Friction assembly with variable damping and torsional vibration damper

Abstract

The invention relates to a variable damping friction assembly and a torsional vibration damper. The friction assembly with the variable damping comprises a hub, the friction sleeve is arranged outside the hub in a torsion-resistant and sleeving manner, and an inclined plane is arranged on one axial side of the friction sleeve; the friction flange is located on one axial side of the friction sleeve, and the axial distance between the friction flange and the friction sleeve is fixed; the wave spring is axially located between the friction sleeve and the friction flange and connected with the friction flange in an anti-torsion mode, and a protrusion is arranged on the side, close to the friction sleeve, of the wave spring; when the hub drives the friction sleeve to rotate in the first direction relative to the friction flange, the inclined face abuts against the protrusion and axially extrudes the protrusion, and when the hub drives the friction sleeve to rotate in the second direction relative to the friction flange, the inclined face is separated from the protrusion.

Description

Technical Field

[0001] The invention relates to the technical field of vehicle shock absorption, and in particular to a friction component with variable damping and a torsional vibration damper. Background Art

[0002] Motor vehicles will continue to be powered by internal combustion engines for the foreseeable future. Regardless of the type of transmission used, the basic requirements for torque transmission between the engine and the transmission are the same, that is, torsional vibrations and rotational non-uniformity should be reduced while starting and transmitting average torque. Therefore, a vibration damping device is usually provided between the engine and the transmission to absorb and buffer the vibration of the torque output from the engine (forward torque transmission) or the vibration of the torque output from the motor in the transmission box (reverse torque transmission).

[0003] The torsional vibration damper in the related art is a double-flange design. However, when the reverse torque is transmitted, the corresponding flange often does not have sufficient damping, making it easier for the vibration generated by the motor to be transmitted to the torsional vibration damper, which has a greater impact on the engine and is not conducive to improving the noise, vibration and harshness (NVH) of the entire vehicle. Summary of the invention

[0004] In order to overcome the problems existing in the related art, the present invention provides a friction assembly with variable damping and a torsional vibration damper.

[0005] According to a first aspect of an embodiment of the present invention, the present invention provides a friction assembly with variable damping, comprising: a friction sleeve, wherein an inclined surface is provided on one axial side of the friction sleeve; a friction flange, which is located on one axial side of the friction sleeve and has a fixed axial spacing with the friction sleeve; and a wave spring, which is axially located between the friction sleeve and the friction flange and is torsionally connected to the friction flange, wherein a protrusion is provided on a side of the wave spring close to the friction sleeve; wherein when the friction sleeve rotates in a first direction relative to the friction flange, the inclined surface abuts against the protrusion and axially squeezes the protrusion; and when the friction sleeve rotates in a second direction relative to the friction flange, the inclined surface is separated from the protrusion.

[0006] In some embodiments, one axial side of the friction sleeve is provided with: a groove, including a first plane and the inclined surface; and a protrusion, including a second plane, and the second plane is transitionally connected to the first plane through the inclined surface, wherein the axial sides of the wave spring are respectively in contact with the second plane and the friction flange, and the protrusion of the wave spring is located in the groove and abuts against the first plane.

[0007] In some embodiments, the inner wall of the friction flange is provided with a plurality of tooth grooves along the circumferential direction; the friction assembly is provided with a latching tooth which is torsionally connected to the friction sleeve, wherein the latching tooth is located in the tooth groove, and the tooth width of the tooth groove is greater than the tooth width of the latching tooth, and when the latching tooth abuts against the tooth groove, the friction flange and the friction sleeve are driven to rotate together.

[0008] In some embodiments, a slot is provided on the radial outer side of the friction flange; a claw is provided on the radial outer side of the wave spring at a position corresponding to the slot, and the claw is engaged with the slot to fix the wave spring to the friction flange.

[0009] In some embodiments, the friction sleeve includes a plurality of inclined surfaces along the circumferential direction; and the wave spring includes a plurality of protrusions along the circumferential direction.

[0010] In some embodiments, the inclined surface is an inclined plane or an inclined curved surface.

[0011] In some embodiments, the friction sleeve is made of hard plastic, and the friction flange is made of metal material.

[0012] According to a second aspect of an embodiment of the present invention, the present invention provides a torsional vibration damper, comprising: a wheel hub; a first support plate, rotatably connected to one axial end of the wheel hub; a second support plate, torsionally connected to the first support plate and rotatably connected to the other axial end of the wheel hub; and a friction assembly with variable damping as described in the first aspect, wherein the friction assembly is sleeved on the outside of the wheel hub and axially abuts between the wheel hub and the first support plate.

[0013] In some embodiments, the friction sleeve is torsionally connected to the wheel hub; the friction flange is frictionally abutted against the first support plate, wherein when the friction sleeve rotates in a first direction relative to the friction flange, a changing friction force is generated between the friction flange and the first support plate, and when the friction sleeve rotates in a second direction relative to the friction flange, the friction force between the friction flange and the first support plate remains unchanged.

[0014] In some embodiments, a plurality of latch teeth are circumferentially arranged on the outer wall of the hub.

[0015] The technical solution provided by the embodiment of the present invention may include the following beneficial effects: the axial distance between the friction sleeve and the friction flange is fixed, the wave spring is fixedly connected to the friction flange, and the inclined surface located on the friction sleeve abuts against the protrusion of the wave spring, so that when the wheel hub drives the friction sleeve to rotate in the first direction, the friction force between the friction flange and the first support plate is increased. When the friction sleeve rotates in the second direction (opposite to the first direction), the inclined surface separates from the protrusion, and the friction force between the friction flange and the first support plate remains unchanged, thereby achieving the effect of increasing damping in one direction. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and, together with the description, serve to explain the principles of the invention.

[0017] Figure 1 is a partial cross-sectional view of a torsional vibration damper according to an exemplary embodiment;

[0018] Figure 2 yes Figure 1 Axonometric view of the middle hub and friction assembly combination;

[0019] Figure 3 yes Figure 1 A three-dimensional view of the middle wheel hub and the friction assembly;

[0020] Figure 4 yes Figure 1 A front view of the middle friction assembly as viewed from the transmission side;

[0021] Figure 5 It is a three-dimensional combination diagram of the wheel hub, friction sleeve and wave spring;

[0022] Figure 6 yes Figure 5 The side view shows that when the wheel hub is at 0°, the inclined surface of the friction sleeve just abuts against the protrusion of the wave spring;

[0023] Figure 7 yes Figure 5 The side view shows that when the wheel hub is at 0°→-3° (i.e., the first direction), the inclined surface of the friction sleeve interferes with the protrusion of the wave spring;

[0024] Figure 8 yes Figure 5 The side view shows that when the wheel hub rotates from 0°→+3° (i.e., the second direction), the inclined surface of the friction sleeve and the protrusion of the wave spring are in a separated position;

[0025] Fig. 9 It is a schematic diagram of the change in friction force when the torque is transmitted in the forward direction (right side of the coordinate graph) and the torque is transmitted in the reverse direction (left side of the coordinate graph). DETAILED DESCRIPTION

[0026] Exemplary embodiments will be described in detail herein, examples of which are shown in the accompanying drawings. When the following description refers to the drawings, the same numbers in different drawings represent the same or similar elements unless otherwise indicated. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present invention. Instead, they are merely examples of devices and methods consistent with some aspects of the present invention as detailed in the appended claims.

[0027] In the present invention, unless otherwise specified, the axial direction A, radial direction R and circumferential direction W refer to the axial direction A, radial direction R and circumferential direction W of the torsional vibration damper respectively; the radial outer side refers to the direction away from the radial direction R. Figure 1 The side of the central axis O in the Figure 1 The radial inner side refers to the side close to the central axis O in the radial direction R (e.g. Figure 1 ).

[0028] In addition, the term "transmission connection" refers to the ability to transmit driving force / torque between two components, and the two components can be directly connected or through various transmission mechanisms or connection structures to achieve the above functions. The term "torsion-resistant connection" refers to the connection between two elements in a manner that does not rotate relative to each other, which can be achieved through a press fit (i.e., an interference fit) or by forming the two components mentioned in one piece. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to the specific circumstances.

[0029] The present invention provides a variable damping friction assembly 100, which can be applied to a torque damping device. The torque damping device is a device arranged between an engine and a transmission, and is used to transmit torque between the engine and the transmission and reduce torsional vibration or torsional impact when transmitting torque.

[0030] The torque damping device may include a torque limiter and a torsional vibration damper (also referred to as a damper). The torque limiter may be used to transfer a torque not exceeding a predetermined torque between the engine and the transmission to avoid excessive torque being transferred between the engine and the transmission, thereby causing damage to the engine or the transmission. The torsional vibration damper may reduce torsional vibration or torsional shock when torque is transferred between the engine and the transmission. Therefore, the torque damping device has both a torque limiting function and a torque damping function through the torque limiter and the torsional vibration damper. In this embodiment, the torque limiter is located radially outside the torsional vibration damper.

[0031] The variable damping friction assembly 100 provided by the present invention is applied to a torsional vibration damper. Figure 1As shown, the torsional vibration damper may further include a first support plate 300 , a second support plate 400 , a first flange 500 , a second flange 600 , and a wheel hub 200 .

[0032] The first support plate 300 is rotatably connected to one axial end of the hub 200 (eg Figure 1 The second support plate 400 is rotatably connected to the other axial end of the hub 200 (such as Figure 1 The first support plate 300 and the second support plate 400 are torsionally connected, the first flange 500 (arranged near the second support plate 400) and the second flange 600 (arranged near the first support plate 300) are torsionally connected to the wheel hub 200 and are axially located between the first support plate 300 and the second support plate 400. The wheel hub 200 is used for torsionally connecting to the input shaft of the transmission.

[0033] When the engine transmits torque to the transmission in the forward direction, the first support plate 300 and the second support plate 400, after receiving the torque transmitted by the torque limiter, transmit the torque to the first flange 500 and the second flange 600 in sequence through the coil spring, and the first flange 500 and the second flange 600 then transmit the torque to the wheel hub 200 and the input shaft of the transmission.

[0034] When the transmission transmits torque to the engine in reverse, the input shaft of the transmission drives the wheel hub 200 to rotate, and the wheel hub 200 drives the second flange 600 and the first flange 500 to rotate in turn. The first flange 500 and the second flange 600 rotate the compression coil spring to drive the first support plate 300 and the second support plate 400 to rotate, and the first support plate 300 and the second support plate 400 then transmit the torque to the torque limiter.

[0035] like Figure 1 As shown, in this embodiment, the variable damping friction assembly 100 is axially abutted between the first support plate 300 and the wheel hub 200, and is used to increase the friction between the wheel hub 200 and the first support plate 300 when the torque is transmitted in the reverse direction, thereby increasing the damping of the wheel hub 200 when the torque is transmitted in the reverse direction, thereby reducing the vibration generated when the wheel hub 200 transmits torque to the second flange 600 and the first flange 500.

[0036] Specifically, Figure 2 As shown, the friction assembly 100 includes a friction sleeve 10, a wave spring 30 and a friction flange 20. Figure 3 As shown, the friction assembly 100 is sleeved on the outside of the wheel hub 200 , that is, the friction sleeve 10 , the wave spring 30 and the friction flange 20 are all sleeved on the outside of the wheel hub 200 .

[0037] The friction sleeve 10 is connected to the wheel hub 200 in a torsion-proof manner, and the axial end surface of the friction sleeve 10 away from the first support plate 300 abuts against the wheel hub 200, so that the axial position and circumferential position of the friction sleeve 10 on the wheel hub 200 are fixed. In some embodiments, the wheel hub 200 is made of a metal material for transmitting torque, and the friction sleeve 10 is made of hard plastic. The friction sleeve 10 made of hard plastic can provide friction and reduce the weight of the entire friction assembly 100.

[0038] In some other embodiments, the friction sleeve 10 and the wheel hub 200 may also be integrally formed, that is, the friction sleeve 10 and the wheel hub 200 are integrally formed of metal material. The integrally formed friction sleeve 10 and wheel hub 200 can increase the strength of the friction sleeve 10, facilitate processing, and reduce the number of parts and installation steps.

[0039] Furthermore, the friction flange 20 is coaxial with the friction sleeve 10 and is frictionally connected to the first support plate 300. Since the axial distance between the hub 200 and the first support plate 300 is fixed, the axial distance between the friction sleeve 10 and the friction flange 20 is fixed.

[0040] The friction connection between the friction flange 20 and the first support plate 300 means that there is friction between the friction flange 20 and the first support plate 300. When the wheel hub 200 rotates within a preset angle, the friction force can prevent the friction flange 20 from rotating in the circumferential direction relative to the first support plate 300, and the wheel hub 200 can drive the friction sleeve 10 to rotate relative to the friction flange 20. When the wheel hub 200 rotates beyond the preset angle range, the wheel hub 200 abuts against the friction flange 20, and the wheel hub 200 drives the friction flange 20 to rotate and overcome the friction between the friction flange 20 and the first support plate 300, so that the wheel hub 200 can drive the friction sleeve 10 and the friction flange 20 to rotate relative to the first support plate 300.

[0041] Furthermore, the wave spring 30 is axially located between the friction sleeve 10 and the friction flange 20 , and the wave spring 30 is torsionally connected to the friction flange 20 .

[0042] In some embodiments, Figure 2 and Figure 4 As shown, a claw 33 is provided on the radial outer side of the wave spring 30, and a slot 22 is provided on the radial outer side of the friction flange 20; the wave spring 30 is fixedly connected to the friction flange 20 by inserting the claw 33 into the slot 22 of the friction flange 20. In some other embodiments, the wave spring 30 and the friction flange 20 may also be integrally formed.

[0043] Furthermore, if Figure 2 and Figure 5As shown, a slope 11 is provided on the side of the friction sleeve 10 opposite to the wave spring 30 , and a protrusion 31 is provided on the side of the wave spring 30 opposite to the friction sleeve 10 .

[0044] In this embodiment, the first direction is defined as the rotation direction of the hub 200 when the torque is transmitted in the reverse direction. Figure 4 and Figure 5 The second direction is defined as the rotation direction of the hub 200 when the torque is transmitted in the positive direction. Figure 4 and Figure 5 As shown by arrow D2, the axial dimension of the inclined surface 11 gradually decreases along the first direction D1.

[0045] When the hub 200 drives the friction sleeve 10 to rotate relative to the friction flange 20 in the first direction D1 (i.e., reverse torque transmission), Figure 6 As shown, the inclined surface 11 will abut against the protrusion 31. Since the protrusion 31 is a part of the wave spring 30, the wave spring 30 can be elastically deformed, such as Figure 7 As shown, as the hub 200 drives the friction sleeve 10 to continue to rotate in the first direction D1, the inclined surface 11 of the friction sleeve 10 will continue to squeeze the protrusion 31, so the inclined surface 11 and the protrusion 31 interfere with each other in the circumferential and axial directions. The inclined surface 11 squeezes the protrusion 31, causing elastic deformation of the protrusion 31, so that the friction force between the friction flange 20 and the first support plate 300 changes.

[0046] As the hub 200 drives the friction sleeve 10 to rotate in the first direction D1, the squeezing force of the inclined surface 11 on the protrusion 31 increases, that is, the friction force between the friction flange 20 and the first support plate 300 gradually increases. Fig. 9 Therefore, the friction force between the friction flange 20 and the first support plate 300 changes with the rotation angle of the hub 200 in the first direction D1, and the speed of change of the friction force, that is, the slope of the A slope, depends on the inclination angle of the inclined surface 11.

[0047] The inclined surface 11 may be a plane, a curved surface, or an irregular contact surface.

[0048] When the hub 200 drives the friction sleeve 10 to rotate relative to the friction flange 20 in the second direction D2 (i.e., transmitting torque in the positive direction), Figure 8 As shown, the inclined surface 11 is separated from the protrusion 31 , and there is no interference between the inclined surface 11 and the protrusion 31 , so the friction force between the friction flange 20 and the first support plate 300 remains unchanged.

[0049] It can be seen that the friction assembly 100 of the present invention can increase the damping when transmitting torque in the reverse direction, and can also keep the damping unchanged when transmitting torque in the forward direction, thereby achieving the effect of variable damping, especially the effect of increasing damping in one direction. The increased damping makes the damping in both the forward and reverse torque transmissions within the preset range, and can simultaneously meet the requirements of vibration absorption and torque transmission efficiency.

[0050] In some embodiments, the friction sleeve 10 includes a plurality of inclined surfaces 11 along the circumferential direction, and the wave spring 30 includes a plurality of protrusions 31 along the circumferential direction. The number and position of the inclined surfaces 11 match the number and position of the protrusions 31, and the inclined surfaces 11 and the protrusions 31 are arranged at equal intervals along the circumferential direction. In this way, the friction sleeve 10 and the wave spring 30 can be subjected to uniform force in the circumferential direction.

[0051] In some embodiments, when the torque is transmitted in the forward direction, the wave spring 30 is spaced from the friction sleeve 10 in both the axial direction and the circumferential direction, the protrusion 31 of the wave spring 30 does not abut against the protrusion 31 of the friction sleeve 10, and the friction assembly 100 does not provide damping force for the wheel hub 200 when the torque is transmitted in the forward direction. Only when the torque is transmitted in the reverse direction, the inclined surface 11 of the friction sleeve 10 abuts against the protrusion 31 of the wave spring 30, so that friction is generated between the friction flange 20 and the first support plate 300.

[0052] In this embodiment, when the torque is transmitted in the positive direction, the protrusion 31 of the wave spring 30 also abuts against the friction sleeve 10 , that is, the protrusion 31 of the wave spring 30 is separated from the inclined surface 11 in the circumferential direction, but abuts against the friction sleeve 10 in the axial direction.

[0053] Specifically, Figures 2 to 8 As shown, a groove 13 and a convex block 14 are provided on one axial side of the friction sleeve 10. That is, the convex block 14 and the groove 13 are arranged crosswise along the circumferential direction W of the friction sleeve 10.

[0054] The groove 13 includes a first plane 12 and an inclined plane 11, and the protrusion 14 includes a second plane 15, which is transitionally connected to the first plane 12 via the inclined plane 11. The first plane 12 and the second plane 15 are parallel and are radial planes perpendicular to the axial direction.

[0055] The wave spring 30 further includes a flat section 32, and the flat section 32 and the protrusion 31 are arranged crosswise along the circumferential direction. Figure 1 As shown, the axial sides of the plane section 32 are respectively in contact with the second plane 15 and the friction flange 20. Figures 5 to 8 As shown, the protrusion 31 of the wave spring 30 is located in the groove 13 and always abuts against the first plane 12 in the axial direction. In this way, the stacking space of the friction assembly 100 in the axial direction can be reduced.

[0056] Furthermore, the circumferential length of the protrusion 31 of the wave spring 30 is smaller than the circumferential length of the groove 13, and the circumferential length of the plane section 32 of the wave spring 30 is larger than the circumferential length of the second plane 15. In this way, the friction sleeve 10 is allowed to rotate relative to the wave spring 30 or the friction flange 20, so that the protrusion 31 of the wave spring 30 is circumferentially separated from the inclined surface 11 of the friction sleeve 10.

[0057] In some embodiments, the inner wall of the friction flange 20 is provided with a plurality of tooth grooves 21 along the circumferential direction; the friction assembly 100 is provided with a plurality of latch teeth 40 connected to the friction sleeve 10 in a torsion-proof manner. In this embodiment, the latch teeth 40 are located on the outer wall of the hub 200. When the friction flange 20 is sleeved on the outside of the hub 200, the tooth grooves 21 are aligned with the latch teeth 40, so that the latch teeth 40 are located in the tooth grooves 21. Figure 4 As shown, the tooth width of the tooth groove 21 is greater than the tooth width of the latching tooth 40 . When the latching tooth 40 abuts against the tooth groove 21 , the friction flange 20 and the friction sleeve 10 are driven to rotate together.

[0058] Specifically, Figure 6 As shown, when the inclined surface 11 of the friction sleeve 10 just abuts against the protrusion 31, the wheel hub 200 is at 0°. Figure 4 There is a gap between the right outer wall of the latch 40 and the right inner wall of the tooth groove 21 , wherein the width of the gap determines the rotation angle of the wheel hub 200 relative to the friction flange 20 . In this embodiment, the width of the gap allows the wheel hub 200 to rotate 3° relative to the friction flange 20 .

[0059] When the hub 200 rotates in the first direction, Figure 7 The arrow D1 shown and Figure 4 As shown by arrow D1, Figure 7 As shown, the inclined surface 11 of the friction sleeve 10 and the protrusion 31 of the wave spring 30 interfere with each other. Figure 4 As shown, the right outer wall of the latch tooth 40 of the wheel hub 200 approaches the right inner wall of the tooth groove 21 of the friction flange 20. When the right outer wall of the latch tooth 40 abuts against the right inner wall of the tooth groove 21, the wheel hub 200 overcomes the friction force between the friction flange 20 and the first support plate 300, drives the friction flange 20 to rotate in the first direction, and the friction force between the wheel hub 200 and the first support plate 300 reaches the maximum and no longer changes, as shown in FIG. Fig. 9 The straight line B is shown.

[0060] When the wheel hub 200 rotates in the second direction, Figure 8 The arrow D2 shown and Figure 4 As shown by arrow D2, Figure 8As shown, the inclined surface 11 of the friction sleeve 10 and the protrusion 31 of the wave spring 30 are circumferentially separated until the left outer wall of the latch tooth 40 of the hub 200 abuts against the right inner wall of the tooth groove 21 of the friction flange 20 (as shown in FIG. Figure 4 As shown), the wheel hub 200 overcomes the friction between the friction flange 20 and the first support plate 300, driving the friction flange 20 to rotate in the second direction, and the friction between the wheel hub 200 and the first support plate 300 is minimal and no longer changes, as shown in FIG. Fig. 9 The straight line C is shown.

[0061] It can be seen from this that when the torsional vibration damper transmits torque in the positive direction, there is also a small and constant friction force between the wheel hub 200 and the first support plate 300, such as Fig. 9 The straight line C shown in the figure increases the damping of the wheel hub 200 when the torque is transmitted in the forward direction within the preset damping range, and reduces the torsional vibration and torsional impact of the wheel hub 200 when the torque is transmitted in the forward direction, which is beneficial to improving the noise, vibration and harshness (NVH) of the entire vehicle.

[0062] Based on the same inventive concept, the present invention also provides a torsional vibration damper. The specific manner in which the functions implemented in the torsional vibration damper in the above embodiment are implemented has been described in detail in the embodiment of the friction assembly 100 and will not be elaborated here.

[0063] It is to be understood that in the present invention, "plurality" refers to two or more than two, and other quantifiers are similar. "And / or" describes the association relationship of associated objects, indicating that three relationships may exist. For example, A and / or B can represent: A exists alone, A and B exist at the same time, and B exists alone. The character " / " generally indicates that the associated objects before and after are in an "or" relationship. The singular forms "a", "the" and "the" are also intended to include plural forms, unless the context clearly indicates other meanings.

[0064] It is further understood that the terms "first", "second", etc. are used to describe various structures, but these structures should not be limited to these terms. These terms are only used to distinguish structures of the same type from each other, and do not indicate a specific order or importance. In fact, the expressions "first", "second", etc. can be used interchangeably. For example, without departing from the scope of the present invention, a first structure can also be referred to as a second structure, and similarly, a second structure can also be referred to as a first structure.

[0065] Those skilled in the art will readily appreciate other embodiments of the present invention after considering the specification and practicing the invention disclosed herein. This application is intended to cover any variations, uses or adaptations of the present invention, which follow the general principles of the present invention and include common knowledge or customary techniques in the art that are not disclosed by the present invention. The specification and examples are intended to be exemplary only, and the true scope and spirit of the present invention are indicated by the following scope of rights.

[0066] It should be understood that the present invention is not limited to the precise structures described above and shown in the drawings, and that various modifications and changes may be made without departing from the scope thereof. The scope of the present invention is limited only by the scope of the appended claims.

Claims

1. A variable damping friction assembly (100), characterized in that: include: A friction sleeve (10), wherein an inclined surface (11) is provided on one axial side of the friction sleeve (10); a friction flange (20), located on one axial side of the friction sleeve (10) and having a fixed axial spacing with the friction sleeve (10); and a wave spring (30) axially located between the friction sleeve (10) and the friction flange (20) and connected to the friction flange (20) in a torsion-resistant manner, and a protrusion (31) is provided on a side of the wave spring (30) close to the friction sleeve (10); Wherein, when the friction sleeve (10) rotates in a first direction (D1) relative to the friction flange (20), the inclined surface (11) abuts against the protrusion (31) and axially presses the protrusion (31); When the friction sleeve (10) rotates in a second direction (D2) relative to the friction flange (20), the inclined surface (11) is separated from the protrusion (31).

2. The variable damping friction assembly (100) according to claim 1, characterized in that: The friction sleeve (10) is provided on one axial side with: A groove (13) comprising a first plane (12) and the inclined surface (11); and The convex block (14) comprises a second plane (15), wherein the second plane (15) is transitionally connected to the first plane (12) via the inclined surface (11), The wave spring (30) is respectively fitted with the second plane (15) and the friction flange (20) on both axial sides, and the protrusion (31) of the wave spring (30) is located in the groove (13) and abuts against the first plane (12).

3. The variable damping friction assembly (100) according to claim 1, characterized in that: The inner wall of the friction flange (20) is provided with a plurality of tooth grooves (21) along the circumferential direction (W); The friction assembly (100) is provided with a latching tooth (40) which is connected to the friction sleeve (10) in a torsion-proof manner. The latching tooth (40) is located in the tooth groove (21), and the tooth width of the tooth groove (21) is greater than the tooth width of the latching tooth (40). When the latching tooth (40) abuts against the tooth groove (21), the friction flange (20) and the friction sleeve (10) are driven to rotate together.

4. The variable damping friction assembly (100) according to claim 1, characterized in that: A clamping groove (22) is provided on the radial outer side of the friction flange (20); A claw (33) is provided on the radial outer side of the wave spring (30) at a position corresponding to the slot (22), and the claw (33) is engaged with the slot (22) to fix the wave spring (30) to the friction flange (20).

5. The variable damping friction assembly (100) according to claim 1, characterized in that: The friction sleeve (10) comprises a plurality of inclined surfaces (11) along the circumferential direction (W); and The wave spring (30) includes a plurality of protrusions (31) along a circumferential direction (W).

6. The variable damping friction assembly (100) according to claim 1, characterized in that: The inclined surface (11) is an inclined plane or an inclined curved surface.

7. The variable damping friction assembly (100) according to claim 1, characterized in that: The friction sleeve (10) is made of hard plastic, and The friction flange (20) is made of metal material.

8. A torsional vibration damper, characterized in that: include: Wheel hub (200); A first support plate (300) rotatably connected to one axial end of the hub (200); A second support plate (400) is torsionally connected to the first support plate (300) and is rotationally connected to the other axial end of the wheel hub (200); as well as The variable damping friction assembly (100) according to any one of claims 1 to 7, The friction assembly (100) is sleeved on the outside of the wheel hub (200) and axially abuts between the wheel hub (200) and the first support plate (300).

9. The torsional vibration damper according to claim 8, characterized in that: The friction sleeve (10) is connected to the wheel hub (200) in a torsion-resistant manner; The friction flange (20) is in frictional contact with the first support plate (300). When the friction sleeve (10) rotates in a first direction (D1) relative to the friction flange (20), a changing friction force is generated between the friction flange (20) and the first support plate (300); when the friction sleeve (10) rotates in a second direction (D2) relative to the friction flange (20), the friction force between the friction flange (20) and the first support plate (300) remains unchanged.

10. The torsional vibration damper according to claim 8, characterized in that: The outer wall of the wheel hub (200) is provided with a plurality of latch teeth (40) along the circumferential direction (W).

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