Shock absorber

Abstract

The utility model relates to a shock absorber. The shock absorber comprises a spoke spring buffering piece, the spoke spring buffering piece comprises a center part, an outer ring part and a plurality of spoke springs, the outer ring part coaxially surrounds the radial outer side of the center part, and the spoke springs are connected between the outer ring part and the center part in the radial direction and distributed at intervals in the circumferential direction. The plurality of spoke springs are elastically deformable to allow the outer ring portion to rotate relative to the central portion. The shock absorber further comprises a side plate assembly and one or more friction rollers, the side plate assembly comprises an outer ring part section coaxially fixed relative to the center part, the outer ring part section comprises one or more track grooves penetrating in the axial direction, and each friction roller is installed on the outer ring part so as to be capable of rotating relative to the center part along with the outer ring part. And when the outer ring part rotates relative to the central part, each friction roller can move along the corresponding track groove and is in frictional contact with the edge of the corresponding track groove. The shock absorber provided by the utility model has an improved structure.

Description

Technical Field

[0001] The utility model relates to the technical field of vehicles, and in particular to a shock absorber for a transmission system of a motor vehicle. Background Art

[0002] In traditional fuel vehicles or hybrid vehicles, the crankshaft of the internal combustion engine is often affected by torque vibration. The torque vibration of the crankshaft can cause crankshaft damage and NVH (noise, vibration and harshness) problems. The current conventional solution to this problem is to set a rubber vibration damper (TVD). The TVD vibration damper mainly uses the friction generated by the rotation of the outer ring with a large moment of inertia relative to the rubber elastic element to consume the energy of torsional vibration, thereby reducing the torsional amplitude of the crankshaft and avoiding resonance within the commonly used speed range. However, due to the limitation of the installation space, this type of vibration damper is often difficult to provide sufficient attenuation for the torsional vibration of the crankshaft, and the rubber is prone to aging under the heat generated by friction, thus affecting the service life.

[0003] CN 115182963 A proposes a novel spoke spring type shock absorber. The spoke spring type shock absorber comprises a plurality of spoke spring buffers, each of which has different radial dimensions, so as to provide multiple frequencies to buffer the torque vibration of the crankshaft. Since different spoke spring buffers have different shapes and sizes, the shock absorber requires a more complicated processing technology and a higher production cost. Moreover, the damping provided by the shock absorber depends only on the shapes of the spoke spring buffers and the friction between them, and the damping that can be provided is limited. In addition, especially when the friction damping is small, if the deformation of the spoke spring buffer is too large, the spoke spring buffer may break and fail. Utility Model Content

[0004] Therefore, the technical problem that the utility model needs to solve is to provide an improved shock absorber.

[0005] The above technical problems are solved by a shock absorber according to the utility model. The shock absorber includes a spoke spring buffer, which includes a central part, an outer ring part and a plurality of spoke springs, the outer ring part coaxially surrounds the radial outer side of the central part, the plurality of spoke springs are respectively connected between the outer ring part and the central part in the radial direction and are distributed at intervals along the circumferential direction, and the plurality of spoke springs can be elastically deformed so as to allow the outer ring part to rotate relative to the central part. The shock absorber also includes a side plate assembly and one or more friction rollers, the side plate assembly includes an outer ring segment coaxially fixed relative to the central part, the outer ring segment and the outer ring part are axially opposite to each other so as to have at least partially overlapping axial projections, the outer ring segment includes one or more track grooves penetrating in the axial direction, each friction roller is mounted on the outer ring part so as to be able to rotate with the outer ring part relative to the central part, and each friction roller passes through the corresponding track groove in the axial direction, so that when the outer ring part rotates relative to the central part, each friction roller can move along the corresponding track groove and make friction contact with the edge of the corresponding track groove. As the friction roller moves in the track groove as the outer ring rotates, friction can be generated, thereby improving the damping effect on the outer ring. At the same time, the distribution of friction damping within the rotation range can be flexibly adjusted by matching the shape of the friction roller and the track groove. In addition, the track groove can also limit the rotation range of the outer ring, thereby preventing the spoke spring from being damaged due to excessive deformation.

[0006] According to a preferred embodiment of the utility model, the track groove of each friction roller can extend along an arc line convex toward the radial outside, so that the extension direction of the track groove is adapted to the moving direction of the friction roller.

[0007] According to another preferred embodiment of the utility model, the track groove of each friction roller may have a width perpendicular to the extension direction, and the width of the track groove of each friction roller may vary in the extension direction, so that each friction roller has different friction contact areas and / or friction contact pressures at different positions in the corresponding track groove, thereby generating different friction damping; and / or, the rotation direction of each friction roller around the central portion and the extension direction of the corresponding track groove may be at least partially non-parallel, so that each friction roller has different friction contact pressures at different positions in the corresponding track groove, thereby generating different friction damping. This allows the friction damping to vary as required during the rotation of the outer ring portion.

[0008] According to another preferred embodiment of the utility model, the outer ring portion may have a neutral position relative to the central portion, which makes the plurality of spoke springs inelastically deformable, and two predetermined maximum rotation positions that deviate from the neutral position in two opposite rotation directions, respectively, and the friction damping generated between each friction roller and the corresponding track groove at the neutral position is smaller than the friction damping generated at the two predetermined maximum rotation positions. This means that when the outer ring portion rotates relative to the central portion to an area close to the predetermined maximum rotation position, the friction roller will generate greater friction damping, thereby preventing the outer ring portion from rotating too much.

[0009] According to another preferred embodiment of the utility model, each friction roller can be rotatably mounted on the outer ring portion, so that each friction roller can rotate relative to the outer ring portion around its own central axis when the outer ring portion moves in the corresponding track groove. In other words, the friction roller can roll in the track groove.

[0010] According to another preferred embodiment of the utility model, the spoke spring buffer may include a plurality of laminations stacked in the axial direction, each lamination having the same shape and size in a plane perpendicular to the axial direction, the plurality of laminations being fixedly connected together in the central portion, each friction roller passing through each of the plurality of laminations in the axial direction and having different matching clearances relative to different laminations in the plurality of laminations, so that the rotation of the outer ring portion relative to the central portion can be performed in the plurality of laminations in an incompletely synchronous manner, thereby generating friction damping between the plurality of laminations. This enables the outer ring portion to provide greater friction damping.

[0011] According to another preferred embodiment of the utility model, the outer ring segment can directly or indirectly abut the outer ring portion axially via a friction pad, so as to directly or indirectly frictionally contact the outer ring portion when the outer ring portion rotates relative to the center portion, thereby providing additional friction damping.

[0012] According to another preferred embodiment of the utility model, the side plate assembly may include two outer ring segments, the outer ring portion is axially located between the two outer ring segments, and each friction roller passes through two corresponding track grooves respectively located on the two outer ring segments in the axial direction. This enables the friction roller to provide greater friction damping and ensures that the force on the friction roller is balanced in the axial direction.

[0013] According to another preferred embodiment of the utility model, each friction roller may include two axial ends of two corresponding track grooves protruding from the two outer ring segments in the axial direction away from the outer ring portion, and two flanges formed on the two axial ends, and the two flanges of each friction roller respectively abut the two outer ring segments in the axial direction to define the axial position of each friction roller. Such flanges can be formed by a stamping process.

[0014] According to another preferred embodiment of the utility model, the side plate assembly may include two outer edge segments extending radially outward from the two outer ring segments and crossing the outer ring portion, the two outer edge segments are fixedly connected to each other, and the side plate assembly also includes an inner segment, the inner segment extends radially inward from one of the two outer ring segments and is fixedly connected to the center portion. The two outer ring segments are thus connected together and fixed to the center portion through the inner segment on one side. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] The present invention is further described below in conjunction with the accompanying drawings. The same reference numerals in the drawings represent components with the same functions. Among them:

[0016] Figure 1 A front view showing a shock absorber according to an exemplary embodiment of the present invention;

[0017] Figure 2 A cross-sectional view showing a vibration absorber according to an exemplary embodiment of the present invention at section AA; and

[0018] Figure 3 A partial detail view of a vibration absorber at a track groove according to an exemplary embodiment of the present invention is shown. DETAILED DESCRIPTION

[0019] The following will describe the specific implementation of the shock absorber according to the utility model in conjunction with the accompanying drawings. The following detailed description and drawings are used to exemplarily illustrate the principle of the utility model. The utility model is not limited to the preferred embodiments described, and the protection scope of the utility model is defined by the claims.

[0020] According to an embodiment of the utility model, a vibration damper for a transmission system is provided. Such a vibration damper can be installed on a crankshaft of an engine, for example, to buffer the torque vibration of the crankshaft, or can be installed in a transmission system of other machinery to buffer the torque vibration. Such a vibration damper can provide a buffering and vibration reduction effect based on a spoke spring and additional friction damping.

[0021] The following combination Figures 1 to 3 The exemplary embodiment shown is used to illustrate the specific structure of the shock absorber according to the present invention. Figure 1 shows a front view of a vibration absorber according to an exemplary embodiment of the present invention, Figure 2 shows a cross-sectional view of the shock absorber through the central axis, Figure 3 A partial detail view of the shock absorber is shown.

[0022] like Figure 1 As shown in FIG, the shock absorber is generally in the shape of a disc. Figure 2 As shown, the shock absorber mainly includes a spoke spring buffer 10 , a side plate assembly 20 and one or more friction rollers 30 .

[0023] The spoke spring buffer 10 can be an integrally formed component or a whole formed by a plurality of laminations stacked and fixed together in the axial direction. When the spoke spring buffer 10 is formed by a plurality of laminations stacked, each lamination has the same shape and size in a plane perpendicular to the axial direction.

[0024] like Figure 1 As shown, the spoke spring buffer 10 includes a central portion 11, an outer ring portion 13 and a plurality of spoke springs 12. The spoke spring buffer 10 has a central axis parallel to the axial direction. The central portion 11 is a plate-like component that is generally annular or disc-shaped and formed around the central axis. The outer ring portion 13 coaxially surrounds the radially outer side of the central portion 11 and is radially spaced apart from the central portion 11. Each spoke spring 12 extends substantially radially between the outer ring portion 13 and the central portion 11 so as to connect the outer ring portion 13 and the central portion 11 as a whole. The plurality of spoke springs 12 of the spoke spring buffer 10 are spaced apart in the circumferential direction, preferably uniformly distributed in the circumferential direction, and each spoke spring 12 may preferably have substantially the same shape and size. For example, if applied in the transmission system of a motor vehicle, the spoke spring buffer 10 can be connected to the engine crankshaft (not shown) in a torsionally fixed manner, in particular, fixedly connected (directly or indirectly, for example, via the side plate assembly 20 described below), so that it can rotate synchronously with the engine crankshaft around the central axis of the spoke spring buffer 10. The spoke springs 12 of the spoke spring buffer 10 are made of elastic material, so when torque vibration occurs on the spoke spring buffer 10, the spoke springs 12 can be elastically deformed, thereby allowing the outer ring portion 13 to rotate relative to the central portion 11 around the central axis within a certain range (depending on the torque size and the elastic deformation capacity of the spoke spring 12), thereby buffering the torque vibration.

[0025] The side plate assembly 20 is coaxially arranged with the spoke spring buffer 10 so as to have a common central axis. Figure 1 and Figure 2 As shown, the side plate assembly 20 includes one or two outer ring segments 21. Each outer ring segment 21 is in a generally annular shape around the central axis. The entire side plate assembly 20 including the outer ring segment 21 is coaxially fixed relative to the central portion 11. Each outer ring segment 21 and the outer ring portion 13 are axially opposite to each other so as to have at least partially overlapping axial projections. When the side plate assembly 20 includes two outer ring segments 21, the outer ring portion 13 is axially located between the two outer ring segments 21. The two outer ring segments 21 of the side plate assembly 20 can be fixed together and then fixed together to the central portion 11. For example, as Figure 2As shown, the side plate assembly 20 may include two outer edge segments 22 and an inner segment 23: the two outer edge segments 22 extend radially outward from the two outer ring segments 21 respectively over the outer ring portion 13, and are fixedly connected to each other on the radial outer side of the outer ring portion 13 (for example, by a first fastener 40, such as a rivet or a screw, etc.); the inner segment 23 extends radially inward from one of the two outer ring segments 21 and is fixedly connected to the center portion 11, for example, via a second fastener 50 (such as a screw or a rivet). When the spoke spring buffer 10 is formed by a plurality of laminations, the laminations may also be fixed to each other via the second fastener 50. This makes it so that there is no relative movement between the plurality of laminations in the center portion 11 and between the center portion 11 and the entire side plate assembly 20. In addition, the inner segment 23 of the side plate assembly 20 may also be formed with a hub at the inner edge so as to be fixed to, for example, an engine crankshaft, so that the entire shock absorber may also be mounted to the engine crankshaft via the side plate assembly 20. Alternatively, the two outer ring segments 21 of the side plate assembly 20 may also be fixed to the axial sides of the center portion 11. For example, the side plate assembly 20 may include two inner segments 23, which extend radially inward from the two outer ring segments 21 and are fixedly connected to the axial sides of the center portion 11, for example, via second fasteners 50 (such as screws or rivets).

[0026] like Figure 1 As shown, each outer ring segment 21 includes one or more track grooves 24 extending in the axial direction. Each track groove 24 extends substantially in a plane perpendicular to the axial direction. When each outer ring segment 21 includes a plurality of track grooves 24, these track grooves 24 are spaced and preferably evenly distributed in the circumferential direction. Each friction roller 30 is mounted on the outer ring portion 13 and can rotate relative to the central portion 11 along with the outer ring portion 13. For each friction roller 30, a corresponding track groove 24 is formed on the outer ring segment 21 on either side. Each friction roller 30 passes through the corresponding track groove 24 in the axial direction. If the side plate assembly 20 of the shock absorber includes only one outer ring segment 21, each friction roller 30 passes through a corresponding track groove 24 in the axial direction; if the side plate assembly 20 of the shock absorber includes two outer ring segments 21 on both sides, the axial ends of the friction roller 30 pass through two corresponding track grooves 24 respectively. The track grooves 24 corresponding to the same friction roller 30 on the two outer ring segments 21 have substantially overlapping projections in the axial direction.

[0027] When the outer ring portion 13 rotates relative to the central portion 11, each friction roller 30 also rotates relative to the central portion 11 around the central axis of the spoke spring buffer 10, while each track groove 24 and the entire side plate assembly 20 remain stationary relative to the central portion 11. Therefore, each friction roller 30 also moves along the corresponding track groove 24 as the central portion 11 rotates. Each friction roller 30 contacts a portion of the edge of the corresponding track groove 24, and thus forms friction contact with the edge of the track groove 24 when moving along the corresponding track groove 24. This friction contact can provide a damping force that hinders the outer ring portion 13 from rotating relative to the central portion 11.

[0028] Preferably, the track groove 24 of each friction roller 30 can extend along an arc. The arc is an arc that bulges toward the radial outside of the outer ring segment 21. The track groove 24 of each friction roller 30 has a certain width in a direction perpendicular to its own extension direction. Through the specific design of the extension direction and / or width of the track groove 24, the friction contact pressure and / or friction contact area between the friction roller 30 and the track groove 24 can present a desired distribution state (for example, constant or variable) within the extension range of the track groove 24, thereby making the friction damping present a desired distribution state within the rotation range of the outer ring portion 13. The change in the friction contact area here means that the friction roller 30 can contact the edges of both sides of the track groove 24 at the same time in a part of the track groove 24, and can only contact the edge of one side of the track groove 24 in another part of the track groove 24.

[0029] If constant friction damping is desired, the width of the track groove 24 of each friction roller 30 is kept substantially constant in the extension direction, and the rotation direction of each friction roller 30 around the central portion 11 and the extension direction of the corresponding track groove 24 are always kept substantially coincident or substantially parallel. Therefore, during the movement of the friction roller 30 along the track groove 24, the friction contact pressure and friction contact area between the friction roller 30 and the track groove 24 remain constant, thereby maintaining substantially constant friction damping.

[0030] If a variable friction damping is desired, it can be achieved in the following two ways. First, the friction damping is changed by changing the width of the track groove 24. Specifically, the width of the track groove 24 of each friction roller 30 can be changed in the extension direction, so that each friction roller 30 has different friction contact areas (only contacts the edge of one side of the track groove 24 or even does not contact the edge of the track groove 24 in a section with a larger width, and contacts the edges of both sides of the track groove 24 at the same time in a section with a smaller width) and / or different friction contact pressures at different positions in the corresponding track groove 24, thereby generating different friction damping. Second, the friction damping is changed by the extension direction of the track groove 24. Specifically, the rotation direction of each friction roller 30 around the center portion 11 and the extension direction of the corresponding track groove 24 are at least partially non-parallel, so that each friction roller 30 has different friction contact pressures at different positions in the corresponding track groove 24, thereby generating different friction damping. For example, as Figure 3 As shown, there is a non-zero angle between the rotation direction R of the friction roller 30 at the current position and the extension direction E of the track groove 24 at the corresponding position. At this time, the friction roller 30 only contacts the radial inner edge of the track groove 24. If the friction roller 30 continues to move clockwise in the track groove 24 from the current position, the angle will cause the friction roller 30 to further squeeze the radial inner edge of the track groove 24, thereby increasing the friction contact pressure and friction damping. The above two methods can be used alone or together.

[0031] The allowable rotation range of the outer ring portion 13 relative to the central portion 11 can be limited by the cooperation of the friction roller 30 and the track groove 24. The outer ring portion 13 can have a neutral position located in the middle of the allowable rotation range and two predetermined maximum rotation positions located at both ends of the allowable rotation range. At the neutral position, all spoke springs 12 are not elastically deformed. The two predetermined maximum rotation positions deviate from the neutral position in two opposite rotation directions, respectively. In this case, the variable friction damping achieved by the above method can present the following distribution: the friction damping generated between each friction roller 30 and the corresponding track groove 24 at the neutral position is less than the friction damping generated at the two predetermined maximum rotation positions. That is, the friction roller 30 provides greater friction damping at the predetermined maximum rotation position close to the spoke spring 12 that produces the maximum elastic deformation relative to the neutral position without elastic deformation. This can effectively reduce the risk of damage to the spoke spring 12 due to excessive deformation.

[0032] Preferably, each friction roller 30 can be rotatably mounted on the outer ring portion 13, so that each friction roller 30 can rotate relative to the outer ring portion 13 around its own central axis as the outer ring portion 13 moves in the corresponding track groove 24. The friction roller 30 can thus roll and contact the edge of the track groove 24.

[0033] When the side plate assembly 20 includes two outer ring segments 21 located on both sides in the axial direction, preferably, each friction roller 30 may include two axial ends of two corresponding track grooves 24 protruding from the two outer ring segments 21 in the axial direction away from the outer ring portion 13, and two flanges formed on the two axial ends. The two flanges of each friction roller 30 abut against the two outer ring segments 21 in the axial direction, thereby defining the axial position of each friction roller 30. Such flanges may be formed by a stamping process after the friction roller 30 is installed.

[0034] In a preferred embodiment, when the spoke spring buffer 10 includes a plurality of laminations stacked in the axial direction, the laminations can be fixedly connected together in the central portion 11 so that the laminations in the central portion 11 can move completely synchronously. At the same time, the laminations are constrained in the spoke spring 12 and the outer ring portion 13 only by the friction rollers 30, each of which passes through each of the laminations in the axial direction and has different fitting clearances relative to different laminations. Therefore, the laminations with larger fitting clearances and the laminations with smaller clearances can be slightly offset from each other in the outer ring portion 13, so that the rotation of the outer ring portion 13 relative to the central portion 11 can be performed in the laminations in an incompletely synchronous manner. Thereby, friction damping can be generated between the laminations.

[0035] In a preferred embodiment, each outer ring segment 21 can also directly abut the outer ring portion 13 axially, or can also indirectly abut the outer ring portion 13 axially via a friction gasket, which enables each outer ring segment 21 to directly or indirectly frictionally contact the outer ring portion 13 when the outer ring portion 13 rotates relative to the center portion 11, thereby providing additional friction damping.

[0036] The shock absorber according to the present invention can generate a buffering effect by rotating the outer ring relative to the center part on the one hand, and can also provide an additional damping effect by the friction contact between the friction roller and the track groove on the other hand, thereby improving the vibration reduction performance of the shock absorber. At the same time, by adjusting the shape and size of the track groove, a desired friction damping distribution state can be obtained within the rotation range of the outer ring part, which helps to flexibly design the damping effect and prevent the outer ring part from rotating excessively, thereby reducing the risk of damaging the spoke spring and increasing the service life.

[0037] Although possible embodiments are described exemplarily in the above description, it should be understood that there are still a large number of variations of embodiments through all known and other technical features and embodiments that can be easily thought of by the technician. It should also be understood that the exemplary embodiment is only an example, and such an embodiment does not limit the scope of protection, application and configuration of the utility model in any form. The above description is more to provide a technical guide for converting at least one exemplary embodiment to the technician, wherein various changes can be made, especially changes in the functions and structures of the components, as long as they do not depart from the scope of protection of the claims.

[0038] Reference numerals list

[0039] 10 Spoke spring buffer

[0040] 11 Center

[0041] 12 Spoke Spring

[0042] 13 Outer ring

[0043] 20 Side panel assembly

[0044] 21 Outer ring segment

[0045] 22 Outer edge section

[0046] 23 Medial segment

[0047] 24 Track Slots

[0048] 30 Friction roller

[0049] 40 First Fastener

[0050] 50 Second fastener

[0051] E Extension direction

[0052] R Rotation direction

[0053] AA Section

Claims

1. A shock absorber, comprising a spoke spring buffer (10), the spoke spring buffer (10) comprising a central portion (11), an outer ring portion (13) and a plurality of spoke springs (12), the outer ring portion (13) coaxially surrounding the radial outer side of the central portion (11), the plurality of spoke springs (12) respectively connected radially between the outer ring portion (13) and the central portion (11) and distributed at intervals in the circumferential direction, the plurality of spoke springs (12) being elastically deformable so as to allow the outer ring portion (13) to rotate relative to the central portion (11), It is characterized in that The vibration damper further comprises a side plate assembly (20) and one or more friction rollers (30), wherein the side plate assembly (20) comprises an outer ring segment (21) coaxially fixed relative to the central portion (11), wherein the outer ring segment (21) and the outer ring portion (13) are axially opposed to each other so as to have at least partially overlapping axial projections, wherein the outer ring segment (21) comprises one or more track grooves (24) extending axially therethrough, wherein each friction roller (30) is mounted on the outer ring portion (13) so as to be able to rotate with the outer ring portion (13) relative to the central portion (11), and each friction roller (30) passes through the corresponding track groove (24) axially, so that when the outer ring portion (13) rotates relative to the central portion (11), each friction roller (30) is able to move along the corresponding track groove (24) and come into frictional contact with the edge of the corresponding track groove (24).

2. The shock absorber according to claim 1, characterized in that: The track groove (24) of each friction roller (30) extends along an arc line convex toward the radial outside.

3. The shock absorber according to claim 2, characterized in that: The track groove (24) of each friction roller (30) has a width perpendicular to the extension direction, and the width of the track groove (24) of each friction roller (30) varies in the extension direction, so that each friction roller (30) has different friction contact areas and / or friction contact pressures at different positions in the corresponding track groove (24), thereby generating different friction damping; and / or The rotation direction of each friction roller (30) around the central portion (11) and the extension direction of the corresponding track groove (24) are at least partially non-parallel, so that each friction roller (30) has different friction contact pressures at different positions in the corresponding track groove (24), thereby generating different friction damping.

4. The shock absorber according to claim 3, characterized in that The outer ring portion (13) has a neutral position relative to the central portion (11) so that the multiple spoke springs (12) are not elastically deformed, and two predetermined maximum rotation positions deviating from the neutral position in two opposite rotation directions, respectively, and the friction damping generated between each friction roller (30) and the corresponding track groove (24) at the neutral position is smaller than the friction damping generated at the two predetermined maximum rotation positions.

5. The vibration absorber according to claim 1, characterized in that: Each friction roller (30) is rotatably mounted on the outer ring portion (13), so that each friction roller (30) can rotate relative to the outer ring portion (13) around its own central axis as the outer ring portion (13) moves in the corresponding track groove (24).

6. The shock absorber according to claim 1, characterized in that The spoke spring buffer (10) comprises a plurality of laminations stacked in an axial direction, each lamination having the same shape and size in a plane perpendicular to the axial direction, the plurality of laminations being fixedly connected together in the central portion (11), each friction roller (30) passing through each of the plurality of laminations in an axial direction and having different fitting clearances relative to different laminations in the plurality of laminations, so that the outer ring portion (13) can rotate relative to the central portion (11) in an incompletely synchronous manner in the plurality of laminations, thereby generating friction damping between the plurality of laminations.

7. The vibration absorber according to claim 1, characterized in that: The outer ring segment (21) abuts against the outer ring portion (13) axially directly or indirectly via a friction pad, thereby directly or indirectly in friction contact with the outer ring portion (13) when the outer ring portion (13) rotates relative to the center portion (11).

8. The vibration absorber according to any one of claims 1 to 7, characterized in that The side plate assembly (20) comprises two outer ring segments (21), the outer ring portion (13) is axially located between the two outer ring segments (21), and each friction roller (30) axially passes through two corresponding track grooves (24) respectively located on the two outer ring segments (21).

9. The vibration absorber according to claim 8, characterized in that Each friction roller (30) comprises two axial ends protruding from two corresponding track grooves (24) on the two outer ring segments (21) respectively along the axial direction away from the outer ring portion (13), and two flanges respectively formed on the two axial ends. The two flanges of each friction roller (30) respectively abut against the two outer ring segments (21) along the axial direction to define the axial position of each friction roller (30).

10. The vibration absorber according to claim 8, characterized in that The side plate assembly (20) includes two outer edge segments (22) extending radially outward from the two outer ring segments (21) and crossing the outer ring portion (13), and the two outer edge segments (22) are fixedly connected to each other. The side plate assembly (20) also includes an inner segment (23), which extends radially inward from one of the two outer ring segments (21) and is fixedly connected to the center portion (11).

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