, the first leg 18 of the pressure pot moves the leg 31 of the wear detector 20 with it in axial direction A. Consequently, the sensor plate 30 moves to the left by the wear of the friction device 2, or in axial direction A by the wear of the friction device 2.

[0126] As a result, the preload spring 28 of the wear sensor 20 no longer acts on the energy storage device 23 of the wear sensor 20, thus enabling a relative rotation in the circumferential direction U and / or in the tangential direction T between the first and second adjusting rings 21, 22. The relative rotation, caused by the energy storage device 23, between the first and second adjusting rings 21, 22 continues until the first adjusting ring 21 again contacts or abuts the sensor plate 31 and the axial force of the preload spring 28 exceeds the axial force of the energy storage device 23.

[0127] Because the wear sensor 20 has lengthened in axial direction A by means of the guide geometries 24, 25, the position of the first adjusting ring 21 and thus of the stop formed by it for the pressure pot 16 or its first leg 18 also changes in axial direction A. Consequently, in the open state of the torque transmission device 1, the pressure pot 16 is located in a different position compared to Fig. 1 to reduce the wear of the friction device 3 less in the opposite direction A.

[0128] Consequently, the return spring 14 generates a lower force in the axial direction A than the energy storage device 9 of the adjusting device 8. Thus, a relative rotation, generated by the adjusting device 8, in the circumferential direction U and / or in the tangential direction T between the first and second piston sections 4, 5 of the piston assembly 3 is possible with the aid of the energy storage device 9 and the guide geometries 10, 11. The relative rotation, caused by the energy storage device 9, between the first and second piston sections 4, 5 continues until the first piston section 4 again contacts or strikes the pressure pot 16 and the axial force of the return spring 14 exceeds the axial force of the energy storage device 9.

[0129] Furthermore, it is assumed that Fig. Figure 1 shows that the friction device 2 comprises a first lamellar carrier 32 and first lamellars 33, which are arranged on the lamellar carrier 32 in a rotationally fixed but axially displaceable manner. The first lamellar carrier 32 has a housing or is designed as a housing, wherein the first lamellars 33 are designed as steel lamellars.

[0130] Furthermore, the friction device 2 has a second lamellar carrier 34 and second lamellars 35, which are arranged on the lamellar carrier 34 in a rotationally fixed but axially displaceable manner and which are designed as friction lamellars.

[0131] In addition, the second lamellar carrier 34 has a hub 36 for a shaft which has a profile for friction and / or form-fit connection.

[0132] It also goes out Fig. Figure 1 shows that the first and second lamella carriers 32, 34 are arranged coaxially, with the first and second lamellae 33, 35 arranged alternately in the axial direction A. As already mentioned, the piston device 3 is designed to decrease and increase the distance between the first and second lamellae 33, 35 in the axial direction A.

[0133] Furthermore, it shows Fig. 1, that the friction device 5 comprises a pressure plate 37 for generating counter-pressure for the piston device 3 and an adjusting disc 38 for setting an axial tolerance of the friction device 2. The pressure plate 37 and the adjusting disc 38 are attached to the friction device 5 or to its first lamellar carrier 32 and are fixed in axial direction A.

[0134] Furthermore, it should be noted that the presented torque transmission device 1 can be part of a braking device for a motor vehicle, in which case a shaft (not shown) may be present which is arranged on the friction device 2 or its second lamellar carrier 35.

[0135] Fig. Figure 8 shows a force-displacement diagram of a prior art torque transmission device and Fig. 9 a force-displacement diagram of the torque transmission device 1 from Fig. 1.

[0136] This is in Fig. Figure 8 shows a characteristic curve of a torque transmission device in the new condition (P1N; P2N) and in the worn condition (P1W; P2W).

[0137] The characteristic curve is divided into two sections. In the first section (up to P1N or P1W), the clearance is bridged, with a low increase in force. In the second section (from P1N to P2N or P1W to P2W), where the torque is built up, the force increases very sharply, while only a small actuation distance is covered. Due to wear, the first section from P1N to P1W is extended. This results in a longer actuation time and a greater actuation distance.

[0138] According to Fig. 9 The adjustment device 8 reduces the extension of the characteristic curve or the first part of the characteristic curve to a minimum when wear occurs.

[0139] Because the adjusting device 8, when the friction device 2 wears down – as illustrated – resets the beginning of the second range, or P1W, towards P1N. Thus, the actuation time or actuation stroke can be maintained at a similar level to that of the new torque transmission device 1, even when worn, thereby increasing the safety of the torque transmission device 1. Reference symbol list 1 Torque transmission device 2 friction device 3 Piston assembly 4 first piston part 5 second piston part 6 Leadership 7 Leadership 8 Adjustment device 9 Energy storage 10 First guide geometry 11 second guide geometry 12 first contact section 13 first contact section 14 Return spring 15 first stop part 16 Pressure pot 17th entry 18 first thigh 19 second thigh 20 Wear detection 21 first adjusting ring 22 second adjusting ring 23 Energy storage 24 third guide geometry 25 fourth guide geometry 26 second contact section 27 second contact section 28 Preload spring 29 second stop part 30 sensor plates 31 thighs 32 first lamellar carrier 33 first slats 34 second lamellar carrier 35 second slats 36 hub 37 Pressure plate 38 Adjustment disc D pressure chamber A axial direction R radial direction X first distance Y second distance

Claims

[1] comprising a torque transmission device (1) for a motor vehicle: - a friction device (2) for transmitting torques, - a piston device (3) for closing and opening the friction device (2), - wherein the piston assembly (3) comprises a first and a second piston part (4, 5), - wherein the friction device (2) in conjunction with the piston device (3) forms a pressure chamber (D) such that the piston device (3) is movable in the axial direction (A) due to a pressurized fluid in the pressure chamber (D), where - the torque transmission device (1) has an adjusting device (8) with which the piston device (3) can be extended in the axial direction (A) according to wear of the friction device (2), - characterized by , that each piston part (4, 5), viewed in the axial direction (A), has a first and second axial end, - wherein the first axial ends of the two piston parts (4, 5) are in contact opposite each other and / or in contact with each other, - wherein the first axial ends have at least a first contact section (12, 13) of the first and / or second piston part (4, 5) with a guide geometry (10, 11), - wherein the second axial ends have a first distance (X) in the axial direction (A) from each other, and - wherein the two piston parts (4, 5) or their first contact sections (12, 13) are designed such that after a relative rotation of one piston part (4; 5) relative to the other piston part (5; 4) the second axial ends have a second distance (Y) in axial direction (A) to each other. [2] Torque transmission device (1) according to claim 1, - wherein the adjusting device (8) is formed between the first and second piston parts (4, 5) of the piston assembly (3), and / or - wherein the adjusting device (8) has an energy storage device (9) which applies a force to the first piston part (4) and the second piston part (5) in the circumferential direction (U) and / or in the tangential direction (T). [3] Torque transmission device (1) according to claim 1 or 2, - wherein the adjusting device (8) has a first guide geometry (10) and a second guide geometry (11), - wherein the first and second guide geometries (10, 11) are geometrically complementary, and - wherein the first and / or second guide geometry (10, 11) is designed in the form of a ramp or in the form of a curve or in a step-like manner. [4] Torque transmission device (1) according to any one of the preceding claims, - wherein the piston assembly (3) comprises a return spring (14), a first stop part (15) on the friction device (2) and a pressure pot (16), - wherein the return spring (14) is clamped between the first stop part (15) and the pressure pot (16) in order to return the piston assembly (3) to a starting position after a pressure drop in the pressure chamber (D), and / or - wherein the torque transmission device (1) further comprises a wear detection device (20) for detecting the wear of the friction device (2), and - wherein the wear detection (20) is designed to enable the adjusting device (8) to adjust the detected wear in the axial direction (A). [5] Torque transmission device (1) according to claim 4, - wherein the wear detection (20) has a first and a second adjusting ring (21, 22), and - wherein the wear detection (20) has an energy storage device (23) which applies a force to the first adjusting ring (21) and the second adjusting ring (22) in the circumferential direction (U) and / or in the tangential direction (T), and / or - wherein the wear detection (20) comprises a preload spring (28), a second stop part (29) on the friction device (2) and a sensor plate (30), - wherein the preload spring (28) is clamped between the second stop part (29) and the sensor plate (30). [6] Torque transmission device (1) according to claim 4 or 5, - wherein the wear detection (20) has a third guide geometry (24) and a fourth guide geometry (25), - wherein the third and fourth guide geometries (24, 25) are geometrically complementary, and - wherein the third and / or fourth guide geometry (24, 25) is designed in the form of a ramp or in the form of a curve or in a step-like manner. [7] Torque transmission device (1) according to one of the preceding claims in combination with claim 5, - wherein each adjusting ring (21, 22), viewed in the axial direction (A), has a first and second axial end, - wherein the first axial ends of the two adjusting rings (21, 22) are in contact opposite each other and / or in contact with each other, - wherein the first axial ends have at least a second contact section (26, 27) of the first and / or second adjusting ring (21, 22) with a guide geometry (24, 25), - wherein the second axial ends have a first distance (X) in the axial direction (A) from each other, and - wherein the two adjusting rings (21, 22) or their second contact sections (26, 27) are designed such that after a relative rotation of one adjusting ring (21; 22) relative to the other adjusting ring (22; 21) the second axial ends have a second distance (Y) in axial direction (A) to each other. [8] Having a clutch or brake device for a motor vehicle: - a torque transmission device (1) according to one of the preceding claims, and - a shaft which is arranged on the friction device (2). [9] Having an electric drive axle for an electric motor vehicle: - an electric drive, and - a torque transmission device (1) according to one of the preceding claims, or - a clutch or brake device for a motor vehicle according to the preceding claim.

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