Vibration damper with adjustable damping force

Abstract

This utility model relates to a vibration damper with adjustable damping force, comprising: an inner tube; a piston rod disposed within the inner tube in a manner capable of axial reciprocating movement; a piston connected to the piston rod within the inner tube, the piston dividing the interior of the inner tube into two working chambers; the piston including a body and a check valve; the body forming independent flow channels and bypass channels; the check valve disposed in the flow channels and located on the working chamber side of the body closer to the piston rod; the check valve is configured to block the fluid connection between the two working chambers via the flow channels during the rebound phase, allow the fluid connection between the two working chambers via the flow channels during the compression phase, and allow the fluid connection between the two working chambers via the bypass channels during both the compression and rebound phases. The vibration damper of this utility model provides different fluid bypasses during the compression and rebound phases by forming independent flow channels and bypass channels within the piston, thereby achieving different damping forces.

Description

Technical Field

[0001] This utility model relates to the technical field of vibration dampers, and in particular to a vibration damper with adjustable damping force. Background Technology

[0002] In a shock absorber with adjustable damping force, there is an inner tube and an outer tube coaxially arranged around the inner tube. The inner tube is provided with a piston that can move axially to divide the piston into multiple working chambers. The damping valve is usually placed on the outside of the outer tube to achieve fluid communication between the multiple working chambers during the compression and rebound phases of the shock absorber.

[0003] The required damping force differs between the compression and rebound phases of a shock absorber to balance the demands for vehicle stability and comfort. However, existing shock absorbers adjust damping only through a single oil orifice, failing to autonomously adjust the damping force during both compression and rebound phases. Consequently, they cannot accommodate the varying damping force requirements at different operating stages. Furthermore, existing shock absorbers rely on solenoid valves for damping adjustment, resulting in a complex system and high adjustment costs. Utility Model Content

[0004] To address the problems existing in the prior art, this utility model provides an improved damper that provides different fluid bypasses during the compression and rebound phases by forming independent flow channels and bypass channels in the piston, thereby achieving different damping forces.

[0005] According to an embodiment of the present invention, a vibration damper with adjustable damping force is provided. The vibration damper includes: an inner tube at least partially filled with damping fluid; a piston rod disposed in the inner tube in a manner that allows axial reciprocating movement; and a piston connected to the piston rod in the inner tube and capable of reciprocating with the piston rod. The piston divides the interior of the inner tube into two working chambers, the two working chambers including a first working chamber on the piston rod side and a second working chamber away from the piston rod. The piston includes a body and a check valve. The body forms an independent flow channel and a bypass channel. The check valve is disposed in the flow channel and located on the side of the body closer to the first working chamber. The check valve is configured to block the fluid connection between the two working chambers via the flow channel during the rebound phase, and allow the fluid connection between the two working chambers via the flow channel during the compression phase, and allow the fluid connection between the two working chambers via the bypass channel during both the compression phase and the rebound phase.

[0006] In a preferred embodiment of this utility model, the check valve includes a valve disc and a spring member. The valve disc is disposed between the spring member and the body, so that the valve disc abuts against the body under the preload of the spring member.

[0007] In a preferred embodiment of the present invention, the piston body has a base, the valve disc and the spring are arranged in the base, and the flow channel is in fluid communication with the base.

[0008] In a preferred embodiment of the present invention, the base has a bottom surface, on which two rib-shaped rings protruding from the bottom surface along the axial direction toward the valve disc are coaxially disposed. The flow channel is formed between the two rib-shaped rings and passes through the body along the axial direction. The valve disc abuts against the two rib-shaped rings under the action of the preload generated by the spring.

[0009] In a preferred embodiment of the present invention, the check valve includes: a first damping disc assembly disposed on the side of the spring member away from the valve disc to form a reverse support for the spring member, and at least a portion of the first damping disc assembly is arranged in the base.

[0010] In a preferred embodiment of the present invention, the first damping disc assembly includes a first bypass disc, which abuts against the circumferential edge of the base and has an opening that allows the damping fluid to flow through the flow channel.

[0011] In a preferred embodiment of the present invention, the piston includes a second damping disc assembly, which is disposed on the side of the piston body near the second working chamber.

[0012] In a preferred embodiment of the present invention, the second damping disc assembly includes a second bypass disc having a notch for allowing the damping fluid to flow through the bypass channel.

[0013] In a preferred embodiment of the present invention, the second bypass disc is annular, and the notch is radially recessed inward from the outer peripheral surface of the second bypass disc.

[0014] In a preferred embodiment of the present invention, the piston body has a central axis, and the flow channel and the bypass channel extend at an angle to the central axis.

[0015] The shock absorber with adjustable damping force of this invention has other features and advantages that will be apparent from or will be set forth in detail in the accompanying drawings and subsequent embodiments incorporated herein, which together serve to explain the particular principles of this invention. Attached Figure Description

[0016] Figure 1 This is a cross-sectional schematic diagram of the vibration damper according to the present invention; Figure 2 An exploded perspective view of the piston according to this utility model; Figure 3 This is an exploded side view of the piston according to the present invention; Figure 4 This is a cross-sectional view of the piston according to the present invention; Figure 5 This shows the damping fluid passing through the piston when the damper is in the compression phase; Figure 6 This illustrates the action of damping fluid passing through the piston during the rebound phase of the shock absorber. Detailed Implementation

[0017] The present invention will now be described in detail with reference to various embodiments, examples of which are presented in the accompanying drawings and described below. Although the present invention will be described in conjunction with exemplary embodiments, it should be understood that this specification is not intended to limit the present invention to these exemplary embodiments. Rather, the present invention is intended to cover not only these exemplary embodiments, but also various alternatives, modifications, equivalents and other embodiments that may be included within the spirit of the present invention and the scope defined by the appended claims.

[0018] In the following description of this utility model, it should be noted that, unless otherwise stated, the term "multiple" refers to two or more; the terms "upper," "lower," "inner," "outer," "top," "bottom," etc., indicating orientation or positional relationships are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on this utility model. The directional terms appearing in the following description refer to the directions shown in the figures and are not intended to limit the specific structure of this utility model.

[0019] In the description of this utility model, it should also be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0020] To better understand this utility model, the following is in conjunction with... Figures 1 to 6A vibration damper with adjustable damping force according to an embodiment of the present invention will be described in detail.

[0021] Figure 1 A cross-sectional schematic diagram and a schematic diagram of a shock absorber 10 with adjustable damping force are shown. The shock absorber 10 includes an inner tube 11 at least partially filled with a damping fluid, which can be a liquid, particularly hydraulic oil, or a gas, particularly a gas mixture. An axially reciprocating piston rod 12 and a piston 13 connected to and moving with the piston rod 12 are disposed within the inner tube 11. The interior of the inner tube 11 is divided by the piston 13 into a first working chamber C1 on the piston rod 12 side and a second working chamber C2 away from the piston rod 12. The direction of movement of the piston 13 can be defined as the longitudinal direction of the shock absorber 10, i.e., the axial direction. The upper end of the inner tube 11 is closed by means of a piston rod guide 14, and the lower end of the inner tube 11 is closed by means of a cap 15.

[0022] The intermediate tube 16 is coaxially arranged around the inner tube 11, so that a first annular cavity C3 is formed between the inner tube 11 and the intermediate tube 16. An opening 110 is formed in the wall of the inner tube 11, through which the damping fluid can overflow from the inner tube 11 into the first annular cavity C3.

[0023] The inner tube 11 and the intermediate tube 16 are together surrounded and wrapped by the outer tube 17, so that a second annular cavity C4 is formed between the outer tube 17 and the inner tube 11 or the intermediate tube 16.

[0024] The damper 10 may also have two separately adjustable damping valves, a first damping valve 18 and a second damping valve 19. For each of the piston 13's extension and retraction movements, the first damping valve 18 and the second damping valve 19 are effectively connected to a first working chamber C1 on the piston rod 12 side and a second working chamber C2 away from the piston rod 12. The first damping valve 18 and the second damping valve 19 are located radially outward from the outer tube 17. The first damping valve 18 is fluidly connected to the first working chamber C1 on the piston rod 12 side, and the second damping valve 19 is fluidly connected to the second working chamber C2 away from the piston rod 12.

[0025] When the damper 10 is in the rebound stage, the piston rod 12 and piston 13 move out. The damping fluid is transported from the first working chamber C1 on the piston rod 12 side through the opening 110 and the first annular chamber C3 to the corresponding first damping valve 18, and then transported to the external second annular chamber C4 through the outlet side of the first damping valve 18. Then the damping fluid flows from the second annular chamber C4 through the inlet side of the second damping valve 19 and enters the second working chamber C2 away from the piston rod 12. When the damper 10 is in the compression stage, the piston rod 12 or piston 13 retracts. The damping fluid is directly transported from the second working chamber C2 away from the piston rod 12 to the corresponding second damping valve 19, and then transported to the external second annular chamber C4 via the outlet side of the second damping valve 19. Then, the damping fluid flows from the second annular chamber C4 through the inlet side of the first damping valve 18 and enters the first annular chamber C3. Subsequently, it enters the first working chamber C1 on the piston rod 12 side through the opening 110.

[0026] Therefore, the first damping valve 18 and the second damping valve 19 can make the first working chamber C1 on the piston rod 12 side and the second working chamber C2 away from the piston rod 12 fluidly connected to each other, so as to dampen the outward or retracted movement of the piston rod 12 or the piston 13 during the compression or rebound phase of the damper 10.

[0027] Figure 2 and Figure 3 An exploded perspective view and an exploded side view of the piston according to the present invention are shown. Figures 4 to 6 A cross-sectional view of the piston according to the present invention is shown, wherein Figure 5 This illustrates the situation when the damping fluid passes through piston 13 during the compression phase of the shock absorber. Figure 6 This shows the damping fluid passing through piston 13 when the damper is in the rebound phase.

[0028] like Figures 2 to 6As shown, the piston 13 includes a body 131, which is generally cylindrical and has a central through-hole. The piston rod 12 is sealed and inserted into the central through-hole. The body 131 contains independent flow channels 132 and bypass channels 133. The flow channels 132 and bypass channels 133 extend axially through the body 131 of the piston 13, allowing the two working chambers C1 and C2 to communicate with each other. The number of each of the flow channels 132 and bypass channels 133 can be one or more. The term "independent" here means that the fluids passing through the flow channels 132 and bypass channels 133 do not affect each other; that is, the damping fluids passing through the flow channels 132 and bypass channels 133 do not merge within the body 131 of the piston 13. This design of damping flow channels inside the piston 13 allows for modular damping design, facilitating assembly and maintenance, thereby reducing costs.

[0029] Piston 13 also includes a check valve 20, which is disposed in the flow passage 132 and located on the side of the body 131 near the first working chamber C1. The check valve 20 is configured to allow only unidirectional flow of damping fluid between the two working chambers C1 and C2. Specifically, during the compression phase, the check valve 20 allows damping fluid to flow from the second working chamber C2, which is away from piston rod 12, to the first working chamber C1 on the piston rod 12 side (e.g., ...). Figure 5 (As shown by the upward arrow on the left), but during the rebound phase, the flow channel 132 is blocked, thereby preventing the damping fluid from flowing from the first working chamber C1 on the piston rod 12 side to the second working chamber C2 away from the piston rod 12 (as ...). Figure 6 (As shown by the short downward arrow on the left). The bypass channel 133 is configured to allow fluid connection between the two working chambers C1 and C2 at all times, whether in the compression or rebound phase. Specifically, in the compression phase, the bypass channel 133 is configured to allow damping fluid to flow from the second working chamber C2, which is farther from the piston rod 12, to the first working chamber C1 on the piston rod 12 side (as shown by the short downward arrow on the left). Figure 5 (As shown by the upward arrow on the right), and during the rebound phase, the bypass channel 133 is configured to allow damping fluid to flow from the first working chamber C1 on the piston rod 12 side to the second working chamber C2 away from the piston rod 12 (as shown by the upward arrow on the right), and during the rebound phase, the bypass channel 133 is configured to allow damping fluid to flow from the first working chamber C1 on the piston rod 12 side to the second working chamber C2 away from the piston rod 12 ( Figure 6 (As shown by the downward arrow on the right).

[0030] Therefore, in the compression stage, such as Figure 5 As shown, the damping fluid in the second working chamber C2, away from the piston rod 12, flows not only through the flow channel 132 but also through the bypass channel 133 to the first working chamber C1 on the piston rod 12 side. Through the synergistic effect of the two channels, a smaller damping force can be achieved, which helps to gently absorb road impacts, reduce the impact transmitted to the vehicle body, and improve ride comfort. During the rebound phase, as... Figure 6As shown, the fluid in the first working chamber C1 on the piston rod 12 side flows only through the bypass channel 133 to the second working chamber C2 away from the piston rod 12. As a result, the damping force applied by the damping fluid to the piston 13 is relatively large, which helps to control the rapid rebound of the suspension, improve the adhesion between the tire and the ground, and enhance the handling stability of the vehicle.

[0031] Therefore, by forming independent flow channels 132 and bypass channels 133 in the piston 13 and providing a check valve 20 at the flow channel 132, this utility model can provide different fluid bypasses in the compression and rebound stages, thereby providing different damping forces in different stages of the shock absorber and thus improving the damping characteristics of the shock absorber.

[0032] like Figures 4 to 6 As shown, the check valve 20 includes a valve disc 21 and a spring member 22. The valve disc 21 is disposed between the spring member 22 and the body 131, so that the valve disc 21 abuts against the body 131 under the preload of the spring member 22. The spring member 22 abuts against the side of the valve disc 21 closest to the first working chamber C1. When the check valve 20 is in the closed state, the valve disc 21, under the preload generated by the spring member 22, seals against the circumferential edge of the flow channel 132, thereby preventing damped fluid from passing through the flow channel 132. Figure 5 As shown, during the compression phase of the damper, when the fluid pressure flowing towards the first working chamber C1 on the piston rod 12 side is greater than the preload generated by the spring member 22, the valve disc 21 is pushed open by the damping fluid and moves away from the circumferential edge of the flow channel 132. This allows the damping fluid to enter the first working chamber C1 on the piston rod 12 side from the second working chamber C2 away from the piston rod 12 through the flow channel 132. During this process, the check valve 20 is in the open state. Simultaneously, the damping fluid in the second working chamber C2 also enters the first working chamber C1 on the piston rod 12 side through the bypass channel 133 via the notch 42 of the second bypass disc 41 in the second damping disc assembly 40 located near the second working chamber C2 (described later). Thus, during the compression phase of the damper, as the piston rod 12 and piston 13 compress, the damping fluid can simultaneously flow from the second working chamber C2 to the first working chamber C1 through the flow channel 132 and the bypass channel 133.

[0033] The spring element 22 can introduce its preload into the valve disc 21 radially inward, radially outward, and / or radially centered. In other words, the spring element 22 can introduce preload into the valve disc 21 by abutting against the valve disc 21 through a spring end in a radially inner surface region, a radially outer surface region, or a radially central surface region. The spring element 22 preferably comprises a truncated conical spring, a cylindrical spring, a cylindrical spring, and / or a leaf spring. Other spring types are also possible. Furthermore, the spring element 22 can preferably be in the form of a compression spring or alternatively a tension spring.

[0034] Valve disc 21 is preferably annular, and particularly circular. When check valve 20 is closed, valve disc 21 is in an undeformed state and is flat. When check valve 20 is open, valve disc 21 is deformed and conical; however, it should be understood that other shapes are also possible.

[0035] from Figures 4-6 As can be seen, the piston 13's body 131 has a base 134. This base 134 is preferably an annular recess in the body 131 and advantageously forms a space for receiving functional elements (e.g., spring 22, valve disc 21, and first damping disc assembly 23, etc.), such that the valve disc 21 and spring 22 are arranged within the base 134. By accommodating these functional elements within the base 134, a compact structure can be achieved. A flow channel 132 is in fluid communication with the base 134.

[0036] The base 134 has a bottom surface 1341, on which two rib-shaped rings 134a and 134b are coaxially arranged, protruding axially from the bottom surface 1341 toward the valve disc 21. A flow channel 132 is formed between the two rib-shaped rings 134a and 134b and extends axially through the body 131. Under the preload of the spring member 22, the valve disc 21 abuts against the two rib-shaped rings 134a and 134b, thereby causing the check valve 20 to be in a closed state and blocking the flow channel 132. During the compression phase, when the fluid pressure in the first working chamber C1 on the piston rod 12 side is greater than the preload generated by the spring 22, the valve disc 21 will move away from at least one of the two rib rings 134a and 134b in the opposite direction of the preload of the spring 22. This causes the check valve 20 to be in the open state, allowing damping fluid to enter the first working chamber C1 on the piston rod 12 side from the second working chamber C2 away from the piston rod 12 through the flow channel 132. Therefore, the two rib rings 134a and 134b are used as the two control edges of the valve disc 21. By abutting the valve disc 21 against the control edges of the rib rings 134a and 134b protruding from the bottom surface 1341, the contact surface between the valve disc 21 and the bottom surface of the base 134 can be reduced, thereby reducing the switching noise when the check valve 20 is opened or closed.

[0037] The check valve 20 also includes first damping disc assemblies 23 stacked on top of each other. The first damping disc assemblies 23 abut against the spring member 22 on the side of the spring member 22 away from the valve disc 21, forming a reverse support for the spring member 22, thereby providing different spring preload forces. The number of first damping disc assemblies 23 can be set according to the required spring preload force of the check valve 20. The first damping disc assemblies 23 are annular, with some arranged in the base 134 and others arranged on the outer side of the base 134. However, the invention is not limited to this; all the first damping disc assemblies 23 can be arranged in the base 134. A more compact design can be achieved by integrating at least partially the first damping disc assemblies 23 into the base 134.

[0038] like Figure 2 As shown, the first damping disc assembly 23 disposed on the outer side of the base 134 includes a first bypass disc 231, which abuts against the circumferential edge of the base 134 and forms an opening 232 for the damping fluid to flow through the flow channel 132. Figure 2 As shown, the first bypass disc 231 has a plurality of spaced openings 232 in the circumferential direction. These openings 232 are preferably radially inward recesses from the outer peripheral surface of the first damping disc assembly 23. During the compression phase, these openings 232 communicate with the flow channel 132, thereby allowing damping fluid to flow from the second working chamber C2 away from the piston rod 12 to the first working chamber C1 on the piston rod 12 side. It is understood that the first damping disc assembly 23 does not block the bypass channel 133, i.e., it is not fluid-associated with the bypass channel 133, thereby allowing fluid communication between the two working chambers C1 and C2 in both the compression and rebound phases.

[0039] In addition, such as Figures 2 to 6 As shown, the piston 13 also includes a second damping disk assembly 40, which is stacked on top of each other on the side of the piston 13 body 131 near the second working chamber C2 to ensure the structural stability of the piston 13 and to provide adjustable damping characteristics for the piston 13.

[0040] Preferably, such as Figure 2 As shown, the second damping disc assembly 40 includes a second bypass disc 41. The second bypass disc 41 has a notch 42 that allows damping fluid to flow through a bypass channel 133, the notch 42 being fluidly associated with the bypass channel 133 throughout the compression and rebound phases. Preferably, the second bypass disc 41 is annular, and the notch 42 is formed radially outward of the second bypass disc 41. Preferably, the notch 42 is a recess radially inward from the outer peripheral surface of the second bypass disc 41. Figure 2Only one notch 42 is shown, corresponding to a bypass passage 133 provided in the piston body 131, but multiple bypass passages 133 and multiple notches 42 are also possible. It is understood that the second bypass disc 41 does not cover the flow passage 132, i.e., it is not fluid-associated with the flow passage 132.

[0041] In some embodiments, such as Figures 4 to 6 As shown, the piston 13's body 131 has a central axis M, and a flow channel 132 and a bypass channel 133 extend at an angle to the central axis M. Preferably, at least one of the flow channel 132 and the bypass channel 133 has a segmented design, with each segment forming a different angle with the central axis M and having a different orifice diameter in the axial direction. This design can increase the flow resistance of the damping fluid as it flows through the channels 132 and 133, thereby increasing the damping force exerted on the piston 13 by the damping fluid as it passes through the channels 132 and 133.

[0042] In addition, such as Figures 4 to 6 As shown, the flow channel 132 and the bypass channel 133 have a curved, meandering shape in the axial direction of the piston 13. It is conceivable that the flow channel 132 and the bypass channel 133 could also have a curved, meandering shape in the circumferential direction of the piston 13. This design not only reduces the weight of the entire piston body 131, but also increases the vortex effect of the damping fluid in channels 132 and 133, thereby increasing the damping force exerted on the piston 13 by the damping fluid as it passes through channels 132 and 133.

[0043] The description of the exemplary embodiments presented above is only for illustrating the technical solutions of this utility model and is not intended to be exhaustive or to limit the utility model to the precise forms described. Obviously, those skilled in the art can make many changes and variations based on the above teachings. The exemplary embodiments were chosen and described to explain the specific principles of this utility model and its practical applications, thereby enabling other those skilled in the art to understand, implement, and utilize the various exemplary embodiments of this utility model and their various alternatives and modifications. The scope of protection of this utility model is intended to be defined by the appended claims and their equivalents.

[0044] List of reference numerals 10 shock absorbers 11 Inner Tube 12 piston rods 13 Pistons 131 body 132 flow channels 133 Bypass 134 base 134a and 134b rib rings 14 Piston Rod Guide 15 caps 16 intermediate tube 17 outer tube 18 First damping valve 19 Second damping valve 20 Check Valve 21 Valve Disc 22 spring parts 23 First damping disc assembly 231 First Bypass 232 opening 40 Second Damping Disc Assembly 41 Second Bypass Disc 42 gaps.

Claims

1. A vibration damper (10) with adjustable damping force, the vibration damper (10) comprising: The inner tube (11) is at least partially filled with damping fluid; The piston rod (12) is disposed in the inner tube (11) in a manner that allows for axial reciprocating movement; A piston (13) is connected to the piston rod (12) in the inner tube (11) and is able to reciprocate together with the piston rod (12). The piston (13) divides the interior of the inner tube (11) into two working chambers (C1, C2). The two working chambers (C1, C2) include a first working chamber (C1) on the side of the piston rod (12) and a second working chamber (C2) away from the piston rod (12). Its features are, The piston (13) includes a body (131) and a check valve (20). The body (131) has an independent flow channel (132) and a bypass channel (133). The check valve (20) is located in the flow channel (132) and is located on the side of the body (131) near the first working chamber (C1). The check valve (20) is configured to block the fluid connection between the first working chamber (C1) and the second working chamber (C2) via the flow channel (132) during the rebound phase, and to allow the fluid connection between the first working chamber (C1) and the second working chamber (C2) via the flow channel (132) during the compression phase, and to allow the fluid connection between the first working chamber (C1) and the second working chamber (C2) via the bypass channel (133) during both the compression phase and the rebound phase.

2. The vibration damper (10) with adjustable damping force according to claim 1, characterized in that, The check valve (20) includes a valve disc (21) and a spring (22). The valve disc (21) is disposed between the spring (22) and the body (131) so that the valve disc (21) abuts against the body (131) under the preload of the spring (22).

3. The vibration damper (10) with adjustable damping force according to claim 2, characterized in that, The piston (13) has a base (134) on its body (131), the valve disc (21) and the spring (22) are arranged in the base (134), and the flow channel (132) is in fluid communication with the base (134).

4. The vibration damper (10) with adjustable damping force according to claim 3, characterized in that, The base (134) has a bottom surface (1341) on which two rib rings (134a, 134b) protruding from the bottom surface (1341) along the axial direction toward the valve disc (21) are coaxially arranged. The flow channel (132) is formed between the two rib rings (134a, 134b) and passes through the body (131) along the axial direction. The valve disc (21) abuts against the two rib rings (134a, 134b) under the action of the preload generated by the spring (22).

5. The damper (10) with adjustable damping force according to claim 3, characterized in that The check valve (20) includes: A first damping disc assembly (23) is disposed on the side of the spring (22) away from the valve disc (21) to form a reverse support for the spring (22), and at least a portion of the first damping disc assembly (23) is disposed in the base (134).

6. The vibration damper (10) with adjustable damping force according to claim 5, characterized in that, The first damping disc assembly (23) includes a first bypass disc (231) abutting against the circumferential edge of the base (134) and having an opening (232) that allows the damping fluid to flow through the flow channel (132).

7. The shock absorber (10) with adjustable damping force according to claim 5, characterized in that The piston (13) comprises: The second damping disc assembly (40) is disposed on the side of the body (131) near the second working cavity (C2).

8. The vibration damper (10) with adjustable damping force according to claim 7, characterized in that, The second damping disc assembly (40) includes a second bypass disc (41) having a notch (42) for allowing the damping fluid to flow through the bypass channel (133).

9. The vibration damper (10) with adjustable damping force according to claim 8, characterized in that, The second bypass disc (41) is annular, and the notch (42) is radially recessed from the outer peripheral surface of the second bypass disc (41).

10. The vibration damper (10) with adjustable damping force according to any one of claims 1 to 9, characterized in that, The piston (13) has a body (131) with a central axis (M), and the flow channel (132) and the bypass channel (133) extend at an angle to the central axis.

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