Shock absorber and vehicle

Abstract

A vehicle, comprising a shock absorber (1). The shock absorber comprises: a cylinder (100); a piston (200) movably arranged in the cylinder, the piston dividing the interior of the cylinder into a compression cavity (111) and a recovery cavity (112); a flow regulating valve (300) arranged in the piston, the flow regulating valve being separately communicated with the compression cavity and the recovery cavity; and a control valve (400) arranged in the piston, the control valve regulating the flow of fluid between the compression cavity and the recovery cavity by controlling the flow regulating valve. The shock absorber can continuously regulate damping force by regulating the flow of fluid between the compression cavity and the recovery cavity, so that riding comfort and the handling performance of the vehicle are improved.

Description

Shock absorber and vehicle

[0001] Cross-reference to related applications

[0002] This application claims priority to Chinese Patent Application No. 202422966752.5, filed on November 30, 2024, entitled “Pilot Valve for Shock Absorber, Shock Absorber and Vehicle,” Chinese Patent Application No. 202422954075.5, filed on November 30, 2024, entitled “Flow Regulating Valve for Shock Absorber, Shock Absorber and Vehicle,” Chinese Patent Application No. 202411762611.X, filed on September 30, 2024, entitled “Pilot Valve for Shock Absorber, Shock Absorber and Vehicle,” Chinese Patent Application No. 202411754914.7, filed on September 30, 2024, entitled “Overflow Valve Seat, Flow Regulating Valve for Shock Absorber, Shock Absorber and Vehicle,” Chinese Patent Application No. 202411759761.5, filed on September 30, 2024, entitled “Valve Spool Assembly for Shock Absorber, Shock Absorber and Vehicle,” Chinese Patent Application No. 202422970005.9, filed on November 30, 2024, entitled “Flow Regulating Valve for Shock Absorber, Shock Absorber and Vehicle,” Chinese Patent Application No. 202411768009.7, filed on September 30, 2024, entitled “Shock Absorber and Vehicle,” Chinese Patent Application No. 202411754883.5, filed on September 30, 2024, entitled “Flow Regulating Valve for Shock Absorber, Shock Absorber and Vehicle,” Chinese Patent Application No. 202411768046.8, filed on September 30, 2024, entitled “Overflow Valve Disc, Flow Regulating Valve for Shock Absorber, Shock Absorber and Vehicle,” and Chinese Patent Application No. 202411402669.3, filed on September 30, 2024, entitled “Shock Absorber and Vehicle,” all of which are incorporated by reference in their entirety. TECHNICAL FIELD

[0003] The present application relates to the technical field of vehicles, and in particular to a shock absorber and a vehicle. BACKGROUND

[0004] The vehicle in the related art is usually provided with a shock absorber in the wheel area to reduce the bumping of the vehicle during driving on uneven road surfaces by using the shock absorber, and when the vehicle body and the wheel move relatively, the piston in the shock absorber can move up and down to repeatedly flow the fluid in the shock absorber from one of the rebound chamber and the compression chamber into the other, and convert the vibration energy into heat energy of the fluid and gas dissipated to the atmosphere. However, the shock absorber in the related art has many parts and a complex structure, and it is not easy to adjust the damping force of the shock absorber.

[0005] SUMMARY

[0006] The present application aims to at least solve one of the technical problems existing in the prior art. To this end, one object of the present application is to provide a shock absorber capable of continuously adjusting damping force by adjusting fluid flow between compression chamber and recovery chamber, which is beneficial to improve ride comfort and handling performance of a vehicle, and the structure of the shock absorber is simple and easy to adjust.

[0007] The present application also provides a vehicle with the above shock absorber.

[0008] To achieve the above object, according to the first aspect of the present application, a shock absorber is provided, comprising: a cylinder; a piston movably arranged in the cylinder, and the piston separates a compression chamber and a recovery chamber in the cylinder; a flow regulating valve arranged in the piston and respectively communicating with the compression chamber and the recovery chamber; a control valve arranged in the piston, the control valve adjusts the fluid flow between the compression chamber and the recovery chamber by controlling the flow regulating valve.

[0009] The shock absorber according to the embodiments of the present application can continuously adjust the damping force by adjusting the fluid flow between the compression chamber and the recovery chamber, which is beneficial to improve the ride comfort and handling performance of the vehicle, and the structure of the shock absorber is simple and easy to adjust.

[0010] According to some embodiments of the present application, the flow regulating valve comprises: a relief valve body movably mounted in the piston; a relief valve seat mounted in the piston and located on the side of the relief valve body away from the control valve, the relief valve seat is provided with a first flow channel, the first flow channel communicates with the compression chamber; a relief valve plate movably arranged between the relief valve body and the relief valve seat, a second flow channel is formed between the relief valve plate and the relief valve body, and a third flow channel is formed between the relief valve plate and the relief valve seat, the second flow channel and the third flow channel respectively communicate with the first flow channel and the recovery chamber; wherein the second flow channel and / or the third flow channel are opened and closed by the movement of the relief valve body.

[0011] According to some embodiments of the present application, the relief valve plate is configured with a relief passage, and when the relief valve seat and the relief valve body respectively abut against the relief valve plate, the relief passage respectively communicates with the first flow channel and the recovery chamber of the shock absorber.

[0012] According to some embodiments of the present application, the relief passage is configured as a plurality of relief passages, and the plurality of relief passages are arranged in a circumferential direction of the relief valve plate.

[0013] According to some embodiments of the present application, the relief valve body is movably arranged on one side of the relief valve seat.

[0014] According to some embodiments of the present application, the overflow valve plate is configured with at least one communication hole, and the second flow channel communicates with the first flow channel through the communication hole.

[0015] According to some embodiments of the present application, one of the overflow valve body and the overflow valve seat is provided with a support column extending along the axial direction of the cylinder body, and the overflow valve plate is movably sleeved on the support column to move along the axial direction of the cylinder body under the guidance of the support column.

[0016] According to some embodiments of the present application, the cross-sectional area of the free end of the support column decreases towards the overflow valve body.

[0017] According to some embodiments of the present application, the cross-sectional area of the free end of the support column decreases towards the overflow valve seat.

[0018] According to some embodiments of the present application, the overflow valve body is provided with the support column, and the cross-sectional area of the free end of the support column decreases towards the overflow valve seat; or

[0019] The overflow valve seat is provided with the support column, and the cross-sectional area of the free end of the support column decreases towards the overflow valve body.

[0020] According to some embodiments of the present application, the overflow valve body is provided with the support column, one end of the support column towards the overflow valve seat is configured as a guide section, and the cross-sectional area of the guide section decreases along the axial direction of the support column towards the overflow valve seat; or,

[0021] According to some embodiments of the present application, the overflow valve seat is provided with the support column, one end of the support column towards the overflow valve body is configured as a guide section, and the cross-sectional area of the guide section decreases along the axial direction of the support column towards the overflow valve body.

[0022] According to some embodiments of the present application, the overflow valve body is provided with the support column, and the gap between the overflow valve plate and the guide section increases along the axial direction of the support column towards the overflow valve seat; or,

[0023] The overflow valve seat is provided with the support column, and the gap between the overflow valve plate and the guide section increases along the axial direction of the support column towards the overflow valve body.

[0024] According to some embodiments of the present application, the overflow valve seat comprises: a first seat body, the first seat body and the overflow valve plate form the third flow channel therebetween; a second seat body supported on the side of the first seat body away from the overflow valve plate and connected with the piston, the second seat body and the first seat body jointly define the first flow channel.

[0025] According to some embodiments of the present application, the overflow valve piece is arranged between the first seat body and the overflow valve body; wherein one of the first seat body and the second seat body is configured to form the support column.

[0026] According to some embodiments of the present application, the first seat body and the second seat body jointly define a first flow channel, which is adapted to communicate with a compression chamber of the shock absorber.

[0027] According to some embodiments of the present application, the first seat body is configured with a through hole, the second seat body is configured with at least one flow channel hole, and the second seat body is configured to form the support column, which extends into the through hole.

[0028] The through hole and the flow channel hole constitute the first flow channel.

[0029] According to some embodiments of the present application, the overflow valve piece comprises: a main body portion arranged between the overflow valve body and the overflow valve seat; a guide portion connected to the main body portion and protruding from at least one side of the main body portion in the axial direction of the cylinder body, the guide portion and the main body portion jointly defining a guide hole, and the support column being arranged in the guide hole.

[0030] According to some embodiments of the present application, the guide portion is provided with a first fillet surface extending along the circumference of the guide hole, and the side of the guide portion away from the main body portion and the inner side wall of the guide hole are arc transitioned by the first fillet surface.

[0031] According to some embodiments of the present application, the main body portion is provided with a second fillet surface extending along the circumference of the guide hole, and the side of the main body portion away from the guide portion and the inner side wall of the guide hole are arc transitioned by the second fillet surface.

[0032] According to some embodiments of the present application, the guide portion is connected to the main body portion and protrudes from at least one side of the main body portion in the thickness direction, and the overflow valve piece is adapted to be movably sleeved on the support column through the guide hole.

[0033] According to some embodiments of the present application, in the axial direction of the overflow valve piece, the length of the guide portion is L, and the thickness of the main body portion is W;

[0034] L and W satisfy L>2D; and / or

[0035] The support column is in clearance fit with the guide hole, and the distance between the outer peripheral surface of the support column and the inner side wall of the guide hole is D, D satisfies 0.02mm≤D≤0.15mm.

[0036] According to some embodiments of the present application, the guide portion is arranged on one side of the thickness direction of the main body portion; or

[0037] The guide portions are multiple, and the multiple guide portions include a first guide portion and a second guide portion, the first guide portion is arranged on one side of the thickness direction of the main body portion, and the second guide portion is arranged on the other side of the thickness direction of the main body portion.

[0038] According to some embodiments of the present application, the first guide portion is provided with a third fillet surface, the third fillet surface extends along the circumferential direction of the guide hole, and the side of the first guide portion away from the main body portion and the inner side wall of the guide hole are arc transitioned through the third fillet surface; and / or,

[0039] The second guide portion is provided with a fourth fillet surface, the fourth fillet surface extends along the circumferential direction of the guide hole, and the side of the second guide portion away from the main body portion and the inner side wall of the guide hole are arc transitioned through the fourth fillet surface.

[0040] According to some embodiments of the present application, the flow regulating valve further comprises a magnetic attraction member, the magnetic attraction member is arranged on the side of the overflow valve seat facing the overflow valve piece, and the magnetic attraction member generates a magnetic attraction force attracting the overflow valve piece.

[0041] According to some embodiments of the present application, the overflow valve seat is configured with at least one flow channel hole, the magnetic attraction member (350) is adjacent to the flow channel hole, and the flow channel hole is configured as an arc-shaped flow channel hole extending around the magnetic attraction member.

[0042] According to some embodiments of the present application, the flow regulating valve further comprises a limiting member, the limiting member is arranged on the support column and located on the side of the magnetic attraction member adjacent to the overflow valve piece, so as to limit the magnetic attraction member and the overflow valve piece;

[0043] Wherein, the support column is formed with a clamping groove, and the limiting member is clamped in the clamping groove.

[0044] According to some embodiments of the present application, the flow regulating valve further comprises a magnetic force adjusting member, the magnetic force adjusting member is arranged on the side of the magnetic attraction member facing the overflow valve piece, and the magnetic force adjusting member is used to adjust the magnetic attraction force of the magnetic attraction member to the overflow valve piece.

[0045] According to some embodiments of the present application, the magnetic force adjusting member comprises at least one magnetic force adjusting piece, the at least one magnetic force adjusting piece is arranged in layers, and the magnetic force adjusting piece adjusts the magnetic attraction force of the magnetic attraction piece to the overflow valve piece by adjusting the number of the magnetic force adjusting pieces, and an adsorption gap is formed between two adjacent magnetic force adjusting pieces; and / or the magnetic force adjusting member comprises a magnetic force adjusting block, the magnetic force adjusting block adjusts the magnetic attraction force of the magnetic attraction piece to the overflow valve piece by adjusting the height of the magnetic force adjusting block along the axial direction of the cylinder, and the magnetic force adjusting block is provided with an adsorption hole.

[0046] According to some embodiments of the present application, the flow regulating valve further comprises at least one magnetic force adjusting piece, the at least one magnetic force adjusting piece is arranged on the side of the magnetic attraction piece facing the overflow valve piece, and the magnetic force adjusting piece adjusts the magnetic attraction force of the magnetic attraction piece to the overflow valve piece by adjusting the number of the magnetic force adjusting pieces.

[0047] According to some embodiments of the present application, the side of the overflow valve body facing the overflow valve piece is provided with a first abutting ring platform, the side of the overflow valve seat facing the overflow valve piece is provided with a second abutting ring platform, and the inner diameter of the first abutting ring platform is smaller than the inner diameter of the second abutting ring platform.

[0048] According to some embodiments of the present application, the second abutting ring platform is arranged on the side of the overflow valve seat facing the overflow valve body.

[0049] According to some embodiments of the present application, the first abutting ring platform and the second abutting ring platform are arranged staggered in the radial direction of the flow regulating valve.

[0050] Among them, at least part of the overflow channel is located between the first abutting ring platform and the second abutting ring platform in the radial direction of the overflow valve piece.

[0051] According to some embodiments of the present application, at least part of the overflow channel is located between the outer circumferential surface of the first abutting ring platform and the inner circumferential surface of the second abutting ring platform.

[0052] According to some embodiments of the present application, the end of the overflow valve body away from the overflow valve seat is provided with a sealing sink, the valve body is provided with a sealing ring platform, and the sealing ring platform is arranged spaced apart from the inner side wall of the valve body in the radial direction of the cylinder, the overflow valve body and the inner side wall of the valve body are in dynamic sealing cooperation, and the sealing sink and the outer side wall of the sealing ring platform are in dynamic sealing cooperation; wherein the inner diameter of the sealing sink is smaller than the inner diameter of the second abutting ring platform.

[0053] According to some embodiments of the present application, the inner cross-sectional area of the second abutting ring platform is S1, the inner cross-sectional area of the sealing sink is S2, and S1 and S2 satisfy: S2≤S1≤1.3×S2.

[0054] According to some embodiments of the present application, the outer diameter of the first abutting ring platform is smaller than the inner diameter of the second abutting ring platform.

[0055] According to some embodiments of the present application, a side surface of the overflow valve plate facing the overflow valve body is configured with a valve body abutting surface and a valve body pressure bearing surface, the valve body abutting surface is adapted to abut against the first abutting ring platform, and the valve body pressure bearing surface is formed between the valve body abutting surface and the outer periphery of the overflow valve plate.

[0056] According to some embodiments of the present application, the overflow valve plate is configured with at least one overflow hole, and along the radial direction of the overflow valve plate, the overflow hole is located between the outer peripheral surface of the first abutting ring platform and the inner peripheral surface of the second abutting ring platform, and the overflow hole is respectively communicated with the compression cavity and the recovery cavity when the flow regulating valve is in the closed valve state.

[0057] According to some embodiments of the present application, at least one of the side of the overflow valve body facing the overflow valve plate, the side of the overflow valve seat facing the overflow valve plate and the overflow valve plate is configured with an overflow notch, and the overflow notch is respectively communicated with the compression cavity and the recovery cavity.

[0058] According to some embodiments of the present application, one of the overflow valve body and the overflow valve seat is provided with a support column, and the other of the overflow valve body and the overflow valve seat is provided with a first elastic member between the support column.

[0059] According to some embodiments of the present application, the overflow valve body is provided with the support column, and an end of the support column facing the overflow valve seat is configured with a support ring platform, and the first elastic member is abutted against the support ring platform; or, the overflow valve seat is provided with the support column, and an end of the support column facing the overflow valve body is configured with a support ring platform, and the first elastic member is abutted against the support ring platform.

[0060] According to some embodiments of the present application, the support ring platform comprises: a connecting section connected with the support column; and a transition section connected to an end of the connecting section away from the support column, and the outer diameter of the transition section is smaller than the outer diameter of the connecting section; wherein the first elastic member is in interference fit with the connecting section, and there is a gap between the first elastic member and the transition section.

[0061] According to some embodiments of the present application, a side of the overflow valve seat facing the overflow valve disc is provided with a second abutting ring platform and a flow guide surface, the second abutting ring platform abuts against the overflow valve disc, and the flow guide surface is located radially outward of the second abutting ring platform; wherein, along the radial direction of the overflow valve seat, the distance between any point of the flow guide surface and the radially outer side of the end of the second abutting ring platform facing the overflow valve disc is X; along the axial direction of the overflow valve seat, the distance between the any point of the flow guide surface and the radially outer side of the end of the second abutting ring platform facing the overflow valve disc is Y; X and Y satisfy: Y / X>0.5.

[0062] According to some embodiments of the present application, the flow guide surface is provided on a side of the overflow valve seat facing the overflow valve body, and the flow guide surface is located radially outward of the second abutting ring platform.

[0063] According to some embodiments of the present application, the flow guide surface comprises:

[0064] a first step surface connected to the radially outer side of the second abutting ring platform and extending along the radial direction of the overflow valve seat, and the second abutting ring platform exceeds the first step surface in the direction close to the overflow valve body;

[0065] a second step surface connected to the radially outer side of the first step surface and extending along the radial direction of the overflow valve seat, and the first step surface exceeds the second step surface in the direction close to the overflow valve body; or

[0066] the flow guide surface comprises:

[0067] a third step surface connected to the radially outer side of the second abutting ring platform and extending along the radial direction of the overflow valve seat, and the second abutting ring platform exceeds the third step surface in the direction close to the overflow valve body;

[0068] a slope surface connected to the radially outer side of the third step surface and extending outward along the radial direction of the overflow valve seat, the slope surface gradually moves away from the overflow valve body; or

[0069] the flow guide surface comprises a slope surface connected to the radially outer side of the second abutting ring platform and extending outward along the radial direction of the overflow valve seat, the slope surface gradually moves away from the overflow valve body;

[0070] wherein, along the axial direction of the overflow valve seat close to the overflow valve body, the second abutting ring platform exceeds the end of the slope surface adjacent to the overflow valve body; or

[0071] The guide surface comprises a slope, which is connected to the radial outer side of the second abutting ring platform, and gradually moves away from the overflow valve body in the radial outward direction of the overflow valve seat;

[0072] Wherein, in the axial direction of the overflow valve seat, the end of the slope adjacent to the overflow valve body is flush with the end of the second abutting ring platform facing the overflow valve body.

[0073] According to some embodiments of the present application, in the axial direction of the overflow valve seat, the size B of the second abutting ring platform beyond the end of the guide surface adjacent to the overflow valve body satisfies: 0.4mm≤B≤0.6mm.

[0074] According to some embodiments of the present application, the included angle between the slope and the radial direction of the overflow valve seat is β, which satisfies: 35°≤β≤55°.

[0075] According to some embodiments of the present application, the radial thickness of the second abutting ring platform is ≤0.2mm in the radial direction of the overflow valve seat.

[0076] According to some embodiments of the present application, the radial thickness of the second abutting ring platform is >0.15mm in the radial direction of the overflow valve seat.

[0077] According to some embodiments of the present application, the piston comprises: a piston rod; a piston valve assembly, which separates the compression cavity and the recovery cavity in the cylinder; a valve body, through which the piston valve assembly and the piston rod are connected, and in which the overflow valve body and the overflow valve seat are installed, and the control valve extends into the valve body and cooperates with the flow regulating valve.

[0078] According to some embodiments of the present application, the overflow valve body is movably arranged in the valve body, and the overflow valve body and the valve body define a first chamber and a second chamber, and the control valve extends into the second chamber to control the opening and closing of the first chamber and the second chamber.

[0079] According to some embodiments of the present application, the end of the overflow valve body away from the overflow valve seat is provided with a sealing recess, the valve body is provided with a sealing ring platform, and in the radial direction of the cylinder, the sealing ring platform is arranged in a spaced manner with the inner side wall of the valve body, the overflow valve body and the inner side wall of the valve body are in dynamic sealing cooperation, and the sealing recess and the outer side wall of the sealing ring platform are in dynamic sealing cooperation; wherein, the inner side wall of the valve body, the outer side wall of the sealing ring platform and the overflow valve body define the first chamber, and the inner side wall of the sealing ring platform and the overflow valve body define the second chamber.

[0080] According to some embodiments of the present application, the side wall of the valve body is provided with a fourth flow channel and a fifth flow channel, the fourth flow channel is in communication with the first chamber and the recovery chamber respectively, one end of the fifth flow channel is in communication with the recovery chamber, and the other end of the fifth flow channel is in communication with the second flow channel and the third flow channel respectively; and the overflow valve body is configured with a sixth flow channel and a seventh flow channel, one end of the sixth flow channel is in communication with the first chamber, the other end of the sixth flow channel is in communication with the second chamber and the control valve is fitted to the other end of the sixth flow channel, one end of the seventh flow channel away from the overflow valve seat is in communication with the second chamber, and the other end of the seventh flow channel is in communication with the first flow channel, the fluid flow of the sixth flow channel and the fluid flow of the seventh flow channel are controlled by opening and closing of the control valve.

[0081] According to some embodiments of the present application, the valve body comprises: an upper valve body connected to the piston rod, the overflow valve body is movably arranged in the upper valve body, and the overflow valve body and the upper valve body define the first chamber and the second chamber; a lower valve body connected between the piston valve assembly and the upper valve body, and the overflow valve seat is arranged in the lower valve body; wherein the side wall of the upper valve body is provided with the fourth flow channel, and the side wall of the lower valve body is provided with the fifth flow channel.

[0082] According to some embodiments of the present application, the control valve comprises: a valve core assembly arranged in the piston; a pilot valve connected to the valve core assembly, and the valve core assembly controls the flow regulating valve through the pilot valve to adjust the fluid flow between the compression chamber and the recovery chamber.

[0083] According to some embodiments of the present application, the pilot valve comprises: a first body portion connected to the valve core assembly, and the first body portion is provided with at least one first balance hole and a sealing protrusion, the sealing protrusion is arranged on the side of the first body portion facing the flow regulating valve, and the sealing protrusion is fitted with the flow regulating valve; wherein the flow regulating valve comprises an overflow valve body movably mounted in the piston, and the overflow valve body is configured with a sixth flow channel and a seventh flow channel, the pilot valve is fitted to the sixth flow channel through the sealing protrusion to control the on-off of the sixth flow channel and the seventh flow channel.

[0084] According to some embodiments of the present application, along the axis of the pilot valve extending away from the body portion, the sealing protrusion is configured as a truncated cone with decreasing cross-sectional area.

[0085] According to some embodiments of the present application, the sixth flow channel is in communication with the recovery cavity, and the seventh flow channel is in communication with the compression cavity, and the sealing protrusion is fitted in the sixth flow channel to control the opening and closing of the sixth flow channel and the seventh flow channel.

[0086] According to some embodiments of the present application, the body part is further provided with a first balance hole penetrating through the body part along the axial direction of the pilot valve and along the radial direction of the body part, and the first balance hole is located between the first flow guide part and the sealing protrusion.

[0087] wherein the first balance hole is a plurality of first balance holes, and the plurality of first balance holes are arranged in a circumferential direction of the body part; and / or

[0088] The sealing protrusion protrudes from the first flow guide part along the axial direction of the pilot valve; and / or

[0089] A body flow guide surface is formed between the sealing protrusion and the first flow guide part on a side surface of the body part facing the flow regulating valve.

[0090] wherein the body flow guide surface is configured as a frustoconical surface with a decreasing cross-sectional area along the axial direction of the pilot valve extending away from the body part.

[0091] According to some embodiments of the present application, a projection of the first body part on the spool valve body along the axial direction of the cylinder covers at least a portion of the seventh flow channel.

[0092] According to some embodiments of the present application, the pilot valve further comprises a first flow guide part extending along the circumferential direction of the first body part, the first flow guide part extending from the outer periphery of the first body part towards the side of the flow regulating valve, and the first balance hole is located between the first flow guide part and the sealing protrusion.

[0093] According to some embodiments of the present application, the inner diameter of the sixth flow channel at the end facing the pilot valve is d1; the angle between the radial outer side of the sealing protrusion and the axial direction of the cylinder is ; and along the axial direction of the cylinder, the length of the first flow guide part exceeding the first body part in the direction close to the spool valve body is h, and the inner diameter of the first flow guide part is d2; wherein H, d1 and d2 satisfy: h.

[0094] According to some embodiments of the present application, the pilot valve comprises: a base connected to the spool assembly; a pilot valve plug disposed on a side of the base facing the flow regulating valve and movable relative to the base, and cooperating with the flow regulating valve; and a second elastic member disposed between the base and the pilot valve plug to provide an elastic force of the pilot valve plug away from the base.

[0095] According to some embodiments of the present application, the base further comprises an annular boss disposed on a side of the second body portion away from the second elastic member, the annular boss being formed with a guide rod connecting groove.

[0096] According to some embodiments of the present application, the guide rod connecting groove is disposed on a side of the body portion facing the spool assembly, and the spool assembly is connected to the guide rod connecting groove.

[0097] According to some embodiments of the present application, within a compression range of the second elastic member, the pilot valve plug is movable relative to the base along an axial direction of the base between a first position and a second position, and the second elastic member provides an elastic force of 10N-50N to the pilot valve plug.

[0098] According to some embodiments of the present application, the pilot valve plug comprises:

[0099] a plug piece, an edge of a side of the plug piece facing the second elastic member abutting against the second elastic member and a plug piece avoiding groove being formed on a radially inner side of the plug piece;

[0100] a plug head disposed in a middle of a side of the plug piece facing away from the second elastic member.

[0101] According to some embodiments of the present application, a bottom of the plug piece avoiding groove is a circular ring plane; or a bottom of the plug piece avoiding groove is a conical surface inclinedly approaching the second elastic member in a radial direction of the plug piece.

[0102] According to some embodiments of the present application, in an axial direction of the cylinder body, a distance between a radially outer side of the pilot valve plug and the base is smaller than a distance between a radially inner side of the pilot valve plug and the base.

[0103] According to some embodiments of the present application, the second elastic member comprises: an outer ring body abutting against the pilot valve plug; a plurality of inner elastic arms connected to an inner periphery of the outer ring body and disposed in a circumferential direction, and an inner end of each of the inner elastic arms abutting against the base.

[0104] According to some embodiments of the present application, the inner ends of the plurality of inner elastic arms are planar, and the inner ends of the plurality of inner elastic arms are circumscribed by the same circle.

[0105] According to some embodiments of the present application, the width of the inner elastic arm decreases in a direction radially inward along the outer ring body.

[0106] According to some embodiments of the present application, the base comprises a second body portion connected to the valve core assembly, and the second body portion is provided with at least one second balance hole; a second flow guide portion extending along the circumference of the second body portion, and the second flow guide portion extends from the outer periphery of the second body portion towards one side of the flow regulating valve.

[0107] According to some embodiments of the present application, the second flow guide portion is configured with a stop structure that stops on the side of the pilot valve plug away from the body portion.

[0108] According to some embodiments of the present application, the valve core assembly comprises a valve core movably provided in the iron core cover; a static iron core provided in the piston; a coil assembly installed in the piston, and when the coil assembly is energized, the valve core generates magnetism and is attracted to the static iron core; a guide rod provided through the valve core and connected with the valve core, and the pilot valve is connected to the end of the guide rod towards the flow regulating valve.

[0109] According to some embodiments of the present application, the guide rod is provided through the valve core and connected with the valve core.

[0110] According to some embodiments of the present application, the static iron core is provided on the side of the valve core towards the flow regulating valve, and the side of the static iron core towards the valve core is provided with a sink;

[0111] Wherein, when the flow regulating valve is in an open valve state at an initial position, along the axial direction of the valve core assembly, the side of the valve core towards the static iron core is located in the sink, and along the axial direction of the valve core assembly, the distance between the side of the valve core towards the static iron core and the bottom wall of the sink is L2, L2 satisfies: 2mm > L2 > 0.7mm.

[0112] According to some embodiments of the present application, the piston comprises a valve body; the control valve further comprises an iron core cover fixed in the piston; a magnetic isolation ring installed in the piston, the magnetic isolation ring is located between the iron core cover and the valve body and separates the coil assembly and the valve body.

[0113] According to some embodiments of the present application, the top of the core cover is provided with a mounting groove, and a second guide sleeve is arranged in the mounting groove, and the guide rod of the valve core assembly passes through the second guide sleeve.

[0114] According to some embodiments of the present application, the inner circumferential surface of the core cover is provided with a first step portion, and the outer circumferential surface of the valve core is provided with a second step portion, and the first step portion is stopped at the side of the second step portion facing the core cover.

[0115] According to some embodiments of the present application, the axial two ends of the valve core are provided with a first groove and a second groove, the third elastic member is arranged in the first groove and abuts between the groove bottom of the first groove and the core cover of the damper, and the fourth elastic member is arranged in the second groove and abuts between the groove bottom of the second groove and the static core.

[0116] According to some embodiments of the present application, the side of the static core facing the valve core is provided with a groove. When the flow regulating valve is in the closed valve state, along the axial direction of the cylinder body, the side of the valve core facing the pilot valve is located in the groove.

[0117] According to some embodiments of the present application, when the flow regulating valve is in the closed valve state, along the axial direction of the cylinder body, the distance between the side of the valve core facing the pilot valve and the groove opening of the groove is L1, L1 satisfies: 0.5mm>L1>0.1mm; and the distance between the side of the valve core facing the pilot valve and the bottom wall of the groove is L2, L2 satisfies: 2mm>L2>0.7mm.

[0118] According to some embodiments of the present application, when the flow regulating valve is in the open valve state at the initial position, along the axial direction of the valve core assembly, the distance between the side of the valve core facing the static core and the groove opening of the groove is L1, L1 satisfies: 0.5mm>L1>0.1mm.

[0119] According to some embodiments of the present application, the outer diameter of the valve core is D1, and the inner diameter of the groove is D2; wherein, when the valve core moves towards the static core, the distance between the inner side wall of the groove and the outer circumferential wall of the valve core is constant or gradually increases, so that (D2-D1)×(L1+L2) is constant or gradually increases.

[0120] According to some embodiments of the present application, the outer diameter of the valve core is D1, the inner diameter of the groove is D2, and the depth of the groove is L;

[0121] wherein, when the valve core moves towards the static core, the distance between the inner side wall of the groove and the outer circumferential wall of the valve core is constant, so that (D2-D1)×L is constant; or,

[0122] When the spool moves towards the static core, the distance between the inner side wall of the sink and the outer peripheral wall of the spool gradually increases, so that (D2-D1) x L gradually increases.

[0123] According to some embodiments of the present application, the spool is provided with an eighth flow channel, which penetrates through opposite sides of the spool along the axial direction of the spool.

[0124] According to some embodiments of the present application, the spool assembly further comprises a third elastic member and a fourth elastic member, which are sleeved on the guide rod and are respectively arranged on two sides of the moving direction of the spool, and the third elastic member and the fourth elastic member apply elastic force to the spool to keep the position of the spool stable.

[0125] According to the second aspect of the present application, a vehicle is provided, which comprises the shock absorber according to the first aspect of the present application.

[0126] According to the vehicle of the second aspect of the present application, by using the shock absorber according to the first aspect of the present application, the shock absorber can continuously adjust the damping force by adjusting the fluid flow between the compression chamber and the recovery chamber, which is beneficial to improve the riding comfort and the handling performance of the vehicle, and the structure of the shock absorber is simple and convenient to adjust.

[0127] Additional aspects and advantages of the present application will be partially given in the following description, partially will become obvious from the following description, or will be understood by the practice of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0128] The above and / or additional aspects and advantages of the present application will become apparent and be readily understood from the following description, taken in conjunction with the accompanying drawings, in which:

[0129] Fig. 1 is a structural schematic diagram of a shock absorber according to an embodiment of the present application;

[0130] Fig. 2 is a structural schematic diagram of a recovery working condition when a flow regulating valve according to an embodiment of the present application is in an open valve state;

[0131] Fig. 3 is a structural schematic diagram of a compression working condition when the flow regulating valve according to an embodiment of the present application is in the open valve state;

[0132] Fig. 4 is a structural schematic diagram of a recovery working condition when a flow regulating valve according to an embodiment of the present application is in a closed valve state;

[0133] Fig. 5 is a structural schematic diagram of a compression working condition when the flow regulating valve according to an embodiment of the present application is in the closed valve state;

[0134] Fig. 6 is a structural diagram of a damper according to an embodiment of the present application;

[0135] Fig. 7 is a detailed view of A in Fig. 1;

[0136] Fig. 8 is a structural diagram of a spool assembly of a damper according to an embodiment of the present application;

[0137] Fig. 9 is a sectional view of a valve body and a flow regulating valve of a damper according to an embodiment of the present application;

[0138] Fig. 10 is a detailed view of A in Fig. 7;

[0139] Fig. 11 is an exploded view of a flow regulating valve according to an embodiment of the present application;

[0140] Fig. 12 is a sectional view of the flow regulating valve after explosion according to an embodiment of the present application;

[0141] Fig. 13 is a sectional view of the flow regulating valve when a second flow passage is open according to an embodiment of the present application;

[0142] Fig. 14 is a sectional view of the flow regulating valve when a third flow passage is open according to an embodiment of the present application;

[0143] Fig. 15 is a sectional view of the flow regulating valve when a third flow passage is open according to an embodiment of the present application;

[0144] Fig. 16 is a detailed view of D in Fig. 11;

[0145] Fig. 17 is a structural diagram of an overflow valve body of a flow regulating valve according to an embodiment of the present application;

[0146] Fig. 18 is a structural diagram of the overflow valve body of the flow regulating valve from another perspective according to an embodiment of the present application;

[0147] Fig. 19 is a sectional view of the overflow valve body according to an embodiment of the present application;

[0148] Fig. 20 is a sectional view of the overflow valve body of the flow regulating valve according to an embodiment of the present application;

[0149] Fig. 21 is a structural diagram of a second seat body of an overflow valve seat according to an embodiment of the present application;

[0150] Fig. 22 is a structural diagram of an overflow valve disc according to an embodiment of the present application;

[0151] Fig. 23 is a structural diagram of an overflow valve disc according to another embodiment of the present application;

[0152] Fig. 24 is a sectional view of the overflow valve disc according to another embodiment of the present application;

[0153] Fig. 25 is a sectional view of a flow regulating valve according to another embodiment of the present application;

[0154] Fig. 26 is a sectional view of a flow regulating valve according to an embodiment of the present application;

[0155] Fig. 27 is a sectional view of an overflow valve spool according to an embodiment of the present application;

[0156] Fig. 28 is a sectional view of a second seat body of an overflow valve seat according to an embodiment of the present application;

[0157] Fig. 29 is a sectional view of a flow regulating valve according to another embodiment of the present application;

[0158] Fig. 30 is a sectional view of a second seat body of an overflow valve seat according to a second embodiment of the present application;

[0159] Fig. 31 is a sectional view of a second seat body of an overflow valve seat according to a third embodiment of the present application;

[0160] Fig. 32 is a sectional view of a second seat body of an overflow valve seat according to a fourth embodiment of the present application;

[0161] Fig. 33 is a structural view of a first seat body and a magnetic attraction member, a magnetic force regulating spool of an overflow valve seat according to an embodiment of the present application;

[0162] Fig. 34 is a structural view of an overflow valve spool of a flow regulating valve according to an embodiment of the present application;

[0163] Fig. 35 is a structural view of a pilot valve of a shock absorber according to an embodiment of the present application;

[0164] Fig. 36 is an exploded view of a second seat body and a magnetic attraction member of an overflow valve seat according to an embodiment of the present application;

[0165] Fig. 37 is a sectional view of a second seat body and a magnetic attraction member of an overflow valve seat according to an embodiment of the present application;

[0166] Fig. 38 is a sectional view of a second seat body and a magnetic attraction member of an overflow valve seat according to another embodiment of the present application;

[0167] Fig. 39 is a sectional view of a second seat body and a magnetic attraction member of an overflow valve seat according to another embodiment of the present application;

[0168] Fig. 40 is a structural view of an overflow valve spool according to an embodiment of the present application;

[0169] Fig. 41 is a structural view of an overflow valve spool according to an embodiment of the present application;

[0170] Fig. 42 is a sectional view of an overflow valve spool according to an embodiment of the present application;

[0171] Fig. 43 is a structural schematic view of a pilot valve of a shock absorber according to an embodiment of the present application;

[0172] Fig. 44 is a sectional view of a pilot valve of a shock absorber according to an embodiment of the present application;

[0173] Fig. 45 is a sectional view of a pilot valve of a shock absorber according to an embodiment of the present application;

[0174] Fig. 46 is a structural schematic view of a pilot valve of a shock absorber according to an embodiment of the present application;

[0175] Fig. 47 is a schematic view of a principle of fluid being guided by a pilot valve according to an embodiment of the present application;

[0176] Fig. 48 is a structural schematic view of a pilot valve according to an embodiment of the present application;

[0177] Fig. 49 is an exploded view of a pilot valve according to an embodiment of the present application;

[0178] Fig. 50 is an exploded view of a pilot valve according to an embodiment of the present application;

[0179] Fig. 51 is an exploded view of a pilot valve according to another embodiment of the present application;

[0180] Fig. 52 is a sectional exploded view of a pilot valve according to an embodiment of the present application;

[0181] Fig. 53 is a structural schematic view of a second elastic member of a pilot valve according to an embodiment of the present application;

[0182] Fig. 54 is a structural schematic view of an upper valve body according to an embodiment of the present application;

[0183] Fig. 55 is a structural schematic view of a second elastic member of a pilot valve according to an embodiment of the present application;

[0184] Fig. 56 is a structural schematic view of an upper valve body according to an embodiment of the present application;

[0185] Fig. 57 is a sectional view of an upper valve body according to an embodiment of the present application;

[0186] Fig. 58 is a structural schematic view of a lower valve body according to an embodiment of the present application;

[0187] Fig. 59 is a structural schematic view of a lower valve body according to an embodiment of the present application;

[0188] Fig. 60 is a structural schematic view of a pilot valve according to an embodiment of the present application;

[0189] Fig. 61 is a structural schematic view of a pilot valve plug according to an embodiment of the present application;

[0190] Figure 62 is a cross-sectional view of a pilot valve spool of a pilot valve in accordance with an embodiment of the present application;

[0191] Reference signs: 1, shock absorber; 100, cylinder; 110, inner cylinder; 111, compression chamber; 112, recovery chamber; 120, outer cylinder; 121, liquid storage chamber; 130, bottom valve assembly; 200, piston; 210, piston rod; 220, piston valve assembly; 230, valve body; 240, upper valve body; 241, first chamber; 242, second chamber; 243, fourth flow channel; 244, sealing ring table; 250, lower valve body; 251, fifth flow channel; 252, first limiting step; 253, third chamber; 300, flow regulating valve; 310, overflow valve body; 311, second flow channel; 312, first abutting ring table; 3133, overflow gap; 314, sixth flow channel; 314a, radial section; 314b, axial section; 315, seventh flow channel; 316, sealing groove; 317, limiting ring groove; 320, overflow valve seat; 321, first flow channel; 322, third flow channel; 323, first seat body; 3231, through hole; 324, second seat body; 3241, flow channel hole; 325, second abutting ring table; 326, flow guide surface; 3261, inclined surface; 3262, third step surface; 327, second limiting step; 328, reinforcing step; 329, second step surface; 330, overflow valve piece; 331, communication hole; 332, main body part; 3321, second round corner surface; 333, guide part; 3331, first round corner surface; 334, guide hole; 335, valve body abutting surface; 336, valve body pressure bearing surface; 337, valve seat abutting surface; 338, valve seat pressure bearing surface; 339, overflow hole; 340, support column; 341, support ring table; 342, connecting section; 343, transition section; 344, clamping groove; 345, guide section; 350, magnetic attraction piece; 351, magnetic force adjusting piece; 352, magnetic force adjusting piece; 360, first elastic piece; 370, overflow channel; 371, first overflow gap; 380, limiting piece; 400, control valve; 410, coil assembly; 420, magnetic isolation ring; 430, static iron core; 432, groove; 500, valve core assembly; 510, iron core cover; 511, mounting groove; 512, second guide sleeve; 513, first step part; 520, valve core; 521, eighth flow channel; 522, first groove; 523, second groove; 524, second step part; 530, guide rod; 531, guide sleeve; 540, third elastic piece; 550, fourth elastic piece; 600, pilot valve; 610, first body part; 611, first balance hole; 612, sealing protrusion; 613, body flow guide surface; 620, first flow guide part; 630, base; 631, second body part; 632, second flow guide part; 6321, first flow guide section; 6322, second flow guide section; 633, stop structure; 634, second balance hole; 635, gap; 636, base abutting table; 637, base avoiding groove; 638, annular boss; 639, guide rod connecting groove; 640, pilot valve plug;641, plug; 642, plug avoiding groove; 643, plug head; 650, second elastic member; 651, outer ring body; 652, inner elastic arm. DETAILED DESCRIPTION

[0192] Embodiments of the present application are described below in detail with reference to the accompanying drawings, wherein the same or similar components or components having the same or similar functions are denoted by the same or similar reference numerals throughout the drawings. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present application and cannot be understood as a limitation of the present application.

[0193] In the description of the present application, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only used to facilitate the description of the present application and simplify the description, and therefore cannot be understood as indicating or implying that the device or component referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation of the present application.

[0194] In the description of the present application, "first feature" and "second feature" can include one or more of the features.

[0195] In the description of the present application, "a plurality of" means two or more, and "several" means one or more.

[0196] A shock absorber 1 according to an embodiment of the present application is described below with reference to the accompanying drawings.

[0197] As shown in FIGS. 1-62, the shock absorber 1 according to an embodiment of the present application includes a cylinder 100, a piston 200, a flow regulating valve 300, and a control valve 400.

[0198] The piston 200 is movably provided in the cylinder 100, and the piston 200 divides the cylinder 100 into a compression chamber 111 and a rebound chamber 112. The flow regulating valve 300 is provided in the piston 200 and communicates with the compression chamber 111 and the rebound chamber 112, respectively. The control valve 400 is provided in the piston 200, and the control valve 400 controls the flow regulating valve 300 to adjust the fluid flow between the compression chamber 111 and the rebound chamber 112.

[0199] In the compression chamber 111 and the rebound chamber 112, fluid such as fluid with a certain pressure and inert gas can be stored.

[0200] The shock absorber 1 further comprises a bottom valve assembly 130, the cylinder body 100 comprises an outer cylinder 120 and an inner cylinder 110, the inner cylinder 110 extends into the outer cylinder 120, a liquid storage cavity 121 is formed between the outer cylinder 120 and the inner cylinder 110, the piston 200 is movably arranged in the inner cylinder 110 and divides the inner cylinder 110 into a compression cavity 111 and a recovery cavity 112, the bottom valve assembly 130 is installed on the inner cylinder 110 or the outer cylinder 120, and the fluid in the compression cavity 111 flows into the liquid storage cavity 121 through the bottom valve assembly 130, or the fluid in the liquid storage cavity 121 flows into the compression cavity 111 through the bottom valve assembly 130.

[0201] It should be noted that the open valve state of the flow regulating valve 300 refers to the state of the flow regulating valve 300 when the flow regulating valve 300 is not extruded by external pressure, for example, when the spool assembly 500 does not apply force to the flow regulating valve 300, and the closed valve state of the flow regulating valve 300 refers to the state of the flow regulating valve 300 when the flow regulating valve 300 is extruded by external force, for example, when the spool assembly 500 applies force to the flow regulating valve 300.

[0202] According to the shock absorber 1 of the embodiment of the present application, the piston 200 is movably arranged in the cylinder body 100, the piston 200 divides the cylinder body 100 into the compression cavity 111 and the recovery cavity 112, and the flow regulating valve 300 is arranged on the piston 200 and communicates with the compression cavity 111 and the recovery cavity 112, respectively.

[0203] In this way, when the shock absorber 1 is in the compression working condition, the piston 200 compresses the volume of the compression cavity 111, and the volume of the recovery cavity 112 increases accordingly, at this time, the fluid in the compression cavity 111 flows to the recovery cavity 112 through the flow regulating valve 300, and when the shock absorber 1 is in the recovery working condition, the piston 200 compresses the volume of the recovery cavity 112, and the volume of the compression cavity 111 increases accordingly, at this time, the fluid in the recovery cavity 112 flows to the compression cavity 111 through the flow regulating valve 300, in the above process, the moving direction of the piston 200 is repeatedly changed, so that the fluid repeatedly flows between the compression cavity 111 and the recovery cavity 112, the fluid generates heat by rubbing with the shock absorber 1, and the kinetic energy of the piston 200 can be converted into heat energy of the fluid, thereby reducing the kinetic energy of the piston 200.

[0204] Therefore, when the cylinder body 100 and the piston 200 of the shock absorber 1 are connected with two objects (for example, a vehicle frame and a vehicle wheel), respectively, when one of the two objects vibrates, the vibration force transmitted to the other object can be reduced by the presence of the shock absorber 1, thereby achieving the effect of shock absorption.

[0205] In addition, the control valve 400 is arranged on the piston 200, and the control valve 400 adjusts the flow rate of the fluid between the compression cavity 111 and the recovery cavity 112 by controlling the flow regulating valve 300.

[0206] Thus, when the piston 200 moves, the fluid flow between the compression chamber 111 and the recovery chamber 112 can be adjusted by the control valve 400 simultaneously, when the fluid flow through the flow regulating valve 300 is large, the damping force of the shock absorber 1 can be small, i.e. the shock absorber 1 can be "soft", and when the fluid flow through the flow regulating valve 300 is small, the damping force of the shock absorber 1 can be large, i.e. the shock absorber 1 can be "hard", and the control valve 400 can continuously adjust the size of the fluid flow through the flow regulating valve 300, so that the shock absorber 1 can realize continuous adjustment of the damping force, which is beneficial to improve the riding comfort and the handling stability of the vehicle.

[0207] Moreover, by controlling the flow regulating valve 300 through the control valve 400, the structure of the fluid flow between the compression chamber 111 and the recovery chamber 112 of the shock absorber 1 is simple, so that the adjustment structure of the damping force of the shock absorber 1 can be simplified, so as to facilitate the adjustment of the damping force of the shock absorber 1, and the adjustment is more simple and convenient.

[0208] Thus, the shock absorber 1 according to the embodiments of the present application can continuously adjust the damping force by adjusting the fluid flow between the compression chamber 111 and the recovery chamber 112, which is beneficial to improve the riding comfort and the handling performance of the vehicle, and the structure of the shock absorber 1 is simple and convenient to adjust.

[0209] More specifically, the flow regulating valve 300 is in the open valve state at the initial position, which means that the flow regulating valve 300 is opened when there is no external pressure extrusion and no fluid flow in the flow regulating valve 300. In addition, the flow regulating valve 300 is in the closed valve state at the initial position, which means that the flow regulating valve 300 is closed when the overflow valve seat 320 and the overflow valve body 310 of the flow regulating valve 300 abut under the extrusion of external force.

[0210] For example, in some embodiments, the spool assembly 500 is energized to extrude the flow regulating valve 300, at this time, the flow regulating valve 300 is in the open valve state at the initial position, which means that the flow regulating valve 300 is opened when the spool assembly 500 is not energized and there is no fluid flow in the flow regulating valve 300, at this time the flow regulating valve 300 is in the balanced state; and the flow regulating valve 300 is in the closed valve state at the initial position, which means that the flow regulating valve 300 is closed when the spool assembly 500 is energized and the overflow valve seat 320 and the overflow valve body 310 of the flow regulating valve 300 abut.

[0211] Or, in other embodiments, the spool assembly 500 is not energized to press the flow regulating valve 300, then the flow regulating valve 300 is in the open valve state at the initial position, which means the initial state of opening when the spool assembly 500 is energized and there is no fluid flowing in the flow regulating valve 300, at this time the flow regulating valve 300 is in the balance state; and the flow regulating valve 300 is in the closed valve state at the initial position, which means the initial state of closing when the spool assembly 500 is not energized and the overflow valve seat 320 and the overflow valve body 310 of the flow regulating valve 300 abut.

[0212] The flow regulating valve 300 according to the embodiments of the present application is described below with reference to the accompanying drawings.

[0213] As shown in FIG. 1 and FIG. 9, the flow regulating valve 300 includes an overflow valve seat 320, an overflow valve body 310, and a first elastic member 360 (or referred to as a valve body elastic member 360).

[0214] The overflow valve body 310 is movably arranged at one side of the overflow valve seat 320, and one of the overflow valve seat 320 and the overflow valve body 310 is provided with a support column 340, and the first elastic member 360 is arranged between the other of the overflow valve seat 320 and the overflow valve body 310 and the support column 340.

[0215] Wherein, one of the overflow valve seat 320 and the overflow valve body 310 is provided with the support column 340, which means that the support column 340 can be arranged at the side of the overflow valve body 310 facing the overflow valve seat 320, or the support column 340 can be arranged at the side of the overflow valve seat 320 facing the overflow valve body 310.

[0216] It can be understood that the first elastic member 360 can provide a repulsive force to push the overflow valve body 310 and the overflow valve seat 320 apart. In this way, when the flow regulating valve 300 is in the open state, the first elastic member 360 can assist in pushing the overflow valve seat 320 and the overflow valve body 310 apart, so that the flow regulating valve 300 is opened more easily, at this time the flow of the fluid flowing through the flow regulating valve 300 in the compression chamber 111 and the recovery chamber 112 is larger, the damping of the shock absorber 1 is smaller, and the shock absorber 1 can be "soft", and the riding comfort is better.

[0217] Therefore, the flow regulating valve 300 according to the embodiments of the present application can use the first elastic member 360 to push the overflow valve seat 320 and the overflow valve body 310 apart, so as to facilitate the opening of the flow regulating valve 300, and further facilitate the adjustment of the damping force of the shock absorber 1.

[0218] In some specific embodiments of the present application, as shown in FIG. 1, FIG. 7, FIG. 13 and FIG. 16, the flow regulating valve 300 includes an overflow valve body 310, an overflow valve seat 320, and an overflow valve sheet 330.

[0219] The flow regulating valve 300 has an open valve state and a closed valve state. When the flow regulating valve 300 is in the closed valve state, the overflow valve body 310 and the overflow valve seat 320 abut against the overflow valve disc 330. When the flow regulating valve 300 is in the open valve state, one of the overflow valve body 310 and the overflow valve seat 320 can be separated from the overflow valve disc 330.

[0220] The overflow valve body 310 is movably installed in the piston 200. The overflow valve seat 320 is installed in the piston 200 and located on the side of the overflow valve body 310 away from the control valve 400. The overflow valve seat 320 is provided with a first flow channel 321, which is in communication with the compression chamber 111. The overflow valve disc 330 is movably arranged between the overflow valve body 310 and the overflow valve seat 320. The overflow valve disc 330 and the overflow valve body 310 form a second flow channel 311 therebetween. The overflow valve disc 330 and the overflow valve seat 320 form a third flow channel 322 therebetween. The second flow channel 311 and the third flow channel 322 are in communication with the first flow channel 321 and are both in communication with the recovery chamber 112.

[0221] The second flow channel 311 and / or the third flow channel 322 are opened and closed by the movement of the overflow valve body 310.

[0222] When the second flow channel 311 is open, the fluid between the compression chamber 111 and the recovery chamber 112 can flow through the first flow channel 321 and the second flow channel 311. When the third flow channel 322 is open, the fluid between the compression chamber 111 and the recovery chamber 112 can flow through the first flow channel 321 and the third flow channel 322. When the second flow channel 311 and the third flow channel 322 are both open, the fluid between the compression chamber 111 and the recovery chamber 112 can flow through the first flow channel 321 and the second flow channel 311, and can also flow through the first flow channel 321 and the third flow channel 322.

[0223] By dividing the flow regulating valve 300 into the overflow valve body 310, the overflow valve disc 330, and the overflow valve seat 320, the control valve 400 can control the relative movement of the overflow valve body 310 relative to the overflow valve seat 320, so as to close the second flow channel 311 and the third flow channel 322. At this time, the fluid in the recovery chamber 112 and the compression chamber 111 cannot flow through the first flow channel 321 and the second flow channel 311 or the third flow channel 322. Alternatively, the second flow channel 311 and / or the third flow channel 322 can be opened to allow the fluid in the recovery chamber 112 and the compression chamber 111 to flow through the first flow channel 321 and the second flow channel 311 and / or the third flow channel 322. By controlling the opening and closing size of the second flow channel 311 and / or the third flow channel 322, the flow of the fluid between the compression chamber 111 and the recovery chamber 112 can be changed, so as to adjust the damping force of the shock absorber 1 and balance the pressure between the compression chamber 111 and the recovery chamber 112.

[0224] In addition, by adding the movable overflow valve plate 330 between the overflow valve body 310 and the overflow valve seat 320, when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the rebound working condition, the overflow valve body 310 and the overflow valve seat 320 can first abut on opposite sides of the overflow valve plate 330, the fluid can push open the overflow valve body 310, the overflow valve body 310 and the overflow valve plate 330 move relatively, the second flow channel 311 is opened, at this time the fluid in the rebound chamber 112 can flow into the compression chamber 111 through the second flow channel 311 and the first flow channel 321; when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the compression working condition, the overflow valve body 310 and the overflow valve seat 320 can first abut on opposite sides of the overflow valve plate 330, the fluid can push open the overflow valve body 310 and the overflow valve plate 330, that is, the overflow valve plate 330 and the overflow valve body 310 move relatively with respect to the overflow valve seat 320, the third flow channel 322 is opened, at this time the fluid in the compression chamber 111 can flow into the rebound chamber 112 through the third flow channel 322 and the first flow channel 321.

[0225] In this way, when the shock absorber 1 is in the compression working condition or the rebound working condition, the overflow valve body 310 and the overflow valve seat 320 can be relatively moved more easily, that is, the overflow valve plate 330 can assist the overflow valve body 310 and the overflow valve seat 320 to open the valve, so as to facilitate the communication between the compression chamber 111 and the rebound chamber 112.

[0226] Optionally, the overflow valve plate 330 is configured with an overflow channel 370, and when the overflow valve seat 320 and the overflow valve body 310 abut with the overflow valve plate 330 respectively, the overflow channel 370 is in communication with the first flow channel 321 and the rebound chamber 112 of the shock absorber 1 respectively.

[0227] In some embodiments of the present application, as shown in FIGS. 9, 18, 17, 22, 23 and 21, the overflow channel 370 is configured as a plurality of overflow channels 370, and the plurality of overflow channels 370 are arranged in a circumferential direction of the overflow valve plate 330, so that the plurality of overflow channels 370 can simultaneously supply fluid flow, further improving the fluid flow smoothness between the compression chamber 111 and the rebound chamber 112, and the fluid can flow along multiple parts of the circumferential direction of the overflow valve plate 330, the fluid flow is more uniform, so that the damping force of the shock absorber 1 is more stable.

[0228] Optionally, the overflow valve body 310 is movably arranged on one side of the overflow valve seat 320.

[0229] Further, as shown in FIGS. 1, 2 and 28, the overflow valve plate 330 is configured with at least one communication hole 331, and the second flow channel 311 is in communication with the first flow channel 321 through the communication hole 331.

[0230] In this way, when the overflow valve body 310 is separated from the overflow valve plate 330 and the overflow valve seat 320 abuts against the overflow valve plate 330, that is, the second flow channel 311 is opened and the third flow channel 322 is closed, the second flow channel 311 can be in communication with the first flow channel 321 through the communication hole 331, and the structure is more reasonable, so that the fluid in the recovery cavity 112 and the compression cavity 111 can flow through the second flow channel 311, the communication hole 331 and the first flow channel 321.

[0231] In addition, the communication hole 331 can be multiple, and the multiple communication holes 331 can be arranged at intervals along the circumference of the overflow valve plate 330.

[0232] In some embodiments of the present application, as shown in FIGS. 1-8, 10, 12-16, one of the overflow valve body 310 and the overflow valve seat 320 is provided with a support column 340, the support column 340 extends in the axial direction of the cylinder body 100, and the overflow valve plate 330 is movably sleeved on the support column 340, so that the overflow valve plate 330 moves in the axial direction of the cylinder body 100 under the guidance of the support column 340.

[0233] That is, the support column 340 can be arranged on the overflow valve body 310, for example, the support column 340 can be arranged on the side of the overflow valve body 310 facing the overflow valve seat 320; or, the support column 340 can also be arranged on the overflow valve seat 320, for example, the support column 340 can be arranged on the side of the overflow valve seat 320 facing the overflow valve body 310.

[0234] In this way, the support column 340 can limit the movement of the overflow valve plate 330 to limit the movement of the overflow valve plate 330 in the axial direction of the cylinder body 100, avoid the overflow valve plate 330 from being offset relative to the overflow valve body 310 and the overflow valve seat 320 in the radial direction of the cylinder body 100, and more reliably use the overflow valve plate 330 to open and close the second flow channel 311 and the third flow channel 322.

[0235] Furthermore, the support column 340 can guide the movement of the overflow valve plate 330 to make the movement of the overflow valve plate 330 relative to the overflow valve body 310 and the overflow valve seat 320 more easily.

[0236] Further, as shown in FIGS. 13 and 16, the overflow valve body 310 is provided with a support column 340, and the cross-sectional area of the free end of the support column 340 decreases towards the overflow valve seat 320.

[0237] Alternatively, the overflow valve seat 320 is provided with a support column 340, and the cross-sectional area of the free end of the support column 340 decreases towards the overflow valve body 310.

[0238] In other words, one of the overflow valve body 310 and the overflow valve seat 320 is provided with the support column 340, and the outer diameter of the free end of the support column 340 can gradually decrease away from one of the overflow valve body 310 and the overflow valve seat 320.

[0239] Wherein, the cross-sectional area of the free end of the support column 340 gradually decreases, which means that the cross-sectional area of the support column 340 can continuously decrease, or the cross-sectional area of the support column 340 discontinuously decreases, for example, the free end of the support column 340 can be stepped.

[0240] It can be understood that if the support column 340 is arranged on the overflow valve body 310, the end of the support column 340 towards the overflow valve seat 320 is the free end of the support column 340; if the support column 340 is arranged on the overflow valve seat 320, the end of the support column 340 towards the overflow valve body 310 is the free end of the support column 340.

[0241] In this way, the end of the support column 340 can be provided with a slope or an outer diameter difference, and when the overflow valve piece 330 moves a certain distance towards the free end of the support column 340, the gap between the overflow valve piece 330 and the support column 340 will gradually increase, which can reduce the friction between the overflow valve piece 330 and the support column 340, and the overflow valve piece 330 moves more easily, and the movement scraping between the overflow valve piece 330 and the support column 340 is reduced, which is beneficial to improve the damping fluctuation of the movement of the overflow valve piece 330.

[0242] As shown in FIGS. 12-16, the overflow valve body 310 is provided with the support column 340, and the end of the support column 340 towards the overflow valve seat 320 is configured with a support ring platform 341, and the first elastic member 360 is abutted to the support ring platform 341; or, the overflow valve seat 320 is provided with the support column 340, and the end of the support column 340 towards the overflow valve body 310 is configured with the support ring platform 341, and the first elastic member 360 is abutted to the support ring platform 341.

[0243] That is, the free end of the support column 340 can be configured with the support ring platform 341, and the outer diameter of the support ring platform 341 is smaller than the outer diameter of the rest of the support column 340, so that the first elastic member 360 can be sleeved on the support ring platform 341 to position the first elastic member 360 and the support column 340, which is beneficial to improve the installation accuracy of the first elastic member 360.

[0244] In addition, the other one of the overflow valve body 310 and the overflow valve seat 320 can be configured with a limiting ring groove 317, for example, the support column 340 is configured on the overflow valve seat 320.

[0245] The side of the overflow valve body 310 facing the overflow valve seat 320 can be configured with a limiting ring groove 317, and one end of the first elastic member 360 facing the overflow valve seat 320 can be arranged in the limiting ring groove 317, so that the limiting ring groove 317 can limit the first elastic member 360 and the overflow valve body 310, and the installation accuracy of the first elastic member 360 is further improved.

[0246] Further, as shown in FIG. 14, the support ring table 341 includes a connecting section 342 and a transition section 343.

[0247] The connecting section 342 is connected with the support column 340, and the transition section 343 is connected to one end of the connecting section 342 away from the support column 340, and the outer diameter of the transition section 343 is smaller than that of the connecting section 342. The first elastic member 360 is sleeved on the support ring table 341 and is in interference fit with the connecting section 342, and there is a gap between the first elastic member 360 and the transition section 343.

[0248] In this way, when the first elastic member 360 is stretched or contracted, the first elastic member 360 will not interfere with the transition section 343, so that the friction between the first elastic member 360 and the support ring table 341 can be reduced, and the interference fit between the first elastic member 360 and the connecting section 342 can ensure the stability of the connection between the first elastic member 360 and the support ring table 341.

[0249] In some embodiments of the present application, the diameter of the support column 340 is R, and R satisfies: 1mm < R < 7mm. In this way, on the one hand, the diameter of the support column 340 can be prevented from being too small to ensure that the structural strength of the support column 340 can be high, so that the support column 340 can be used to more stably fix the support first elastic member 360, and the overflow valve piece 330 can be prevented from tilting, and on the other hand, the diameter of the support column 340 can be prevented from being too large, so that the support column 340 can be prevented from occupying too much space for fluid flow in the shock absorber 1, so that the fluid can flow more smoothly.

[0250] In some embodiments of the present application, as shown in FIGS. 13 and 14, the overflow valve body 310 is provided with the support column 340, one end of the support column 340 facing the overflow valve seat 320 is configured as a guide section 345, and the guide section 345 is closer to the overflow valve seat 320 along the axial direction of the support column 340, and the cross-sectional area of the guide section 345 is reduced; or, the overflow valve seat 320 is provided with the support column 340, one end of the support column 340 facing the overflow valve body 310 is configured as a guide section 345, and the guide section 345 is closer to the overflow valve body 310 along the axial direction of the support column 340, and the cross-sectional area of the guide section 345 is reduced.

[0251] Specifically, the overflow valve body 310 is provided with the support column 340, and the gap between the overflow valve disc 330 and the guide section 345 increases along the axial direction of the support column 340 close to the overflow valve seat 320; or the overflow valve seat 320 is provided with the support column 340, and the gap between the overflow valve disc 330 and the guide section 345 increases along the axial direction of the support column 340 close to the overflow valve body 310.

[0252] In this way, the guide section 345 can be provided with a slope or a difference in outer diameter, and when the overflow valve disc 330 moves along the guide section 345 to the free end of the support column 340 by a certain distance, the gap between the overflow valve disc 330 and the support column 340 gradually increases, which can reduce the friction between the overflow valve disc 330 and the support column 340, and the overflow valve disc 330 moves more easily, and the movement scraping between the overflow valve disc 330 and the support column 340 is reduced, which is beneficial to improve the damping fluctuation of the movement of the overflow valve disc 330.

[0253] In some specific embodiments of the present application, as shown in FIGS. 1-8 and 10, the overflow valve seat 320 includes a first seat body 323 and a second seat body 324.

[0254] The overflow valve disc 330 is arranged between the first seat body 323 and the overflow valve body 310, the second seat body 324 is supported on the side of the first seat body 323 away from the overflow valve disc 330, and the second seat body 324 is adapted to be connected with the piston 200 of the shock absorber 1.

[0255] Among them, one of the first seat body 323 and the second seat body 324 constitutes the support column 340, that is, the support column 340 can be constituted in the first seat body 323, or the support column 340 can be constituted in the second seat body 324.

[0256] The first seat body 323 and the overflow valve disc 330 form a third flow channel 322, the second seat body 324 is supported on the side of the first seat body 323 away from the overflow valve disc 330 and connected with the piston 200, and the second seat body 324 and the first seat body 323 jointly define a first flow channel 321.

[0257] Among them, the support column 340 can be constituted in the first seat body 323 or the second seat body 324.

[0258] As shown in FIGS. 9-10, the first limiting step 252 can be arranged on the piston 200, for example, the first limiting step 252 can be arranged on the lower valve body 250 as described below, and the outer circumferential surface of the first seat body 323 can be provided with a second limiting step 327, the first limiting step 252 can be stopped on the side of the second limiting step 327 away from the second seat body 324, to further limit and fix the overflow valve seat 320 in the axial direction of the piston 200. Alternatively, the first seat body 323 can also be provided with external threads for connecting and cooperating with the valve body.

[0259] By dividing the overflow valve seat 320 into the first seat body 323 and the second seat body 324, it is convenient to process the overflow valve seat 320, and it is beneficial to simplify the assembly of the overflow valve seat 320 and the piston 200, and the assembly is more convenient. Of course, in some embodiments, the first seat body 323 and the second seat body 324 can also be an integral piece.

[0260] In some specific embodiments of the present application, as shown in FIGS. 11, 13 and 14, the first seat body 323 is configured with a through hole 3231, the second seat body 324 is configured with a plurality of flow channel holes 3241, and the second seat body 324 is configured with a support column 340, the support column 340 is arranged in the through hole 3231, and the plurality of flow channel holes 3241 are arranged along the circumferential direction of the support column 340.

[0261] Among them, the through hole 3231 and the plurality of flow channel holes 3241 constitute the first flow channel 321.

[0262] In this way, the support column 340 and the flow channel hole 3241 can be arranged on the second seat body 324 at the same time, the support column 340 can extend into the through hole 3231, so as to arrange the overflow valve sheet 330 and the magnetic member 350 on the support column 340, and the support column 340 does not block the through hole 3231, so that the through hole 3231 can be communicated with the compression chamber 111 through the flow channel hole 3241.

[0263] In some specific embodiments of the present application, as shown in FIGS. 40-42, the overflow valve sheet 330 includes a main body part 332 and a guide part 333.

[0264] The body portion 332 is arranged between the overflow valve body 310 and the overflow valve seat 320, the guide portion 333 is connected to the body portion 332 and protrudes from at least one side of the body portion 332 in the axial direction of the cylinder body 100 (i.e. the thickness direction of the body portion 332), the guide portion 333 and the body portion 332 jointly define a guide hole 334, and the support column 340 is arranged in the guide hole 334, so that the overflow valve plate 330 moves along the axial direction of the cylinder body 100 under the guidance of the support column 340. More specifically, the overflow valve plate 330 is movably sleeved on the support column 340 in the damper 1 through the guide hole 334, so that the overflow valve plate 330 moves along the axial direction of the damper 1 under the guidance of the support column 340.

[0265] The guide portion 333 is connected to the body portion 332 and protrudes from at least one side of the body portion 332 in the axial direction of the cylinder body 100 (i.e. the thickness direction of the body portion 322), which means that the guide portion 333 can be arranged on only one side of the thickness direction of the body portion 332, or the opposite sides of the thickness direction of the body portion 332 can be provided with the guide portion 333.

[0266] Specifically, the guide portion 333 can be arranged on the side of the body portion 332 in the axial direction of the cylinder body 100 facing the overflow valve body 310; or the guide portion 333 can be arranged on the side of the body portion 332 in the axial direction of the cylinder body 100 facing the overflow valve seat 320; or the opposite sides of the body portion 332 in the axial direction of the cylinder body 100 can be provided with the guide portion 333.

[0267] In addition, when the opposite sides of the body portion 332 in the axial direction of the cylinder body 100 can be provided with the guide portion 333, the axial length of the guide portion 333 on the two sides of the body portion 332 can be the same; or the axial length of the guide portion 333 on the side of the body portion 332 facing the overflow valve body 310 can be greater than the length of the guide portion 333 on the side of the body portion 332 facing the overflow valve seat 320; or the axial length of the guide portion 333 on the side of the body portion 332 facing the overflow valve seat 320 can be greater than the length of the guide portion 333 on the side of the body portion 332 facing the overflow valve body 310.

[0268] By setting the guide portion 333, and the guide portion 333 and the main body portion 332 jointly defining the guide hole 334, the cooperation area of the overflow valve sheet 330 and the support column 340 can be increased, so that the overflow valve sheet 330 can move along the support column 340 more stably, the overflow valve sheet 330 is not easy to be inclined relative to the support column 340, the overflow valve sheet 330 can remain stable after several tens of millions of times of opening and closing, and the stability of the damping force adjustment of the shock absorber 1 is further improved. In this way, the overflow valve sheet 330 according to the embodiment of the present application can guide the movement of the overflow valve sheet 330 by using the guide portion 333, so as to reduce the inclination or shaking of the overflow valve sheet 330 during movement, the movement of the overflow valve sheet 330 is more stable, and the stability of the damping force adjustment of the shock absorber 1 is improved.

[0269] In some embodiments of the present application, as shown in FIG. 42, along the axial direction of the overflow valve sheet 330, the length of the guide portion 333 is L, and the thickness of the main body portion 332 is W; wherein L and W satisfy L>2W.

[0270] For example, L can be greater than 2W, 2.5W, 3W, 3.5W or 4W. In this way, the length of the guide portion 333 along the axial direction of the overflow valve sheet 330 can be avoided to be too short, the contact area of the guide portion 333 and the support column 340 can be larger, and the cooperation is more stable, so that the overflow valve sheet 330 can move along the support column 340 stably, and the stability of the damping force adjustment of the shock absorber 1 is further improved.

[0271] Preferably, the length of the guide portion 333 can be 3 times the thickness of the main body portion 332. In this way, the length of the guide portion 333 will not be too long, the occupied space of the overflow valve sheet 330 will not be too large, the assembly is facilitated, and the machining precision of the guide portion 333 will not be too high, avoiding the machining cost of the overflow valve sheet 330 being too high.

[0272] In some embodiments of the present application, as shown in FIGS. 41 and 42, the guide portion 333 is arranged on one side of the thickness direction of the main body portion 332. In this way, the arrangement structure of the guide portion 333 can be simplified, and the structure of the overflow valve sheet 330 can be simplified, facilitating the machining and manufacturing.

[0273] Further, as shown in FIGS. 41 and 42, the guide portion 333 is provided with a first fillet surface 3331, the first fillet surface 3331 extends along the circumferential direction of the guide hole 334, and the side of the guide portion 333 away from the main body portion 332 and the inner side wall of the guide hole 334 are arc transitioned through the first fillet surface 3331.

[0274] For example, the guide portion 333 is arranged on the side of the main body portion 332 facing the spool valve body 310, so that when the spool valve piece 330 moves along the support column 340 towards the spool valve body 310, the end of the guide portion 333 is less likely to scratch the support column 340, and the friction can be smaller, and the spool valve piece 330 and the support column 340 are less likely to be worn.

[0275] Alternatively, the guide portion 333 is arranged on the side of the main body portion 332 facing the spool valve seat 320, so that when the spool valve piece 330 moves along the support column 340 towards the spool valve seat 320, the end of the guide portion 333 is less likely to scratch the support column 340, and the friction can be smaller, and the spool valve piece 330 and the support column 340 are less likely to be worn.

[0276] In some embodiments of the present application, as shown in FIG. 42, the main body portion 332 is provided with a second rounded surface 3321 extending along the circumference of the guide hole 334, and the side of the main body portion 332 away from the guide portion 333 and the inner side wall of the guide hole 334 are arc transitioned by the second rounded surface 3321.

[0277] For example, when the guide portion 333 is arranged on the side of the main body portion 332 facing the spool valve body 310, so that when the spool valve piece 330 moves along the support column 340 towards the spool valve seat 320, the end of the main body portion 332 is less likely to scratch the support column 340, and the friction can be smaller, and the spool valve piece 330 and the support column 340 are less likely to be worn.

[0278] Alternatively, when the guide portion 333 is arranged on the side of the main body portion 332 facing the spool valve seat 320, so that when the spool valve piece 330 moves along the support column 340 towards the spool valve body 310, the end of the main body portion 332 is less likely to scratch the support column 340, and the friction can be smaller, and the spool valve piece 330 and the support column 340 are less likely to be worn.

[0279] In some embodiments of the present application, the guide portion 333 is a plurality of guide portions 333, and the plurality of guide portions 333 includes a first guide portion (not shown in the figure) and a second guide portion (not shown in the figure).

[0280] The first guide portion is arranged on one side of the thickness direction of the main body portion 332, and the second guide portion is arranged on the other side of the thickness direction of the main body portion 332. That is, both sides of the thickness direction of the main body portion 332 are provided with guide portions 333, so that the stability of the cooperation between the spool valve piece 330 and the support column 340 can be further improved, and the spool valve piece 330 is less likely to shake and tilt, and moves more stably.

[0281] Further, the first guide portion is provided with a third fillet surface (not shown in the figure), which extends along the circumference of the guide hole 334, and the side of the first guide portion away from the main body portion 332 and the inner side wall of the guide hole 334 are arc transitioned by the third fillet surface; and / or, the second guide portion is provided with a fourth fillet surface (not shown in the figure), which extends along the circumference of the guide hole 334, and the side of the second guide portion away from the main body portion 332 and the inner side wall of the guide hole 334 are arc transitioned by the fourth fillet surface.

[0282] For example, the first guide portion can be arranged on the side of the main body portion 332 facing the spool valve body 310, and the second guide portion can be arranged on the side of the main body portion 332 facing the spool valve seat 320.

[0283] In this way, when the spool valve plate 330 moves along the support column 340 towards the spool valve body 310, the end of the first guide portion is less likely to scratch the support column 340, and when the spool valve plate 330 moves along the support column 340 towards the spool valve seat 320, the end of the second guide portion is also less likely to scratch the support column 340, so the spool valve plate 330 and the support column 340 are less likely to be worn, and the friction between the spool valve plate 330 and the support column 340 can be smaller, which facilitates the movement of the spool valve plate 330.

[0284] In some embodiments of the present application, the support column 340 is in clearance fit with the guide hole 334, and the distance between the outer circumferential surface of the support column 340 and the inner side wall of the guide hole 334 is D, which satisfies 0.02mm≤D≤0.15mm.

[0285] For example, the distance D between the outer circumferential surface of the support column 340 and the inner side wall of the guide hole 334 can be 0.02mm, 0.03mm, 0.04mm, 0.05mm, 0.06mm, 0.07mm, 0.08mm, 0.09mm, 0.1mm, 0.11mm, 0.12mm, 0.13mm, 0.14mm or 0.15mm.

[0286] Preferably, the unilateral clearance between the outer circumferential surface of the support column 340 and the inner side wall of the guide hole 334 can be 0.05mm-0.10mm, so that the axial movement of the spool valve plate 330 is stable, and the spool valve plate 330 and the support column 340 are less likely to be tilted and worn out.

[0287] In addition, the end of the guide hole 334 can be configured as a fillet, so that when the spool valve plate 330 moves along the support column 340, the spool valve plate 330 is less likely to scratch the support column 340, and the friction can be smaller, and the spool valve plate 330 and the support column 340 are less likely to be worn.

[0288] In some embodiments of the present application, the single-sided gap between the inner wall of the guide hole 334 and the outer circumferential surface of the support column 340 can be 0.02-0.15 mm, preferably, for example, the single-sided gap can be 0.05-0.10 mm, so that the up-and-down axial movement of the overflow valve piece 330 is smooth, and the overflow valve piece 330 is not prone to tilting and the shaft holes are not prone to wear and failure.

[0289] In some embodiments of the present application, as shown in FIG. 42, the axial length of the guide portion 333 can be greater than twice the thickness of the main body portion 332, for example, the ratio of the axial length of the guide portion 333 to the thickness of the main body portion 332 can be 3, so that not only can the length of the guide portion 333 be avoided to be too short to enable the overflow valve piece 330 to move smoothly along the support column 340, but also the length of the guide portion 333 can be avoided to be too long, so that the space occupied by the overflow valve piece 330 is not too large, facilitating assembly, and the machining precision of the guide portion 333 is not too high, avoiding the machining cost of the overflow valve piece 330 being too high.

[0290] In some embodiments of the present application, as shown in FIG. 1 and FIG. 35-39, the flow regulating valve 300 comprises an overflow valve seat 320, an overflow valve body 310, an overflow valve piece 330 and a magnetic attraction member 350. The overflow valve body 310 is movably arranged on one side of the overflow valve seat 320, the overflow valve piece 330 is movably arranged between the overflow valve body 310 and the overflow valve seat 320, and the magnetic attraction member 350 is arranged on the side of the overflow valve seat 320 facing the overflow valve piece 330, and the magnetic attraction member 350 generates a magnetic attraction force attracting the overflow valve piece 330. By arranging the magnetic attraction member 350 on the side of the overflow valve seat 320 facing the overflow valve piece 330, the magnetic attraction member 350 generates a magnetic attraction force attracting the overflow valve piece 330. The overflow valve piece 330 can be made of a ferrous material, and by arranging the magnetic attraction member 350, the magnetic attraction member 350 attracts the overflow valve piece 330 to be close to the overflow valve seat 320, and when it is necessary to close the flow regulating valve 300, the overflow valve piece 330 can be quickly close to the overflow valve seat 320 with the assistance of the magnetic attraction member 350, and the magnetic attraction force of the magnetic attraction member 350 can make the overflow valve piece 330 and the overflow valve seat 320 fit more closely, so that the overflow valve piece 330 can be sealed to the overflow valve seat 320 to quickly build pressure.

[0291] In this way, the flow regulating valve 300 according to the embodiments of the present application can use the magnetic attraction member 350 to attract the overflow valve piece 330 to be close to the overflow valve seat 320, and then make the overflow valve piece 330 and the overflow valve seat 320 quickly fit and seal, and the sealing stability is better, so as to quickly build pressure.

[0292] Moreover, the magnetic attraction force of the magnetic attraction member 350 on the overflow valve piece 330 can be adjusted by the magnetic force adjusting member 352 to meet the use requirements of different shock absorbers 1.

[0293] When the support column 340 is configured on the overflow valve seat 320, the magnetic member 350 can be sleeved on the support column 340.

[0294] In addition, the magnetic member 350 can also adsorb and filter metal impurities in the shock absorber 1, so that the operation of the shock absorber 1 is more stable and reliable.

[0295] In some embodiments of the present application, as shown in FIG. 35, the overflow valve seat 320 is configured with at least one flow channel hole 3241, and the magnetic member 350 is arranged adjacent to the flow channel hole 3241. In this way, the fluid flowing through the flow channel hole 3241 can be closer to the magnetic member 350, so as to adsorb and filter the magnetic impurities in the fluid by using the magnetic member 350, which is beneficial to improve the filtering effect of the magnetic impurities.

[0296] In some embodiments of the present application, as shown in FIG. 35, the flow channel hole 3241 is configured as a circular arc-shaped flow channel hole extending around the magnetic member 350. Among them, the circular arc-shaped flow channel hole refers to the cross-sectional shape of the flow channel hole 3241 is circular arc-shaped. In this way, the shape of the flow channel hole 3241 and the magnetic member 350 can be matched, and the fluid flowing through the flow channel hole 3241 can flow around the magnetic member 350, that is, the contact area between the fluid and the magnetic member 350 can be increased, and the filtering and adsorbing effect of the magnetic member 350 on the magnetic impurities in the fluid is further improved.

[0297] In some embodiments of the present application, as shown in FIGS. 35-39, the flow regulating valve 300 further comprises a limiting member 380.

[0298] The limiting member 380 is arranged on the support column 340 and located on the side of the magnetic member 350 adjacent to the overflow valve sheet 330, so as to limit the magnetic member 350 and the overflow valve sheet 330.

[0299] Among them, the limiting member 380 can be a clamp. By limiting the magnetic member 350 through the limiting member 380, the movement of the magnetic member 350 along the axial direction of the support column 340 can be avoided, and the fixing stability of the magnetic member 350 is further improved.

[0300] In addition, when the magnetic force adjusting member 352 is provided, the limiting member 380 can also be used to axially limit the magnetic force adjusting member 352.

[0301] In some embodiments of the present application, as shown in FIG. 36, the support column 340 is formed with a clamping groove 344, and the limiting member 380 is clamped in the clamping groove 344. In this way, the connection between the limiting member 380 and the support column 340 can be simplified, and the connection between the limiting member 380 and the support column 340 is reliable.

[0302] Further, the flow regulating valve 300 further comprises a magnetic force adjusting member 352, which is arranged on one side of the magnetic attraction member 350, for example, on the side of the magnetic attraction member 350 facing the overflow valve plate 330, and is used to adjust the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330.

[0303] For example, the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330 can be increased or decreased by adjusting the size of the magnetic force adjusting member 352 between the magnetic attraction member 350 and the overflow valve plate 330, so as to meet the use requirements of different shock absorbers 1. In this way, it can be avoided that the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330 is too large, and the magnetic attraction member 350 excessively adsorbs the overflow valve plate 330, and at the same time, it can be avoided that the magnetic attraction force of the magnetic attraction member 350 is too small, so that the magnetic attraction member 350 and the magnetic force adjusting member can more effectively adsorb and filter the metal impurities in the shock absorber 1.

[0304] For example, the more magnetic force adjusting members 352 are added, the greater the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330 can be, or the more magnetic force adjusting members 352 are added, the smaller the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330 can be.

[0305] In some specific embodiments of the present application, as shown in FIG. 38, the magnetic force adjusting member 352 is arranged on the side of the magnetic attraction member 350 facing the overflow valve plate 330, and the magnetic force adjusting member 352 is used to block the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330, so as to adjust the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330.

[0306] Here, the magnetic force adjusting member 352 is used to block the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330, which means that the magnetic force adjusting member 352 can weaken the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330.

[0307] In this way, by changing the size of the magnetic force adjusting member 352 between the magnetic attraction member 350 and the overflow valve plate 330, the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330 can be adjusted. It should be noted that the greater the size of the magnetic force adjusting member 352 between the magnetic attraction member 350 and the overflow valve plate 330, the more obvious the blocking effect of the magnetic force adjusting member 352 on the magnetic attraction force.

[0308] Therefore, when the size of the magnetic force adjusting member 352 between the magnetic attraction member 350 and the overflow valve plate 330 is large, the blocking effect of the magnetic force adjusting member 352 on the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330 is better, and at this time, the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330 can be reduced; and when the size of the magnetic force adjusting member 352 between the magnetic attraction member 350 and the overflow valve plate 330 is small, the blocking effect of the magnetic force adjusting member 352 on the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330 is weak, and at this time, the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330 can be large.

[0309] In some embodiments of the present application, as shown in FIG. 39, a magnetic force adjusting member 352 is arranged between the magnetic attraction member 350 and the overflow valve seat 320, and the magnetic force adjusting member 352 is used to adjust the minimum distance between the magnetic attraction member 350 and the overflow valve plate 330, so as to adjust the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330.

[0310] It should be noted that the larger the size of the magnetic force adjusting member 352 between the magnetic attraction member 350 and the overflow valve seat 320, the smaller the distance between the magnetic attraction member 350 and the overflow valve plate 330, and the larger the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330.

[0311] Therefore, when the size of the magnetic force adjusting member 352 between the magnetic attraction member 350 and the overflow valve seat 320 is large, the magnetic force adjusting member 352 can support the magnetic attraction member 350, so that the distance between the magnetic attraction member 350 and the overflow valve plate 330 can be small, thereby increasing the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330; and when the size of the magnetic force adjusting member 352 between the magnetic attraction member 350 and the overflow valve seat 320 is small, the distance between the magnetic attraction member 350 and the overflow valve plate 330 can be large, thereby weakening the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330.

[0312] In some embodiments of the present application, as shown in FIGS. 11 and 12, the magnetic force adjusting member 352 comprises at least one magnetic force adjusting plate 351.

[0313] The at least one magnetic force adjusting plate 351 is arranged in a stack, and the magnetic force adjusting plate 351 adjusts the magnetic attraction force of the magnetic attraction member 350 to the overflow valve plate 330 by adjusting the number of the magnetic force adjusting plate 351, and an adsorption gap is formed between two adjacent magnetic force adjusting plates 351.

[0314] When the support column 340 is arranged on the overflow valve seat 320, the magnetic force adjusting plate 351 can also be sleeved on the support column 340.

[0315] In this way, the number of magnetic force adjusting pieces 351 can be changed as needed, so that the magnetic attraction force of the magnetic attraction piece 350 to the overflow valve piece 330 can be increased or decreased to meet the use requirements of different shock absorbers 1. For example, when the number of magnetic force adjusting pieces 351 is increased, the magnetic attraction force of the magnetic attraction piece 350 to the overflow valve piece 330 can be blocked by the magnetic force adjusting pieces 351, so that the magnetic attraction force of the magnetic attraction piece 350 to the overflow valve piece 330 can be reduced. In this way, by adjusting the number of magnetic force adjusting pieces 351, on the one hand, the magnetic attraction force of the magnetic attraction piece 350 to the overflow valve piece 330 can be avoided to be too large, and on the other hand, the magnetic attraction force of the magnetic attraction piece 350 to the overflow valve piece 330 can be avoided to be too small, so that the magnetic attraction piece 350 and the magnetic force adjusting piece 351 can more effectively adsorb and filter the metal impurities in the shock absorber 1.

[0316] For example, when the magnetic force adjusting piece 352 is arranged on the side of the magnetic attraction piece 350 facing the overflow valve piece 330, by increasing the number of magnetic force adjusting pieces 351, the magnetic attraction force of the magnetic attraction piece 350 to the overflow valve piece 330 can be reduced, and by reducing the number of magnetic force adjusting pieces 351, the magnetic attraction force of the magnetic attraction piece 350 to the overflow valve piece 330 can be increased. Alternatively, when the magnetic force adjusting piece 352 is arranged on the side of the magnetic attraction piece 350 facing the overflow valve seat 320, by increasing the number of magnetic force adjusting pieces 351, the magnetic attraction force of the magnetic attraction piece 350 to the overflow valve piece 330 can be increased, and by reducing the number of magnetic force adjusting pieces 351, the magnetic attraction force of the magnetic attraction piece 350 to the overflow valve piece 330 can be reduced.

[0317] Therefore, by adjusting the number of magnetic force adjusting pieces 351, the magnetic attraction force of the magnetic attraction piece 350 to the overflow valve piece 330 can be more accurately adjusted, and the adjustment is more convenient, not only can the magnetic attraction force of the magnetic attraction piece 350 to the overflow valve piece 330 be avoided to be too large, but also the magnetic attraction piece 350 and the magnetic force adjusting piece 351 can more effectively adsorb and filter the metal impurities in the shock absorber 1.

[0318] Further, the magnetic force adjusting pieces 351 are a plurality of, and an adsorption gap is formed between adjacent two magnetic force adjusting pieces 351 or between the magnetic force adjusting piece 351 and the magnetic attraction piece 350.

[0319] Moreover, by forming the adsorption gap between adjacent two magnetic force adjusting pieces 351, it can be understood that the magnetic force adjusting piece 351 will be magnetized by the magnetic attraction piece 350, so that the magnetic force adjusting piece 351 can adsorb the metal dust impurities inside the shock absorber 1 into the adsorption gap, thereby avoiding the metal dust impurities to continue flowing in the shock absorber, so that the operation of the shock absorber 1 is more stable and reliable.

[0320] In some embodiments of the present application, the magnetic force adjusting member 352 comprises a magnetic force adjusting block (not shown in the figure), which adjusts the magnetic attraction force of the magnetic attraction member 350 to the overflow valve piece 330 by adjusting the height of the magnetic force adjusting block along the axial direction of the cylinder body 100. Optionally, the magnetic force adjusting block is provided with an adsorption hole.

[0321] In this way, the height of the magnetic force adjusting block can be changed as needed, so that the magnetic attraction force of the magnetic attraction member 350 to the overflow valve piece 330 can be increased or decreased to meet the use requirements of different shock absorbers 1. For example, when the height of the magnetic force adjusting block along the axial direction of the cylinder body 100 is increased, the magnetic attraction force of the magnetic attraction member 350 to the overflow valve piece 330 can be blocked by the magnetic force adjusting block, so that the magnetic attraction force of the magnetic attraction member 350 to the overflow valve piece 330 can be reduced. In this way, by adjusting the height of the magnetic force adjusting block, on the one hand, the magnetic attraction force of the magnetic attraction member 350 can be prevented from being too large to avoid the magnetic attraction force of the magnetic attraction member 350 to the overflow valve piece 330 being too large, and on the other hand, the magnetic attraction force of the magnetic attraction member 350 can be prevented from being too small to make the magnetic attraction member 350 and the magnetic force adjusting block more effectively adsorb and filter the metal impurities in the shock absorber 1.

[0322] For example, when the magnetic force adjusting block is arranged on the side of the magnetic attraction member 350 facing the overflow valve piece 330, by increasing the height of the magnetic force adjusting block, the magnetic attraction force of the magnetic attraction member 350 to the overflow valve piece 330 can be reduced, and by reducing the height of the magnetic force adjusting block, the magnetic attraction force of the magnetic attraction member 350 to the overflow valve piece 330 can be increased. Alternatively, when the magnetic force adjusting block is arranged on the side of the magnetic attraction member 350 facing the overflow valve seat 320, by increasing the height of the magnetic force adjusting block, the magnetic attraction force of the magnetic attraction member 350 to the overflow valve piece 330 can be increased, and by reducing the height of the magnetic force adjusting block, the magnetic attraction force of the magnetic attraction member 350 to the overflow valve piece 330 can be reduced.

[0323] Furthermore, by constructing the adsorption hole on the adjusting block, it can be understood that the magnetic force adjusting block will be magnetized by the magnetic attraction member 350, so that the magnetic force adjusting block can adsorb the metal dust impurities inside the shock absorber 1 into the adsorption hole, thereby avoiding the metal dust impurities from continuing to flow in the shock absorber, making the operation of the shock absorber 1 more stable and reliable.

[0324] In some embodiments of the present application, as shown in FIGS. 1, 35-39, the overflow valve seat 320 is provided with a support column 340 extending along the axial direction of the overflow valve seat 320, the magnetic attraction member 350 and the overflow valve piece 330 are sleeved on the support column 340, and the overflow valve piece 330 is movable along the axial direction of the support column 340.

[0325] In this way, the support column 340 can guide the movement of the overflow valve disc 330, the overflow valve disc 330 is not prone to radial shaking, and the overflow valve disc 330 can remain stable after several tens of millions of opening and closing of the valve, further improving the stability of the damping force adjustment of the shock absorber 1.

[0326] In addition, by sleeving and fixing the magnetic attraction piece 350 to the support column 340, the position deviation of the magnetic attraction piece 350 can be avoided, so as to improve the fixing reliability of the magnetic attraction piece 350.

[0327] In some embodiments of the present application, as shown in FIGS. 9 and 13, the valve body 230 of the piston 200 is provided with a sealing ring table 244, one end of the overflow valve body 310 away from the overflow valve seat 320 is provided with a sealing sink 316, the sealing ring table 244 extends into the sealing sink 316 and dynamically seals with the sealing sink 316, and the side of the overflow valve seat 320 facing the overflow valve disc 330 is provided with a second abutting ring table 325 (also referred to as a valve seat abutting platform), the second abutting ring table 325 abuts with the overflow valve disc 330, and the inner diameter of the second abutting ring table 325 is greater than the inner diameter of the sealing sink 316.

[0328] In some embodiments of the present application, as shown in FIG. 13, the side of the overflow valve body 310 facing the overflow valve disc 330 is provided with a first abutting ring table 312, the first abutting ring table 312 abuts with the overflow valve disc 330, and the inner diameter of the first abutting ring table 312 is smaller than the inner diameter of the second abutting ring table 325.

[0329] In some embodiments of the present application, as shown in FIGS. 9, 13 and 16, the side of the overflow valve body 310 facing the overflow valve disc 330 is provided with a first abutting ring table 312, and the side of the overflow valve seat 320 facing the overflow valve disc 330 is provided with a second abutting ring table 325. Optionally, the inner diameter of the first abutting ring table 312 is smaller than the inner diameter of the second abutting ring table 325.

[0330] In this way, the contact area of the fluid in the overflow valve body 310 with the overflow valve disc 330 can be smaller than the contact area of the fluid in the overflow valve seat 320 with the overflow valve disc 330, when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the compression working condition, the fluid flows from the compression chamber 111 to the recovery chamber 112, the fluid in the first flow channel 321 is more prone to push the overflow valve disc 330 and the overflow valve body 310, so that the third flow channel 322 formed between the overflow valve disc 330 and the overflow valve seat 320 can be opened, and then the fluid in the compression chamber 111 can flow into the recovery chamber 112 from the first flow channel 321 and the third flow channel 322.

[0331] Optionally, the second abutting ring table 325 is arranged on the side of the overflow valve seat 320 facing the overflow valve body 310.

[0332] Specifically, the first abutment ring 312 and the second abutment ring 325 are staggered in the radial direction of the flow regulating valve 300, and at least part of the spill passage 370 is located between the first abutment ring 312 and the second abutment ring 325 along the radial direction of the spool 330.

[0333] Wherein, the first abutment ring 312 and the second abutment ring 325 are staggered in the radial direction of the flow regulating valve 300, means that the outer diameter of the first abutment ring 312 can be smaller than the inner diameter of the second abutment ring 325, or the inner diameter of the first abutment ring 312 can be larger than the outer diameter of the second abutment ring 325 along the radial direction of the cylinder 100.

[0334] In this way, the spill passage 370 can extend to between the first abutment ring 312 and the second abutment ring 325 along the radial direction of the cylinder 100, and the first abutment ring 312 and the second abutment ring 325 do not completely block the spill passage 370, so that the spill passage 370 can be in communication with the compression chamber 111 and the recovery chamber 112 respectively, so as to facilitate the flow of fluid in the compression chamber 111 and the recovery chamber 112 through the spill passage 370, and the structure is more reasonable.

[0335] In addition, at least part of the spill passage 370 is located between the outer circumferential surface of the first abutment ring 312 and the inner circumferential surface of the second abutment ring 325. In this way, the first abutment ring 312 and the second abutment ring 325 do not completely block the spill passage 370, so that the spill passage 370 can be in communication with the compression chamber 111 and the recovery chamber 112 respectively, so as to facilitate the flow of fluid in the compression chamber 111 and the recovery chamber 112 through the spill passage 370.

[0336] Further, the end of the spill valve body 310 away from the spill valve seat 320 is provided with a sealing groove 316, the valve body 230 is provided with a sealing ring 244, and along the radial direction of the cylinder 100, the sealing ring 244 is spaced apart from the inner side wall of the valve body 230, the spill valve body 310 and the inner side wall of the valve body 230 are in dynamic sealing cooperation, and the sealing groove 316 and the outer side wall of the sealing ring 244 are in dynamic sealing cooperation. And the inner side wall of the valve body 230, the outer side wall of the sealing ring 244 and the spill valve body 310 define a first chamber 241, and the inner side wall of the sealing ring 244 and the spill valve body 310 define a second chamber 242.

[0337] Wherein, the inner diameter of the sealing groove 316 is smaller than the inner diameter of the second abutment ring 325.

[0338] Specifically, the inner diameter of the second abutting ring table 325 can be A, that is, the inner diameter of the overflow valve seat 325 abuttingly contacts the inner diameter of the overflow valve disc 330 to form a pressure bearing area S1: π(A / 2)2, and the inner diameter of the sealing sink groove 316 is B, that is, the inner diameter of the overflow valve body 316 and the dynamic sealing surface of the valve body 230 form a pressure bearing area S2: π(B / 2)2.

[0339] It should be noted that when the flow regulating valve 300 is in the closed valve state and the shock absorber 1 is in the compression working condition, if it is desired to open the third flow channel 322, it is necessary to satisfy: the pressure on one side of the overflow valve disc 330 towards the overflow valve seat 320 (pressure intensity x force bearing area S1 of one side of the overflow valve disc 330 towards the overflow valve seat 320) > electromagnetic force borne by the overflow valve body 310 + pressure on one side of the overflow valve body 310 away from the overflow valve seat 320 (pressure intensity x force bearing area S2 of one side of the overflow valve body 310 away from the overflow valve seat 320), at this time, the fluid is more easily pushed away from the overflow valve disc 330 and the overflow valve body 310, so that the fluid can flow out from between the overflow valve seat 320 and the overflow valve disc 330, and the damping is reduced.

[0340] As can be seen from the above, when the force bearing area S2 of one side of the overflow valve body 310 away from the overflow valve seat 320 and the force bearing area S1 of one side of the overflow valve disc 330 towards the overflow valve seat 320 are proportional, the compression damping force adjustment bandwidth can be greatly improved, and the compression damping force plays a key role in the vehicle driving comfort and maneuverability. In order to improve people's demand for driving experience in different scenarios, it is necessary to try to improve the compression damping adjustment bandwidth.

[0341] Further, the inner cross-sectional area of the second abutting ring table 325 is S1, and the inner cross-sectional area of the sealing sink groove 316 is S2, and S1 and S2 satisfy: S2≤S1≤1.3×S2. Wherein, the inner cross-sectional area of the second abutting ring table 325 refers to the cross-sectional area of the inner circumferential surface of the second abutting ring table 325, and the inner cross-sectional area of the sealing sink groove 316 refers to the cross-sectional area of the inner circumferential surface of the sealing sink groove 316.

[0342] That is, when there is the following relationship: area proportional relationship formula π*(A / 2)2=(1.0-1.3)*π*(B / 2)2, that is, force bearing area S2 < force bearing area S1 ≤ 1.3 times force bearing area S2, the overflow valve disc 330 is easily pushed away for pressure relief when the damping force flows, and at the same time, the compression damping adjustment bandwidth is large, the compression damping force size is easy to adjust, and the upper limit of the vehicle driving comfort and maneuverability is high.

[0343] In some specific embodiments of the present application, as shown in FIGS. 9, 13 and 16, the outer diameter of the first abutting ring table 312 is smaller than the inner diameter of the second abutting ring table 325.

[0344] It is to be noted that the remaining part of the overflow valve body 310 at the end thereof facing the overflow valve disc 330 can extend radially outward beyond the outer circumferential surface of the first abutting ring platform 312.

[0345] In this way, the first abutting ring platform 312 and the second abutting ring platform 325 can be staggered along the radial direction of the overflow valve disc 330, and the remaining part of the overflow valve body 310 at the end thereof facing the overflow valve disc 330 can extend radially outward beyond the first abutting ring platform 312. When the flow regulating valve 300 is in the closed state and the damper 1 is in the rebounding condition, the fluid can flow between the overflow valve disc 330 and the remaining part of the overflow valve body 310 at the end thereof facing the overflow valve disc 330, so as to push the overflow valve disc 330 and the overflow valve body 310 apart, thereby opening the second flow passage 311, and the fluid in the rebounding chamber 112 can flow into the compression chamber 111 through the second flow passage 311, the communication hole 331 and the first flow passage 321.

[0346] In some embodiments of the present application, as shown in Figs. 23-28, the overflow valve disc 330 is configured with overflow passages 370, and the overflow passages 370 are in communication with the first flow passage 321 and the rebounding chamber 112 of the damper 1 when the flow regulating valve 300 is closed.

[0347] In this way, when the flow regulating valve 300 is in the closed state and the damper 1 is in the compression condition, the fluid in the compression chamber 111 can first flow to the rebounding chamber 112 through the overflow passages 370 in a stage, at this time, the flow rate of the fluid flowing from the compression chamber 111 to the rebounding chamber 112 is small, the damper 1 has a large damping, and the damper 1 behaves as "hard"; or, when the flow regulating valve 300 is in the closed state and the damper 1 is in the rebounding condition, the fluid in the compression chamber 111 can first flow to the compression chamber 111 through the overflow passages 370 in a stage, at this time, the flow rate of the fluid flowing from the rebounding chamber 112 to the compression chamber 111 is small, the damper 1 has a large damping, and the damper 1 behaves as "hard".

[0348] Furthermore, by providing the overflow passages 370 on the overflow valve disc 330, for example, the overflow passages 370 can be configured by laser drilling and grooving on the overflow valve disc 330, the machining precision of the overflow passages 370 can be higher, the consistency of the batch production of the overflow valve disc 330 is better, the requirements of the damper 1 can be better met, and in this way, the planarity of the overflow valve seat 320 and the overflow valve body 310 will not be damaged, the overflow valve seat 320 and the overflow valve body 310 can be more tightly attached to and sealed with the overflow valve disc 330, the flow resistance fluctuation of the fluid in the overflow passages 370 is smaller when the damper 1 is in a stage of the compression condition or a stage of the rebounding condition, and the fluid flows more smoothly, thereby ensuring the stability of the damping force of the damper 1 and better damping effect.

[0349] Therefore, the flow regulating valve 300 according to the embodiments of the present application can improve the machining precision of the overflow passage 370, and make the overflow valve seat 320 and the overflow valve body 310 closely adhere to the overflow valve disc 330 respectively, so that the flow resistance fluctuation of the fluid flowing through the overflow passage 370 is small, and the damping force of the shock absorber 1 is more stable.

[0350] According to the shock absorber 1 of the embodiments of the present application, by using the flow regulating valve 300 according to the above embodiments of the present application, the machining precision of the overflow passage 370 can be improved, and the overflow valve seat 320 and the overflow valve body 310 closely adhere to the overflow valve disc 330 respectively, so that the flow resistance fluctuation of the fluid flowing through the overflow passage 370 is small, and the damping force of the shock absorber 1 is more stable.

[0351] Further, as shown in FIG. 10, the side surface of the overflow valve disc 330 facing the overflow valve body 310 is configured with a valve body abutting surface 335, the valve body abutting surface 335 is arranged adjacent to the inner periphery of the overflow valve disc 330, the valve body abutting surface 335 is adapted to abut against the first abutting ring table 312, and a valve body pressure bearing surface 336 is formed between the valve body abutting surface 335 and the outer periphery of the overflow valve disc 330.

[0352] In the axial projection of the cylinder body 100, the inner periphery of the valve body abutting surface 335 is located on the inner side of the second abutting ring table 325.

[0353] Therefore, when the flow regulating valve 300 is in the closed valve state and the shock absorber 1 is in the rebound working condition, the fluid can flow between the valve body pressure bearing surface 336 and the part of the overflow valve body 310 outside the first abutting ring table 312, so as to push away the overflow valve disc 330 and the overflow valve body 310 to open the second flow passage 311.

[0354] In addition, the side surface of the overflow valve disc 330 facing the overflow valve seat 320 is configured with a valve seat abutting surface 337 and a valve seat pressure bearing surface 338, the valve seat abutting surface 337 is arranged adjacent to the outer periphery of the overflow valve disc 330, the valve seat pressure bearing surface 338 is arranged adjacent to the inner periphery of the overflow valve disc 330, and the valve seat abutting surface 337 is adapted to abut against the second abutting ring table 325. In this way, when the flow regulating valve 300 is in the closed valve state and the shock absorber 1 is in the compression working condition, the fluid can push the overflow valve disc 330 through the valve seat pressure bearing surface 338, and then the overflow valve disc 330 and the overflow valve body 310 can be pushed relative to the overflow valve seat 320 to open the third flow passage 322.

[0355] In some embodiments of the present application, as shown in FIGS. 22-28, the overflow passage 370 is configured as an overflow hole 339, the overflow hole 339 penetrates through the overflow valve disc 330 along the thickness direction of the overflow valve disc 330, and the overflow hole 339 is located between the outer peripheral surface of the first abutting ring table 312 and the inner peripheral surface of the second abutting ring table 325.

[0356] For example, the overflow hole 339 can be formed on the overflow valve sheet 330 by means of laser drilling, so that the planeness of the overflow valve sheet 330 is good, and the machining precision of the overflow hole 339 is high, and the consistency is good in batch production.

[0357] In some more specific embodiments of the present application, the overflow valve sheet 330 is configured with at least one overflow hole 339, and along the radial direction of the overflow valve sheet 330, the overflow hole 339 is located between the outer peripheral surface of the first abutting ring table 312 and the inner peripheral surface of the second abutting ring table 325 and respectively communicates with the compression cavity 111 and the recovery cavity 112.

[0358] Among them, the overflow hole 339 can be multiple, and multiple overflow holes 339 can be distributed along the circumference of the overflow valve sheet 330. Among them, the axial direction of the overflow hole 339 can be parallel to the thickness direction of the overflow valve sheet 330, or the axial direction of the overflow hole 339 can also be inclined relative to the thickness direction of the overflow valve sheet 330.

[0359] In this way, the overflow valve body 310 and the overflow valve seat 320 do not interfere with the overflow hole 339, and the overflow hole 339 can always communicate with the compression cavity 111 and the recovery cavity 112.

[0360] In addition, by configuring the overflow channel 370 as the overflow hole 339, the size of the overflow hole 339 needs to be set smaller, so that the flow of the overflow hole 339 can be smaller, when the flow regulating valve 300 is in the closed valve state and the shock absorber 1 is in the compression working condition, the fluid in the compression cavity 111 can first flow to the recovery cavity 112 through the overflow hole 339 in one stage, at this time, the flow of the fluid from the compression cavity 111 to the recovery cavity 112 is smaller, the damping of the shock absorber 1 is larger, and the shock absorber 1 behaves as "hard"; or, when the flow regulating valve 300 is in the closed valve state and the shock absorber 1 is in the recovery working condition, the fluid in the compression cavity 111 can first flow to the compression cavity 111 through the overflow hole 339 in one stage, at this time, the flow of the fluid from the recovery cavity 112 to the compression cavity 111 is smaller, the damping of the shock absorber 1 is larger, and the shock absorber 1 behaves as "hard".

[0361] In some specific embodiments of the present application, as shown in FIGS. 22-28, the overflow channel 370 is configured as a first overflow notch 371, one end of the first overflow notch 371 extends to at least between the outer peripheral surface of the first abutting ring table 312 and the inner peripheral surface of the second abutting ring table 325, and the other end of the first overflow notch 371 extends to the outer peripheral edge of the overflow valve sheet 330 along the radial direction of the overflow valve sheet 330.

[0362] Among them, the first overflow notch 371 in the present application is the overflow notch 3133.

[0363] In this way, the first overflow gap 371 can have a larger radial extension along the spillover valve piece 330, and the first overflow gap 371 is less likely to be blocked by the spillover valve seat 320 and the spillover valve body 310, so as to facilitate the fluid to flow between the compression chamber 111 and the recovery chamber 112 through the first overflow gap 371.

[0364] Further, as shown in FIG. 23, the other end of the first overflow gap 371 extends to the outer periphery of the spillover valve piece 330, so that the other end of the first overflow gap 371 is open. In this way, not only the structure of the first overflow gap 371 can be simplified, and the machining steps of the spillover valve piece 330 can be facilitated, but also the fluid can directly enter the first overflow gap 371 from the outer periphery of the spillover valve piece 330, or the fluid can enter the first overflow gap from the outer periphery of the spillover valve piece 330 along the first overflow gap 371, and the fluid flows more smoothly, and the first overflow gap 371 is less likely to be blocked by the spillover valve seat 320 and the spillover valve body 310, so as to more effectively ensure that the fluid can flow between the compression chamber 111 and the recovery chamber 112 through the first overflow gap 371.

[0365] In some embodiments of the present application, as shown in FIGS. 22-28, the first overflow gap 371 penetrates in the thickness direction of the spillover valve piece 330, so that the structure of the first overflow gap 371 can be simplified, and the machining can be facilitated, and the passage area of the first overflow gap 371 can be larger, and the fluid flows more smoothly at the first overflow gap 371.

[0366] Alternatively, the first overflow gap 371 is arranged on at least one side in the thickness direction of the spillover valve piece 330. For example, the first overflow gap 371 can be arranged on the side in the thickness direction of the spillover valve piece 330 facing the spillover valve body 310, or the first overflow gap 371 can be arranged on the side in the thickness direction of the spillover valve piece 330 facing the spillover valve seat 320, or the first overflow gap 371 can be arranged on both sides in the thickness direction of the spillover valve piece 330.

[0367] In some embodiments of the present application, the side of the first abutting ring table 312 facing the spillover valve piece 330 is provided with a second overflow gap, and the second overflow gap is in communication with the first flow channel 321 and the recovery chamber 112; and / or, as shown in FIG. 21, the side of the second abutting ring table 325 facing the spillover valve piece 330 is provided with a third overflow gap 313, and the third overflow gap 313 is in communication with the first flow channel 321 and the recovery chamber 112.

[0368] In the present application, the second overflow gap and the third overflow gap 313 are overflow gaps 3133.

[0369] For example, the second overflow gap can be configured only on the side of the overflow valve body 310 facing the overflow valve plate 330; or the third overflow gap 313 can be configured only on the side of the overflow valve seat 320 facing the overflow valve plate 330; or the second overflow gap can be configured on the side of the overflow valve body 310 facing the overflow valve plate 330, and the third overflow gap 313 can be configured on the side of the overflow valve seat 320 facing the overflow valve plate 330.

[0370] In this way, when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the compression working condition, the fluid in the compression chamber 111 can first flow to the recovery chamber 112 through the second overflow gap and / or the third overflow gap 313 in a stage, at this time, the flow rate of the fluid flowing from the compression chamber 111 to the recovery chamber 112 is small, the damping of the shock absorber 1 is large, and the shock absorber 1 behaves as “hard”; or when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the recovery working condition, the fluid in the compression chamber 111 can first flow to the compression chamber 111 through the second overflow gap and / or the third overflow gap 313 in a stage, at this time, the flow rate of the fluid flowing from the recovery chamber 112 to the compression chamber 111 is small, the damping of the shock absorber 1 is large, and the shock absorber 1 behaves as “hard”.

[0371] In some embodiments of the present application, as shown in FIGS. 22, 12, 27 and 28, at least one of the side of the overflow valve body 310 facing the overflow valve plate 330, the side of the overflow valve seat 320 facing the overflow valve plate 330 and the overflow valve plate 330 is configured with an overflow gap 313, and the overflow gap 313 is respectively communicated with the compression chamber 111 and the recovery chamber 112.

[0372] In some embodiments of the present application, as shown in FIGS. 22, 12, 27 and 28, at least one of the side of the overflow valve body 310 facing the overflow valve plate 330, the side of the overflow valve seat 320 facing the overflow valve plate 330 and the overflow valve plate 330 is configured with an overflow gap 313, and the overflow gap 313 is respectively communicated with the compression chamber 111 and the recovery chamber 112.

[0373] In addition, it should be noted that the overflow notch 3133 and the overflow hole 339 on the overflow valve piece 330 have the same effect, and at least one of the overflow valve body 310, the overflow valve seat 320 and the overflow valve piece 330 is configured with the overflow notch 3133 or the overflow hole 339.

[0374] In this way, when the flow regulating valve 300 is in the closed valve state and the shock absorber 1 is in the compression working condition, the fluid in the compression chamber 111 can first flow to the recovery chamber 112 through the overflow hole 339 or the overflow notch 3133 in a stage, at this time, the flow of fluid from the compression chamber 111 to the recovery chamber 112 is small, the damping of the shock absorber 1 is large, and the shock absorber 1 behaves as "hard"; or when the flow regulating valve 300 is in the closed valve state and the shock absorber 1 is in the recovery working condition, the fluid in the compression chamber 111 can first flow to the compression chamber 111 through the overflow hole 339 or the overflow notch 3133 in a stage, at this time, the flow of fluid from the recovery chamber 112 to the compression chamber 111 is small, the damping of the shock absorber 1 is large, and the shock absorber 1 behaves as "hard".

[0375] In some embodiments of the present application, as shown in FIG. 9, one of the overflow valve body 310 and the overflow valve seat 320 is provided with a support column 340, and the other of the overflow valve body 310 and the overflow valve seat 320 is provided with a first elastic member 360 between the support column 340, when the flow regulating valve 300 is in the open valve state, the first elastic member 360 can push the overflow valve seat 320 and the overflow valve body 310 apart to form a gap between the overflow valve seat 320 and the overflow valve piece 330, and between the overflow valve body 310 and the overflow valve piece 330, so that the first flow channel 321 can be communicated with the recovery chamber 112 through the second flow channel 311 and / or the third flow channel 322, at this time, the fluid in the compression chamber 111 and the recovery chamber 112 can directly flow through the first flow channel 321 and the second flow channel 311 or the third flow channel 322, the flow of fluid is large, at this time, the damping of the shock absorber 1 is small, and the shock absorber 1 can behave as "soft", and the riding comfort is better.

[0376] In addition, it should be noted that the support column 340 for fixing the overflow valve core 520 and the support column 340 for fixing the first elastic member 360 can also be the same component.

[0377] As shown in FIGS. 1 and 9, the flow regulating valve 300 includes an overflow valve body 310, an overflow valve seat 320 and an overflow valve piece 330, the overflow valve piece 330 is movably arranged between the overflow valve body 310 and the overflow valve seat 320, and the overflow valve piece 330 is sleeved on the support column 340.

[0378] When the overflow valve body 310 and the overflow valve seat 320 are in abutment with the overflow valve sheet 330 respectively, the flow regulating valve 300 is closed; and when at least one of the overflow valve body 310 and the overflow valve seat 320 is separated from the overflow valve sheet 330, the flow regulating valve 300 is opened.

[0379] In some embodiments of the present application, as shown in FIG. 13 and FIG. 16, the side of the overflow valve seat 320 facing the overflow valve sheet 330 is provided with a second abutment ring table 325 and a flow guide surface 326, the second abutment ring table 325 is in abutment with the overflow valve sheet 330, and the flow guide surface 326 is located radially outward of the second abutment ring table 325.

[0380] In some embodiments of the present application, as shown in FIG. 13 and FIG. 16, the side of the overflow valve seat 320 facing the overflow valve sheet 330 is provided with a second abutment ring table 325 and a flow guide surface 326, the second abutment ring table 325 is in abutment with the overflow valve sheet 330, and the flow guide surface 326 is located radially outward of the second abutment ring table 325.

[0381] In some embodiments of the present application, as shown in FIG. 13 and FIG. 16, the side of the overflow valve seat 320 facing the overflow valve sheet 330 is provided with a second abutment ring table 325 and a flow guide surface 326, the second abutment ring table 325 is in abutment with the overflow valve sheet 330, and the flow guide surface 326 is located radially outward of the second abutment ring table 325.

[0382] In some embodiments of the present application, as shown in FIG. 13 and FIG. 16, the side of the overflow valve seat 320 facing the overflow valve sheet 330 is provided with a second abutment ring table 325 and a flow guide surface 326, the second abutment ring table 325 is in abutment with the overflow valve sheet 330, and the flow guide surface 326 is located radially outward of the second abutment ring table 325.

[0383] In some embodiments of the present application, as shown in FIG. 13 and FIG. 16, the side of the overflow valve seat 320 facing the overflow valve sheet 330 is provided with a second abutment ring table 325 and a flow guide surface 326, the second abutment ring table 325 is in abutment with the overflow valve sheet 330, and the flow guide surface 326 is located radially outward of the second abutment ring table 325.

[0384] In some embodiments of the present application, as shown in FIG. 10, the radial thickness of the second abutment ring table 325 along the radial direction of the overflow valve seat 320 is T, and T satisfies: T≤0.2mm. In this way, a relatively small flow resistance can be ensured.

[0385] Further, as shown in FIG. 10, the radial thickness of the second abutment ring table 325 along the radial direction of the overflow valve seat 320 is T, and T satisfies: T≥0.15mm. For example, the radial thickness of the second abutment ring table 325 can be 0.16mm, 0.17mm, 0.18mm, 0.19mm or 0.2mm. In this way, the part cost can be relatively low and the structural strength can be relatively high.

[0386] It should be noted that the thickness T of the second abutting ring table 325 and X and Y will affect the flow area of the fluid between the second abutting ring table 325 and the overflow valve piece 330, that is, will affect the flow area of the fluid at the third flow channel 322. According to Bernoulli's principle, under the same flow line, the greater the flow rate, the smaller the pressure, resulting in an increase in the pressure difference of the overflow valve piece 330, making it difficult for the overflow valve piece 330 to open under the action of fluid force, and easy to produce "adsorption" effect, affecting the consistency of the damping force and the design value, therefore, the smaller the thickness size T of the second abutting ring table 325, the better, in order to ensure the strength and durability, at least the thickness T of the second abutting ring table 325≥10 / material yield strength, for steel, the thickness value T of the second abutting ring table 325 is more appropriate to be 0.15mm or more, and T is too small to require precise machining tolerance of the part, and the manufacturing cost of the part is high.

[0387] Therefore, by limiting T≤0.2mm, it can avoid that the radial thickness of the second abutting ring table 325 is too large, and further can avoid that the adsorption force of the overflow valve seat 320 and the overflow valve piece 330 is too large, so as to facilitate the opening of the overflow valve piece 330.

[0388] And by limiting T≥0.15mm, it can avoid that the radial thickness of the second abutting ring table 325 is too small, so as to ensure that the structural strength of the second abutting ring table 325 can be high, and avoid damage to the overflow valve seat 320.

[0389] In some embodiments of the present application, as shown in FIG. 16, in the direction of the radial outward of the overflow valve seat 320, the distance A between the outer circumferential surface of the overflow valve piece 330 and the outer circumferential surface of the second abutting ring table 325 is 0.15mm≤A≤0.5mm.

[0390] For example, the distance A between the outer circumferential surface of the overflow valve piece 330 and the outer circumferential surface of the second abutting ring table 325 can be 0.15mm, 0.2mm, 0.25mm, 0.3mm, 0.35mm, 0.4mm, 0.45mm or 0.5mm.

[0391] In this way, on the one hand, it can avoid that the distance A between the outer circumferential surface of the overflow valve piece 330 and the outer circumferential surface of the second abutting ring table 325 is too small, and the machining precision of the overflow valve piece 330 and the overflow valve seat 320 can be relatively low, which is beneficial to save the manufacturing cost of the parts, and when the flow regulating valve 300 is in the closed valve state and the shock absorber 1 is in the compression working condition, the fluid can flow along the guide surface 326 to the side of the outer edge of the overflow valve piece 330 facing the overflow valve seat 320, so as to facilitate the opening of the overflow valve piece 330, and on the other hand, it can avoid that the distance A between the outer circumferential surface of the overflow valve piece 330 and the outer circumferential surface of the second abutting ring table 325 is too large, and further can avoid that the outer diameter of the overflow valve piece 330 is too large, which is convenient for assembly.

[0392] In addition, the side of the overflow valve plate 330 facing the overflow valve seat 320 extends radially outward beyond the peripheral surface of the second abutting ring platform 325, so that when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the compression working condition, fluid can flow along the flow guide surface 326 to the side of the outer edge of the overflow valve plate 330 facing the overflow valve seat 320, so as to push the overflow valve plate 330.

[0393] For example, the included angle between the flow guide surface 326 and the central axis of the overflow valve seat 320 can be 10°-90°, preferably, the included angle between the flow guide surface 326 and the central axis of the overflow valve seat 320 is 35°-55°, so as to ensure that the structural strength of the overflow valve seat 320 is high, and the fluid can flow along the flow guide surface 326 and push the overflow valve plate 330.

[0394] In addition, when the flow regulating valve 300 is in the closed state, the overflow valve body 310 and the overflow valve plate 330 abut against the overflow valve seat 320, the smaller the axial dimension of the second abutting ring platform 325 along the overflow valve seat 320, the greater the flow resistance, which is difficult to meet the requirements of the flow regulating valve 300 on the flow resistance, and when the axial dimension of the second abutting ring platform 325 along the overflow valve seat 320 is large, the strength of the second abutting ring platform 325 with thin wall thickness will be low. Therefore, the axial dimension of the second abutting ring platform 325 along the overflow valve seat 320 in the embodiment can be 0.4-0.6 mm, so as to ensure good part strength and very small flow resistance.

[0395] In some specific embodiments of the present application, as shown in FIG. 32, the flow guide surface 326 includes a first stepped surface 328 and a second stepped surface 329.

[0396] In the present application, the first stepped surface 328 is a reinforcing step.

[0397] The first stepped surface 328 is connected to the radially outer side of the second abutting ring platform 325 and extends along the radial direction of the overflow valve seat 320, and the second abutting ring platform 325 extends beyond the first stepped surface 328 towards the direction close to the overflow valve plate 330, and the second stepped surface 329 is connected to the radially outer side of the first stepped surface 328 and extends along the radial direction of the overflow valve seat 320, and the first stepped surface 328 extends beyond the second stepped surface 329 towards the direction close to the overflow valve plate 330. In this way, the structural strength of the second abutting ring platform 325 can be improved by using the first stepped surface 328, and the second abutting ring platform 325 is not easy to be deformed and damaged, and the contact area between the second abutting ring platform 325 and the overflow valve plate 330 can be smaller, avoiding that the up-down pressure difference of the overflow valve plate 330 is too large.

[0398] The second abutting ring platform 325 is arranged on the side of the overflow valve seat 320 facing the overflow valve plate 330 of the shock absorber 1, and the flow guide surface 326 is arranged on the side of the overflow valve seat 320 facing the overflow valve plate 330, and the flow guide surface 326 is located radially outward of the second abutting ring platform 325.

[0399] In this way, the overflow valve seat 320 can abut against the overflow valve plate 330 through the second abutting ring platform 325, and the flow guide surface 326 can be spaced apart from the overflow valve plate 330. By arranging the flow guide surface 326 radially outward of the second abutting ring platform 325, the flow guide surface 326 can be used to reduce the fluid flow resistance between the overflow valve seat 320 and the overflow valve plate 330. In this way, when the flow regulating valve 300 is in the open state, the fluid flowing between the overflow valve seat 320 and the overflow valve plate 330 can be guided by the flow guide surface 326, so as to adjust the fluid flow between the overflow valve seat 320 and the overflow valve plate 330, and further adjust the damping force of the shock absorber 1.

[0400] In this way, the overflow valve seat 320 according to the embodiment of the present application can reduce the fluid flow resistance of the fluid flowing through the flow regulating valve 300, so as to adjust the fluid flow through the flow regulating valve 300, and further adjust the damping force of the shock absorber 1.

[0401] In another specific embodiment of the present application, as shown in FIG. 31, the flow guide surface 326 includes a third stepped surface 3262 and an inclined surface 3261.

[0402] The third stepped surface 3262 is connected to the radially outer side of the second abutting ring platform 325 and extends along the radial direction of the overflow valve seat 320, and the second abutting ring platform 325 extends beyond the third stepped surface 3262 towards the overflow valve plate 330. The inclined surface 3261 is connected to the radially outer side of the third stepped surface 3262 and extends outward along the radial direction of the overflow valve seat 320, and the inclined surface 3261 gradually moves away from the overflow valve plate 330.

[0403] In this way, the distance between the inclined surface 3261 and the overflow valve plate 330 gradually increases along the radial direction of the overflow valve seat 320, further reducing the fluid flow resistance between the inclined surface 3261 and the overflow valve plate 330, and the fluid flow is more smooth, and the flow guide effect of the flow guide surface 326 on the fluid is better.

[0404] In some specific embodiments of the present application, as shown in FIG. 31, the flow guide surface 326 comprises a slope surface 3261 connected to the radially outer side of the second abutting ring platform 325, and gradually away from the spill valve plate 330 in the radially outward direction of the spill valve seat 320. In the axial direction of the spill valve seat 320, the end of the slope surface 3261 adjacent to the spill valve plate 330 is flush with the end of the second abutting ring platform 325 facing the spill valve plate 330. In this way, not only can the fluid be guided by the slope surface 3261 to reduce the flow resistance of the fluid, but the end of the slope surface 3261 adjacent to the spill valve plate 330 can be spaced apart from the spill valve plate 330, so that the spacing between the slope surface 3261 and the spill valve plate 330 can be set to be larger, further reducing the flow resistance of the fluid flowing between the slope surface 3261 and the spill valve plate 330, and the fluid flow is more unobstructed.

[0405] In some specific embodiments of the present application, as shown in FIG. 31, the flow guide surface 326 comprises a slope surface 3261 connected to the radially outer side of the second abutting ring platform 325, and gradually away from the spill valve plate 330 in the radially outward direction of the spill valve seat 320. In the axial direction of the spill valve seat 320, the end of the slope surface 3261 adjacent to the spill valve plate 330 is flush with the end of the second abutting ring platform 325 facing the spill valve plate 330. In this way, not only can the fluid be guided by the slope surface 3261 to reduce the flow resistance of the fluid, but the end of the slope surface 3261 adjacent to the spill valve plate 330 can be spaced apart from the spill valve plate 330, so that the spacing between the slope surface 3261 and the spill valve plate 330 can be set to be larger, further reducing the flow resistance of the fluid flowing between the slope surface 3261 and the spill valve plate 330, and the fluid flow is more unobstructed.

[0406] In some specific embodiments of the present application, as shown in FIGS. 29-34, in the axial direction of the spill valve seat 320 towards the spill valve plate 330, the second abutting ring platform 325 exceeds the end of the flow guide surface 326 adjacent to the spill valve plate 330 by a size B, and B satisfies: 0.4mm≤B≤0.6mm. For example, B can be 0.4mm, 0.45mm, 0.5mm, 0.55mm or 0.6mm.

[0407] In this way, on the one hand, it can avoid that the size B of the second abutting ring platform 325 exceeding the end of the flow guide surface 326 adjacent to the spill valve plate 330 is too small, that is, it can avoid that the gap between the flow guide surface 326 and the spill valve plate 330 is too small, so as to ensure that the flow resistance of the fluid flowing between the flow guide surface 326 and the spill valve plate 330 can be smaller, on the other hand, it can avoid that the size B of the second abutting ring platform 325 exceeding the end of the flow guide surface 326 adjacent to the spill valve plate 330 is too large, that is, it can avoid that the length of the valve seat abutting ring body 325 is too long, so that the structural strength of the second abutting ring platform 325 can be higher, and the second abutting ring platform 325 is not easy to deform and damage.

[0408] In some embodiments of the present application, as shown in FIGS. 29-34, the angle between the inclined surface 3261 and the overflow valve plate 330 is β, which satisfies: 35°≤β≤55°. In this way, the structural strength of the overflow valve seat 320 can be higher, and the inclined surface 3261 has a better fluid guiding effect, the fluid flow resistance can be smaller, the flow is more smooth, and the fluid can flow along the guiding surface 326 and push the overflow valve plate 330.

[0409] In some embodiments, as shown in FIG. 29, the guiding surface 326 can extend from the end of the second abutting ring table 325 away from the overflow valve plate 330 to the outer circumferential surface of the overflow valve seat 320.

[0410] Alternatively, as shown in FIG. 30, the end of the overflow valve seat 320 facing the overflow valve plate 330 can also be configured as a straight edge structure, and a guiding inclined surface 326 is provided on the outer edge of the overflow valve seat 320, that is, the guiding inclined surface 326 and the second abutting ring table 325 can be connected by a straight edge transition.

[0411] Further alternatively, as shown in FIG. 31, the guiding surface 326 can extend from the end of the second abutting ring table 325 facing the overflow valve plate 330 to the outer circumferential surface of the overflow valve seat 320.

[0412] Further alternatively, as shown in FIG. 32, the outer circumferential surface of the second abutting ring table 325 can be configured with a reinforcing step 328, so that the structural strength of the second abutting ring table 325 can be improved by the reinforcing step 328, and the contact area between the second abutting ring table 325 and the overflow valve plate 330 can be smaller, avoiding excessive pressure difference on the overflow valve plate 330.

[0413] In some embodiments of the present application, as shown in FIG. 1, the piston 200 includes a piston rod 210, a piston valve assembly 220, and a valve body 230.

[0414] The piston valve assembly 220 divides the compression chamber 111 and the recovery chamber 112 in the cylinder body 100, the piston valve assembly 220 and the piston rod 210 are connected through the valve body 230, the overflow valve body 310 and the overflow valve seat 320 are installed in the valve body 230, and the control valve 400 extends into the valve body 230 and cooperates with the flow regulating valve 300.

[0415] For example, the piston valve assembly 220 can be sleeved on the outer circumferential surface of the valve body 230 and threadedly connected with the outer circumferential surface of the valve body 230, and the piston rod 210 is sleeved on the outer circumferential surface of the valve body 230 and threadedly connected with the outer circumferential surface of the valve body 230.

[0416] By dividing the piston 200 into the piston rod 210 and the piston valve body 230, the installation of the control valve 400 and the flow regulating valve 300 is more convenient, and the piston valve assembly 220 and the piston rod 210 are connected through the valve body 230, which is convenient for disassembly and assembly.

[0417] Further, as shown in FIG. 1 and FIG. 9, the overflow valve seat 320 is arranged in the valve body 230, and the overflow valve body 310 and the valve body 230 define a first chamber 241 and a second chamber 242, and the control valve 400 extends into the second chamber 242 to control the opening and closing of the first chamber 241 and the second chamber 242.

[0418] The fourth flow channel 243 and the fifth flow channel 251 are arranged on the side wall of the valve body 230, the fourth flow channel 243 is in communication with the first chamber 241 and the recovery chamber 112 respectively, and one end of the fifth flow channel 251 is in communication with the recovery chamber 112, and the other end is in communication with the second flow channel 311 and the third flow channel 322 respectively.

[0419] The third chamber 253 can be formed between the fifth flow channel 251 and the overflow valve body 310 and the overflow valve seat 320, and in the axial direction of the cylinder body 100, the third chamber 253 and the first chamber 241 are arranged on both sides of the overflow valve body 310, specifically, the first chamber 241 is located on the side of the overflow valve body 310 away from the overflow valve seat 320, and the third chamber 253 is located on the side of the overflow valve body 310 facing the overflow valve seat 320.

[0420] It can be understood that when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the recovery working condition, the fluid flow from the fifth flow channel 251 into the third chamber 253 and from the overflow hole 339 or the overflow gap 3133 to the compression chamber 111 is small, at this time, the pressure in the third chamber 253 will rise sharply, and the fluid flow from the fourth flow channel 243 into the first chamber 241 and from the sixth flow channel 314, the second chamber 242 and the seventh flow channel 315 into the compression chamber 111 is large, that is, the pressure in the first chamber 241 will be less than the pressure in the third chamber 253, so that the fluid in the first chamber 241 can push the overflow valve body 310 to move away from the overflow valve seat 320 to open the second flow channel 311.

[0421] In this way, the fluid in the recovery chamber 112 can flow into the first chamber 241 through the fourth flow channel 243, and when the second flow channel 311 and / or the third flow channel 322 are opened, the fluid in the compression chamber 111 can flow to the second flow channel 311 and / or the third flow channel 322 through the first flow channel 321, to the fifth flow channel 251 through the second flow channel 311 and / or the third flow channel 322, and into the recovery chamber 112.

[0422] And, as shown in FIG. 1, FIG. 9 and FIG. 22, the overflow valve body 310 is configured with a sixth flow passage 314 and a seventh flow passage 315.

[0423] One end of the sixth flow passage 314 is in communication with the first chamber 241, the other end of the sixth flow passage 314 is in communication with the second chamber 242 and the control valve 400 is fitted to the other end of the sixth flow passage 314, the seventh flow passage 315 extends through opposite sides of the overflow valve body 310 along the axial direction of the overflow valve body 310, one end of the seventh flow passage 315, which is away from the overflow valve seat 320, is in communication with the second chamber 242, and the other end of the seventh flow passage 315 is in communication with the first flow passage 321, the fluid flow of the sixth flow passage 314 and the fluid flow of the seventh flow passage 315 are controlled by opening and closing of the control valve 400.

[0424] For example, as shown in FIG. 19, the sixth flow passage 314 can include a radial section 314a and an axial section 314b, the radial section 314a extends along the radial direction of the overflow valve body 310, and one end of the radial section 314a penetrates through the outer circumferential surface of the overflow valve body 310, the axial section 314b extends along the axial direction of the overflow valve body 310, one end of the axial section 314b is connected to the other end of the radial section 314a, and the other end of the axial section 314b penetrates through the side of the overflow valve body 310 which faces the pilot valve 600.

[0425] In this way, one end of the radial section 314a can be in communication with the first chamber 241, and the other end of the axial section 314b and one end of the seventh flow passage 315, which faces the spool assembly 500, can be in communication with the second chamber 242, when the control valve 400 is in sealing fit with the other end of the axial section 314b, the sixth flow passage 314 and the seventh flow passage 315 are disconnected, at this time the first flow passage 321 cannot be in communication with the compression chamber 111 through the sixth flow passage 314 and the seventh flow passage 315; and when the control valve 400 is separated from the other end of the axial section 314b, the sixth flow passage 314 and the seventh flow passage 315 are connected, at this time the first flow passage 321 can be in communication with the compression chamber 111 through the sixth flow passage 314 and the seventh flow passage 315.

[0426] Therefore, when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the rebound working condition, when the pressure in the first chamber 241 is relatively large, the fluid in the first chamber 241 can push the control valve 400 away through the sixth flow passage 314, at this time the fluid in the first chamber 241 can flow into the second chamber 242 through the sixth flow passage 314, and then can flow to the compression chamber 111 through the seventh flow passage 315, at this time the fluid flow is relatively large, and the shock absorber 1 behaves as "soft".

[0427] In some embodiments of the present application, as shown in FIG. 1 and FIG. 9, the overflow valve body 310 is provided with a sealing groove 316 on the side opposite to the overflow valve seat 320, the valve body 230 is provided with a sealing ring platform 244, and the sealing ring platform 244 is spaced apart from the inner side wall of the valve body 230 in the radial direction of the cylinder body 100, the overflow valve body 310 is in dynamic sealing cooperation with the inner side wall of the valve body 230, and the sealing groove 316 is in dynamic sealing cooperation with the outer side wall of the sealing ring platform 244.

[0428] The inner side wall of the valve body 230, the outer side wall of the sealing ring platform 244 and the overflow valve body 310 define a first chamber 241, and the inner side wall of the sealing ring platform 244 and the overflow valve body 310 define a second chamber 242.

[0429] In this way, the first chamber 241 and the second chamber 242 do not interfere with each other in position, and when the control valve 400 controls the sixth flow passage 314 and the seventh flow passage 315 to be disconnected, the second chamber 242 can be disconnected from the first chamber 241, at which time the fluid in the recovery chamber 112 and the compression chamber 111 cannot flow through the sixth flow passage 314 and the seventh flow passage 315; when the fluid pressure in the first chamber 241 is relatively large, the fluid in the first chamber 241 can push away the control valve 400 through the sixth flow passage 314, so that the first chamber 241 is in communication with the second chamber 242, at which time the fluid in the recovery chamber 112 and the compression chamber 111 can flow through the sixth flow passage 314 and the seventh flow passage 315.

[0430] Further, as shown in FIG. 1 and FIG. 9, the valve body 230 includes an upper valve body 240 and a lower valve body 250.

[0431] Specifically, the upper valve body 240 is connected to the piston rod 210, the lower valve body 250 is connected between the piston valve assembly 220 and the upper valve body 240, and the overflow valve seat 320 is arranged in the lower valve body 250. By dividing the valve body 230 into the upper valve body 240 and the lower valve body 250, the structure of the valve body 230 can be simplified, the machining and manufacturing of the valve body 230 are facilitated, and the assembly of the piston rod 210, the upper valve body 240, the lower valve body 250, the piston valve assembly 220 and the flow regulating valve 300 is more simple and convenient.

[0432] In addition, the overflow valve body 310 and the upper valve body 240 define the first chamber 241 and the second chamber 242. The first chamber 241 can be formed between the outer peripheral surface of the overflow valve body 310 and the inner peripheral wall of the upper valve body 240.

[0433] The side wall of the upper valve body 240 is provided with a fourth flow channel 243, and the side wall of the lower valve body 250 is provided with a fifth flow channel 251. In this way, the fluid in the recovery cavity 112 can flow into the first chamber 241 through the fourth flow channel 243, and when the second flow channel 311 and / or the third flow channel 322 are opened, the fluid in the compression cavity 111 can flow to the second flow channel 311 and / or the third flow channel 322 through the first flow channel 321, to the fifth flow channel 251 through the second flow channel 311 and / or the third flow channel 322, and into the recovery cavity 112.

[0434] Optionally, the upper valve body 240 is provided with a sealing ring platform 244.

[0435] In some embodiments of the present application, the control valve 400 comprises a spool assembly 500 and a pilot valve 600.

[0436] The spool assembly 500 is movably arranged in the piston 200, the pilot valve 600 is connected to the spool assembly 500, and the spool assembly 500 controls the flow regulating valve 300 through the pilot valve 600, for example, when moving, controls the flow regulating valve 300 through the pilot valve 600, to adjust the fluid flow between the compression cavity 111 and the recovery cavity 112. In this way, by moving the spool assembly 500, the fluid flow between the compression cavity 111 and the recovery cavity 112 can be controlled, so that when the spool assembly 500 moves the same distance, the heat generated by the fluid due to friction is different, to change the damping effect of the shock absorber 1.

[0437] In some embodiments of the present application, as shown in FIGS. 43-62, the pilot valve 600 comprises a first body portion 610.

[0438] The first body portion 610 is connected to the spool assembly 500, and the first body portion 610 is provided with at least one first balance hole 611 and a sealing protrusion 612, the sealing protrusion 612 is arranged on the side of the first body portion 610 facing the flow regulating valve 300, and the sealing protrusion 612 cooperates with the flow regulating valve 300.

[0439] The flow regulating valve 300 comprises an overflow valve body 310, the overflow valve body 310 is movably arranged in the piston 200, and the overflow valve body 310 is configured with a sixth flow channel 314 and a seventh flow channel 315, the pilot valve 600 cooperates with the sixth flow channel 314 through the sealing protrusion 612, to control the opening and closing of the sixth flow channel 314 and the seventh flow channel 315.

[0440] Part of the sealing protrusion 612 can extend into the sixth flow channel 314, to control the opening and closing of the sixth flow channel 314 and the size of the opening and closing of the sixth flow channel 314, and thus the fluid flow through the sixth flow channel 314 of the flow regulating valve 300 can be controlled.

[0441] Specifically, one end of the sixth flow passage 314 is in communication with the first chamber 241, the other end of the sixth flow passage 314 is in communication with the second chamber 242 and the control valve 400 is fitted to the other end of the sixth flow passage 314, the seventh flow passage 315 penetrates through opposite sides of the overflow valve body 310 along the axial direction of the overflow valve body 310, one end of the seventh flow passage 315, which is away from the overflow valve seat 320, is in communication with the second chamber 242, and the other end of the seventh flow passage 315 is in communication with the first flow passage 321, and the fluid flow of the sixth flow passage 314 and the fluid flow of the seventh flow passage 315 are controlled by opening and closing of the control valve 400.

[0442] In this way, when the fluid flows from the sixth flow passage 314 into the second chamber 242, the fluid is blocked by the first body portion 610 and flows towards the direction of the overflow valve body 310, so that the fluid flowing out of the sixth flow passage 314 can quickly flow to the seventh flow passage 315, and then flow to the compression chamber 111 through the seventh flow passage 315, which is conducive to improving the flow speed of the fluid flowing from the recovery chamber 112 to the compression chamber 111.

[0443] In addition, by providing the first balance hole 611 on the first body portion 610, the impact force of the fluid flowing out of the sixth flow passage 314 on the pilot valve 600 can be reduced, so that the impact force of the fluid on the valve core assembly 500 can be reduced, so that the damping force of the shock absorber 1 can be kept stable, and the ride comfort of the vehicle is further improved.

[0444] For example, the first balance hole 611 can be multiple, and the multiple first balance holes 611 can extend along the circumference of the first body portion 610.

[0445] In this way, the pilot valve 600 according to the embodiments of the present application can block and guide the fluid by using the first flow guide portion 620, which is conducive to improving the flow speed of the fluid flowing from the recovery chamber 112 to the compression chamber 111, and making the fluid flow more stable, and the damping force of the shock absorber 1 is more stable.

[0446] In some embodiments of the present application, as shown in FIGS. 43 and 45, the first body portion 610 is further provided with a guide rod connecting groove 639, the guide rod connecting groove 639 is provided on the side of the first body portion 610 facing the valve core assembly 500, and the valve core assembly 500 is connected to the guide rod connecting groove 639.

[0447] Specifically, the guide rod connecting groove 639 can be connected with the guide rod 530 of the valve core assembly 500, so that the pilot valve 600 and the guide rod 530 of the valve core assembly 500 can be connected together, so as to realize the connection and fixation of the pilot valve 600 and the guide rod 530, and the pilot valve 600 and the guide rod 530 move together.

[0448] In some embodiments of the present application, as shown in FIG. 9, the first body portion 610 projects onto the spill valve body 310 in the axial direction of the cylinder body 100 to cover at least a portion of the seventh flow passage 315. In other words, at least a portion of the seventh flow passage 315 is located directly below the first body portion 610. In this way, the fluid can flow in the direction of the spill valve body 310 under the blocking and guiding of the first body portion 610 and the first guide portion 620, and the fluid can flow more smoothly into the seventh flow passage 315.

[0449] In some embodiments of the present application, as shown in FIG. 60 and FIG. 45, the sealing protrusion 612 is configured to be a truncated cone with decreasing cross-sectional area in the axial direction of the pilot valve 600 extending away from the body portion 610.

[0450] That is, the cross-sectional area of the sealing protrusion 612 can gradually decrease in the axial direction of the pilot valve 600 approaching the flow regulating valve 300. This arrangement can facilitate the assembly of the sealing protrusion 612 into the sixth flow passage 314 and seal with the sixth flow passage 314 on the one hand, and guide the fluid flowing out of the sixth flow passage 314 on the other hand, so as to make the fluid flow more smoothly and improve the stability of the damping force of the shock absorber 1.

[0451] In addition, this arrangement can also improve the versatility of the pilot valve 600, and the sealing protrusion 612 can be adapted to a variety of sixth flow passages 314 with different inner diameters, thereby enabling the pilot valve 600 to be adapted to a variety of flow regulating valves 300 with higher versatility.

[0452] In some embodiments of the present application, as shown in FIG. 13 and FIG. 14, the flow regulating valve 300 includes a spill valve body 310, the spill valve body 310 is provided with a sixth flow passage 314 and a seventh flow passage 315, the sixth flow passage 314 is in communication with the rebound chamber 112, and the seventh flow passage 315 is in communication with the compression chamber 111.

[0453] The sealing protrusion 612 of the pilot valve 600 cooperates with the sixth flow passage 314 to control the opening and closing of the sixth flow passage 314 and the seventh flow passage 315.

[0454] Specifically, one end of the sixth flow passage 314 can be in communication with one end of the seventh flow passage 315, the other end of the sixth flow passage 314 is in communication with the rebound chamber 112, the other end of the seventh flow passage 315 is in communication with the compression chamber 111, the control valve 400 cooperates with the other end of the sixth flow passage 314 to control the opening and closing of the sixth flow passage 314 and the seventh flow passage 315, the seventh flow passage 315 can extend through the opposite sides of the spill valve body 310 in the axial direction of the spill valve body 310, and the fluid flow of the sixth flow passage 314 and the fluid flow of the seventh flow passage 315 are controlled by the opening and closing of the pilot valve 600.

[0455] In some embodiments of the present application, as shown in FIGS. 43-62, the body portion 610 is further provided with a first balance hole 611, which penetrates the body portion 610 along the axial direction of the pilot valve 600 and is located between the first flow guide portion 620 and the sealing protrusion 612 along the radial direction of the body portion 610.

[0456] By providing the first balance hole 611 on the body portion 610, part of the fluid flowing out of the sixth flow passage 314 can flow upward through the first balance hole 611, thereby reducing the impact force of the fluid flowing out of the sixth flow passage 314 on the pilot valve 600, so as to reduce the impact force of the fluid on the valve core assembly 500, so that the damping force of the shock absorber 1 can remain stable, which is conducive to improving the ride comfort of the vehicle.

[0457] In some embodiments of the present application, as shown in FIGS. 43-62, the first balance hole 611 is a plurality of first balance holes 611, and the plurality of first balance holes 611 are arranged in a spaced manner along the circumferential direction of the body portion 610. In this way, the fluid can be discharged upward through the plurality of first balance holes 611 at the same time, further reducing the impact force of the fluid on the pilot valve 600, and the buffering effect is better.

[0458] In some embodiments of the present application, as shown in FIGS. 43-62, the sealing protrusion 612 protrudes from the first flow guide portion 620 along the axial direction of the pilot valve 600.

[0459] That is, the sealing protrusion 612 can protrude beyond the first flow guide portion 620 along the axial direction of the pilot valve 600 close to the flow regulating valve 300, so that the extension size of the sealing protrusion 612 along the axial direction of the pilot valve 600 can be larger, and when the sealing protrusion 612 cooperates with the flow regulating valve 300, the first flow guide portion 620 will not interfere with the position of the flow regulating valve 300, and the structure is more reasonable, so that at least part of the sealing protrusion 612 extends into the sixth flow passage 314 to control the flow rate of the fluid flowing through the sixth flow passage 314.

[0460] In some embodiments of the present application, as shown in FIG. 45, a body flow guide surface 613 is formed between the sealing protrusion 612 and the first flow guide portion 620 on the side surface of the first body portion 610 facing the flow regulating valve 300.

[0461] Among them, the body flow guide surface 613 can play a role of transition connection, which is conducive to improving the overall structural strength of the pilot valve 600, and the body flow guide surface 613 can also guide the fluid flowing out of the sixth flow passage 314, further improving the smoothness of the fluid flow, and the stability of the damping force of the shock absorber 1 is better.

[0462] Further, as shown in FIG. 45, the body flow guide surface 613 is configured as a frustoconical surface with a decreasing cross-sectional area along the axial direction of the pilot valve 600 away from the body portion 610.

[0463] That is, the cross-sectional area of the body flow guide surface 613 can also gradually decrease along the axial direction of the pilot valve 600 towards the flow regulating valve 300, so that the body flow guide surface 613 can smoothly transition the body portion 610 and the sealing protrusion 612, and the sealing protrusion 612 and the body flow guide surface 613 can better guide the fluid when the fluid flowing out of the sixth flow passage 314 impacts the pilot valve 600, so as to make the fluid flow in the shock absorber 1 more smooth.

[0464] In some embodiments of the present application, as shown in FIGS. 43-44, the first flow guide portion 620 is configured as a circular ring extending along the circumferential direction of the outer periphery of the body portion 610. In this way, the annular first flow guide portion 620 can stop and guide the fluid in any radial direction of the body portion 610, which is conducive to improving the stopping and guiding effect of the first flow guide portion 620 on the fluid, so that most of the fluid can quickly flow to the compression chamber 111.

[0465] Further, the first body portion 610 projects on the overflow valve body 310 in the axial direction of the cylinder 100 and covers at least part of the seventh flow passage 315. In this way, the fluid can better flow into the seventh flow passage 315 under the stopping of the first body portion 610, so as to make the fluid flow more smooth.

[0466] The first body portion 610 is adapted to be connected with the spool assembly 500 of the shock absorber 1, and the first body portion 610 is adapted to cooperate with the flow regulating valve 300 of the shock absorber 1, the first flow guide portion 620 extends along the circumferential direction of the first body portion 610 and extends from the outer periphery of the first body portion 610 to the side close to the flow regulating valve 300.

[0467] According to the pilot valve 600 of the embodiment of the present application, by connecting the first body portion 610 with the spool assembly 500, when the spool assembly 500 moves, the spool assembly 500 can drive the pilot valve 600 to move, or when the fluid drives the pilot valve 600 to move away from the flow regulating valve 300, the pilot valve 600 can also drive the spool assembly 500 to move, thereby adjusting the fluid flow of the flow regulating valve 300.

[0468] Further, the first flow guide portion 620 extends along the circumference of the first body portion 610 and extends from the outer periphery of the first body portion 610 to the side close to the flow regulating valve 300. In this way, when the fluid flows out of the flow regulating valve 300, the fluid is first blocked by the body portion 610 and flows radially outward along the first body portion 610, and then the first flow guide portion 620 can block the fluid and guide the fluid in the direction of the flow regulating valve 300, so that the fluid flowing out of the recovery cavity 112 through the flow regulating valve 300 can quickly flow through the flow regulating valve 300 to the compression cavity 111, which is conducive to improving the flow speed of the fluid flowing from the recovery cavity 112 to the compression cavity 111.

[0469] Specifically, when the fluid flows from the sixth flow passage 314 to the pilot valve 600, the fluid is first blocked by the body portion 610 and flows radially outward along the body portion 610, and then the flow guide portion 620 can block the fluid and guide the fluid in the direction of the relief valve body 310, so that the fluid flowing out of the sixth flow passage 314 can quickly flow to the seventh flow passage 315 to flow to the compression cavity 111 through the seventh flow passage 315, which is conducive to improving the flow speed of the fluid flowing from the recovery cavity 112 to the compression cavity 111.

[0470] In some embodiments of the present application, as shown in FIGS. 43-62, the pilot valve 600 further comprises a first flow guide portion 620, the first flow guide portion 620 extends along the circumference of the first body portion 610, and the first flow guide portion 620 extends from the outer periphery of the first body portion 610 to the side close to the flow regulating valve 300, and the first balance hole 611 is located between the first flow guide portion 620 and the sealing protrusion 612.

[0471] In this way, when the fluid flows into the second chamber 242 from the sixth flow passage 314, the fluid is first blocked by the first body portion 610 and flows radially outward, and then the first flow guide portion 620 can block the fluid and guide the fluid in the direction of the relief valve body 310, so that the fluid flowing out of the sixth flow passage 314 can quickly flow to the seventh flow passage 315 to flow to the compression cavity 111 through the seventh flow passage 315, which is conducive to improving the flow speed of the fluid flowing from the recovery cavity 112 to the compression cavity 111.

[0472] In addition, in the radial direction of the first body portion 610, the outer side of the first balance hole 611 does not exceed the inner side wall of the first flow guide portion 620.

[0473] In some embodiments of the present application, the inner diameter of the end of the sixth flow passage 314 towards the pilot valve 600 is d1, the radial outer side of the sealing protrusion 612 and the axial direction of the cylinder body 100 form an angle of, and in the axial direction of the cylinder body 100, the first flow guide portion 620 exceeds the length of the first body portion 610 in the direction close to the relief valve body 310 by h, and the inner diameter of the first flow guide portion 620 is d2.

[0474] wherein H, d1 and d2 satisfy: h.

[0475] In this way, when the fluid flows out of the sixth flow passage 314 of the overflow valve body 320 at a high speed, the first flow guide portion 620 can be used more effectively to stop and guide the fluid, i.e., the fluid impact can be better alleviated by the first flow guide portion 620, and the fluid flow stability can be more effectively improved.

[0476] Specifically, by limiting h, the length of the first flow guide portion 620 extending beyond the first body portion 610 in the direction close to the overflow valve body 310 can be longer, and the fluid flowing out of the sixth flow passage 314 can flow to the flow guide portion 620 after sequentially impacting the sealing protrusion 612 and the first body portion 610, at which time most of the fluid rebounded by the first body portion 610 can be stopped by the flow guide portion 620, so that the flow guide portion can guide most of the fluid, and the flow guiding effect of the first flow guide portion 620 can be better.

[0477] In some other specific embodiments of the present application, as shown in FIGS. 43-62, the pilot valve 600 includes a base 630, a pilot valve plug 640, and a second elastic member 650.

[0478] The base 630 is connected to the spool assembly 500, the pilot valve plug 640 is arranged on the side of the base 630 facing the flow regulating valve 300 and is movable relative to the base 630, and the pilot valve plug 640 cooperates with the flow regulating valve 300, and the second elastic member 650 is arranged between the base 630 and the pilot valve plug 640 to provide an elastic force of the pilot valve plug 640 away from the base 630.

[0479] According to the pilot valve 600 of the embodiments of the present application, by connecting one side of the base 630 to the spool assembly 500, when the spool assembly 500 moves, the spool assembly 500 can drive the pilot valve 600 to move, or when the fluid drives the pilot valve 600 to move away from the flow regulating valve 300, the pilot valve 600 can also drive the spool assembly 500 to move, thereby adjusting the fluid flow of the flow regulating valve 300.

[0480] Moreover, by dividing the pilot valve 600 into the base 630, the pilot valve plug 640, and the second elastic member 650, and arranging the second elastic member 650 between the base 630 and the pilot valve plug 640, when the pilot valve plug 640 moves in the direction close to the base 630, the second elastic member 650 can provide an elastic force of the pilot valve plug 640 away from the base 630.

[0481] Thus, along the axial direction of the pilot valve 600, the base 630, the pilot valve plug 640 and the second elastic member 650 can move relatively. When the shock absorber 1 is not powered or is in a low current state, the fluid flowing out of the sixth flow passage 314 can switch the pilot valve plug 640 instantaneously and multiple times, and then the impact force of the fluid can be buffered by the pilot valve plug 640 and the second elastic member 650, which is conducive to reducing the impact force of the fluid on the valve core assembly 500, so as to make the damping force of the shock absorber 1 more stable.

[0482] Thus, according to the pilot valve 600 of the embodiment of the present application, the pilot valve plug 640 can be opened and closed instantaneously and multiple times, and then the impact force of the fluid can be effectively buffered, which is conducive to reducing the impact force on the valve core assembly 500 and making the damping force of the shock absorber 1 more stable.

[0483] In some specific embodiments of the present application, as shown in FIGS. 43-62, the second elastic member 650 includes an outer ring body 651 and an inner elastic arm 652.

[0484] The outer ring body 651 abuts against the pilot valve plug 640, the outer end of the inner elastic arm 652 is connected to the outer ring body 651, and the inner end of the inner elastic arm 652 abuts against the base 630.

[0485] That is, the second elastic member 650 can adjust the position of the outer ring body 651 in the axial direction of the base 630 through the deformation of the inner elastic arm 652, so that the relative position of the pilot valve plug 640 and the base 630 can be adjusted by the second elastic member 650, the pilot valve plug 640 can move relative to the base 630, and the impact force of the fluid can be more effectively buffered by the second elastic member 650, so that the impact force of the fluid can be absorbed by the pilot valve 600, and the damping force of the shock absorber 1 is more stable.

[0486] Further, as shown in FIG. 53, the width of the inner elastic arm 652 decreases in the direction of the radial direction of the outer ring body 651.

[0487] In other words, along the radial direction of the second elastic member 650, the width of the end of the inner elastic arm 652 close to the outer ring body 651 is larger, and the width of the end of the inner elastic arm 652 away from the outer ring body 651 is smaller. By such arrangement, on the one hand, the width of part of the inner elastic arm 652 can be smaller, so that the inner elastic arm 652 can deform, and then the elastic force driving the pilot valve plug 640 away from the base 630 can be generated, and on the other hand, the width of the connection between the inner elastic arm 652 and the outer ring body 651 can be larger, which is conducive to improving the connection strength of the inner elastic arm 652 and the outer ring body 651, i.e., the overall structural strength of the second elastic member 650 can be improved, and the second elastic member 650 is not easy to be damaged and fail.

[0488] In some embodiments of the present application, as shown in FIGS. 48 and 53, the inner elastic arms 652 are multiple, and the multiple inner elastic arms 652 are arranged along the circumference of the outer ring body 651.

[0489] For example, the inner elastic arms 652 can be six, and the six inner elastic arms 652 are arranged along the circumference of the outer ring body 651.

[0490] By arranging multiple inner elastic arms 652, not only can the single inner elastic arm 652 be arranged smaller to facilitate elastic deformation of the single inner elastic arm 652, but also the multiple inner elastic arms 652 can deform simultaneously to provide an elastic force of the pilot valve plug 640 away from the base 630, thereby ensuring that the elastic force is sufficient to make the elastic force of the second elastic member 650 more stable and reliable, and the pilot valve 600 can more effectively absorb the impact force of the fluid on the valve core assembly 500.

[0491] In some embodiments of the present application, as shown in FIG. 53, the inner ends of the multiple inner elastic arms 652 are flat, and the inner ends of the multiple inner elastic arms 652 are circumscribed by the same circle. That is, the structures of the multiple inner elastic arms 652 can be arranged the same, or in other words, the lengths of the multiple inner elastic arms 652 can remain the same along the radial direction of the second elastic member 650.

[0492] In this way, not only can the structure of the multiple inner elastic arms 652 be simplified to make the structure of the second elastic member 650 simpler and facilitate processing, but also when the multiple inner elastic arms 652 deform, it can be ensured that the multiple inner elastic arms 652 can always abut against the base 630, and the deformations of the multiple inner elastic arms 652 can be consistent, further improving the stability of the elastic force generated by the second elastic member 650.

[0493] In addition, the inner end of the inner elastic arm 652 is flat, which means that the end of the inner elastic arm 652 away from the outer ring body 651 is flat. In this way, the structure of the inner elastic arm 652 can be simplified, and the end of the inner elastic arm 652 abutting against the base 630 can be flat, and the abutting area of the inner elastic arm 652 and the base 630 can be larger, which can make the abutment of the inner elastic arm 652 and the base 630 more stable and reliable.

[0494] Further, as shown in FIG. 53, the width of the inner elastic arm 652 decreases in the direction of the radial direction of the outer ring body 651 inward.

[0495] In some embodiments of the present application, within the compression range of the second elastic member 650, the pilot valve plug 640 moves relative to the base 630 along the axial direction of the base 630 between the first position and the second position, and the elastic force provided by the second elastic member 650 to the pilot valve plug 640 is 10N-50N.

[0496] For example, the elastic force provided by the second elastic member 650 to the pilot valve plug 640 can be 10 N, 15 N, 20 N, 25 N, 30 N, 35 N, 40 N, 45 N, or 50 N. In this way, on the one hand, the elastic force provided by the second elastic member 650 to the pilot valve plug 640 can be prevented from being too small to ensure that the pilot valve plug 640 can move away from the base 630 under the action of the second elastic member 650, and the buffering effect of the pilot valve 600 on the fluid is better. On the other hand, the elastic force provided by the second elastic member 650 to the pilot valve plug 640 can be prevented from being too large to make the second elastic member 650 better absorb the impact of the fluid.

[0497] In some embodiments of the present application, as shown in FIGS. 47 and 49, the base 630 further includes an annular boss 638 disposed on the side of the second body portion 631 away from the second elastic member 650, and the annular boss 638 is formed with a guide rod connecting groove 639.

[0498] That is, the annular boss 638 is disposed on the side of the second body portion 631 facing the valve core assembly 500. For example, the annular boss 638 can be disposed at the middle of the radial direction of the second body portion 631 and protrude from the side of the second body portion 631 facing the valve core assembly 500. By constructing the guide rod connecting groove 639 in the annular boss 638, the original structure of the second body portion 631 is not damaged, so that the structural strength of the second body portion 631 can be higher.

[0499] Specifically, the guide rod connecting groove 639 can be connected with the guide rod 530 of the valve core assembly 500, and thus the base 630 and the guide rod 530 of the valve core assembly 500 can be connected together to realize the connection and fixation of the pilot valve 600 and the guide rod 530, and the pilot valve 600 moves together with the guide rod 530.

[0500] In some embodiments of the present application, as shown in FIGS. 51, 61 and 62, the pilot valve plug 640 includes a plug sheet 641 and a plug head 643. The plug head 643 in the embodiment of the present application is the sealing protrusion in the priority application.

[0501] The side edge of the plug sheet 641 facing the second elastic member 650 is in abutment with the second elastic member 650 and the radially inner side thereof is formed with a plug sheet avoiding groove 642, and the plug head 643 is disposed at the middle of the side of the plug sheet 641 away from the second elastic member 650.

[0502] Specifically, the stop structure 633 can stop on the side of the plug sheet 641 away from the main body portion of the base 630, and the plug head 643 can protrude from the side of the plug sheet 641 away from the second elastic member 650. The pilot valve plug 640 can cooperate with the flow regulating valve 300 by using the plug head 643 to adjust the fluid flow of the flow regulating valve 300.

[0503] Further, by arranging the plug avoiding groove 642 on the radially inner side of the side of the plug 641 facing the second elastic member 650, the distance between the radially outer side of the pilot valve plug 640 and the second elastic member 650 in the axial direction of the base 630 can be small, the position close to the outer edge of the pilot valve plug 640 can abut against the second elastic member 650, and the distance between the portion close to the central axis of the pilot valve plug 640 and the second elastic member 650 can be large, the middle portion of the pilot valve plug 640 can be spaced apart from the second elastic member 650, and the deformable amount of the second elastic member 650 can be large, so that the elastic force generated by the deformation of the second elastic member 650 for driving the pilot valve plug 640 away from the main body portion of the base 630 can be better utilized to absorb the impact force of the fluid by the pilot valve 600, so that the damping force of the shock absorber 1 is more stable.

[0504] In some embodiments of the present application, as shown in FIGS. 51 and 62, the groove bottom of the plug avoiding groove 642 is a circular ring plane, that is, the plug avoiding groove 642 can be configured as a groove, so that not only the structure of the plug avoiding groove 642 can be simplified to facilitate processing, but also the space of the plug avoiding groove 642 can be large, and the plug avoiding groove 642 can better avoid the second elastic member 650, so that the second elastic member 650 can have a larger deformable space.

[0505] Alternatively, the groove bottom of the plug avoiding groove 642 is a conical surface that gradually approaches the second elastic member 650 in the radial direction of the plug 641. In this way, along the radial direction of the pilot valve plug 640, the side of the pilot valve plug 640 facing the base 630 can gradually move away from the base 630. In other words, along the axial direction of the cylinder body 100, the distance between the radially outer side of the pilot valve plug 640 and the base 630 is smaller than the distance between the radially inner side of the pilot valve plug 640 and the base 630.

[0506] Therefore, along the radial direction of the pilot valve plug 640, the distance between the groove bottom of the plug avoiding groove 642 and the second elastic member 650 can gradually increase, and when the outer ring body 651 of the second elastic member 650 is deformed in the direction close to the main body portion of the base 630 by the pilot valve plug 640, the plug avoiding groove 642 can also effectively avoid the inner elastic arm 652 to facilitate the deformation of the second elastic member 650. Moreover, the thickness of the pilot valve plug 640 at the position of the plug avoiding groove 642 can gradually decrease, and the influence of the plug avoiding groove 642 on the structural strength of the pilot valve plug 640 can be minimized, which is conducive to ensuring the structural strength of the pilot valve plug 640 to make the structure of the pilot valve 600 more stable and reliable.

[0507] Further, as shown in FIGS. 43-62, the base 630 includes a second body portion 631 and a second flow guide portion 632.

[0508] The second body portion 631 is connected to the spool assembly 500, and the second body portion 631 is provided with at least one second balance hole 634, and the second flow guide portion 632 extends along the circumference of the second body portion 631, and the second flow guide portion 632 extends from the outer periphery of the second body portion 631 to the side of the flow regulating valve 300.

[0509] In this way, when the fluid flows from the sixth flow passage 314 into the second chamber 242, the pilot valve plug 640 can be opened and closed multiple times instantaneously, and at the same time, the fluid can flow out of the second balance hole 634 to reduce the impact force of the fluid on the spool assembly 500, so that the damping force of the shock absorber 1 can be more stable.

[0510] Furthermore, by providing the second flow guide portion 632, the second flow guide portion 632 can block the fluid and guide the fluid in the direction of the overflow valve body 310, and then the fluid flowing out of the sixth flow passage 314 can quickly flow to the seventh flow passage 315, and then flow to the compression chamber 111 through the seventh flow passage 315, which is beneficial to improve the flow speed of the fluid flowing from the recovery chamber 112 to the compression chamber 111.

[0511] The second body portion 631 is adapted to be connected to the spool assembly 500, the second flow guide portion 632 extends along the circumference of the second body portion 631, and the second flow guide portion 632 extends from the outer periphery of the second body portion 631 to the side of the pilot valve plug 640.

[0512] In this way, when the fluid upwardly moves and impacts the second body portion 631 and the second body portion 631 rebounds downwardly, the second flow guide portion 632 can block the fluid and guide the fluid in the direction of the flow regulating valve 300, and then the fluid flowing out of the recovery chamber 112 through the flow regulating valve 300 can quickly flow to the compression chamber 111 through the flow regulating valve 300, which is beneficial to improve the flow speed of the fluid flowing from the recovery chamber 112 to the compression chamber 111, and the fluid flow in the shock absorber 1 is more smooth.

[0513] In addition, the second balance hole 634 can be multiple, and the multiple second balance holes 634 can extend along the circumference of the second body portion 631, and along the radial direction of the second body portion 631, the outer side of the second balance hole 634 does not exceed the inner side wall of the second flow guide portion 632.

[0514] Further, as shown in FIGS. 48 and 49, the second flow guide portion 632 is configured as an annular shape, and the pilot valve plug 640 and the second elastic member 650 are located in the inner ring of the second flow guide portion 632.

[0515] In this way, not only can the annular second flow guide portion 632 be used to more effectively block and guide the fluid, thereby improving the fluid guiding effect, but also the second flow guide portion 632 can be used to limit the pilot valve plug 640 and the second elastic member 650 in the radial direction of the base 630, thereby avoiding the relative deviation of the base 630, the second elastic member 650, and the pilot valve plug 640 in the radial direction of the base 630, and the connection is more reliable.

[0516] In some specific embodiments of the present application, as shown in FIGS. 47-49, the second flow guide portion 632 is configured with a stop structure 633 that stops on the side of the pilot valve plug 640 away from the second body portion 631.

[0517] The stop structure 633 can be a riveting structure, so that after the second elastic member 650 and the pilot valve plug 640 are installed into the base 630, the pilot valve plug 640 and the second elastic member 650 can be riveted and fixed by the stop structure 633, so as to fix the base 630, the second elastic member 650, and the pilot valve plug 640 together, thereby avoiding the second elastic member 650 and the pilot valve plug 640 from being separated from the base 630 in the axial direction of the base 630, and the structure is more reasonable.

[0518] Further, as shown in FIG. 48, the stop structure 633 is a plurality of stop structures 633 that are spaced apart along the circumference of the second flow guide portion 632.

[0519] By simultaneously stopping on the side of the pilot valve plug 640 away from the second body portion 631, the plurality of stop structures 633 can stop a plurality of positions of the pilot valve plug 640, thereby improving the stability of the fixation of the pilot valve plug 640 and the second elastic member 650, and the pilot valve plug 640 and the second elastic member 650 are less likely to be separated from the base 630, and even if some of the plurality of stop structures 633 fail, the other stop structures 633 can still ensure that the second elastic member 650 and the pilot valve plug 640 are stably connected and fixed to the base 630.

[0520] In some specific embodiments of the present application, as shown in FIG. 49, the second flow guide portion 632 includes a first flow guide segment 6321 and a second flow guide segment 6322.

[0521] One end of the first flow guide segment 6321 is connected to the second body portion 631, the second flow guide segment 6322 and the first flow guide segment 6321 are arranged in the axial direction of the base 630, and the second flow guide segment 6322 is connected to the end of the first flow guide segment 6321 away from the second body portion 631.

[0522] The thickness of the second flow guide section 632 is smaller than the thickness of the first flow guide section 631, and the stop structure 633 is arranged on the second flow guide section 632. The thickness of the second flow guide section 632 refers to the dimension of the second flow guide section 632 along the radial direction of the base 630.

[0523] By setting the thickness of the second flow guide section 632 to be small, the strength of the second flow guide section 632 can be reduced, so that the stop structure 633 can be conveniently arranged on the second flow guide section 632, and the arrangement of the stop structure 633 on the second flow guide section 632 can avoid compressing the axial space of the first flow guide section 631, so that the second elastic member 650 and the pilot valve plug 640 can be fixed in the base 630, and the structure is more reasonable.

[0524] In some embodiments of the present application, as shown in FIG. 48, the stop structure 633 is arranged as a stop rib extending towards the central axis of the second body portion 631 relative to the second flow guide portion 632.

[0525] In other words, along the axial direction of the second flow guide portion 632 away from the second body portion 631, the stop rib can extend towards the central axis of the second body portion 631, that is, along the axial direction of the second flow guide portion 632 away from the second body portion 631, the distance between the stop rib and the side wall on the other side of the second flow guide portion 632 gradually decreases. In this way, the distance between the end of the stop rib away from the second body portion 631 and the side wall of the second flow guide portion 632 can be small, and the stop rib can be used to stop the side of the pilot valve plug 640 away from the base 630, so as to fix the base 630, the second elastic member 650 and the pilot valve plug 640 together.

[0526] In addition, the stop rib is formed by bending a portion of the base flow guide portion 632, and a notch 635 is formed at the position of the corresponding portion of the second flow guide portion 632.

[0527] By arranging the notch 635 on the second flow guide portion 632, not only can the position interference between the stop rib and the corresponding portion of the second flow guide portion 632 be avoided, but also the stop rib can be disconnected from the corresponding portion of the second flow guide portion 632, so as to facilitate the bending deformation of the stop rib. Specifically, after the second elastic member 650 and the pilot valve plug 640 are installed in the base 630, the stop rib can be bent towards the central axis of the base 630, so that the stop rib can be riveted on the side of the pilot valve plug 640 away from the base 630, thereby the second elastic member 650 and the pilot valve plug 640 can be stopped by the stop rib, and the second elastic member 650 and the pilot valve plug 640 can be prevented from being separated from the base 630.

[0528] In some specific embodiments of the present application, as shown in FIG. 49 and FIG. 52, a base abutting table 636 protruding towards the second elastic member 650 is formed in the middle of the side of the second body portion 631 facing the second elastic member 650, a base avoiding groove 637 is formed between the base abutting table 636 and the second flow guide portion 632, the radial outer side of the second elastic member 650 is spaced from the base avoiding groove 637, and the radial inner side of the second elastic member 650 abuts against the base abutting table 636.

[0529] Here, the middle of the side of the second body portion 631 facing the second elastic member 650 refers to the position close to the central axis of the second body portion 631 on the side of the second body portion 631 facing the second elastic member 650, i.e., the position of the radial center of the side of the second body portion 631 facing the second elastic member 650 is provided with the base abutting table 636.

[0530] Therefore, the middle of the side of the second body portion 631 facing the second elastic member 650 can protrude towards the second elastic member 650, so that the radial inner side of the second elastic member 650 abuts against the base abutting table 636, and the radial outer side of the second elastic member 650 can be spaced from the base avoiding groove 637, which can reserve a deformable space for the second elastic member 650, so that the second elastic member 650 can deform to generate an elastic force driving the pilot valve plug 640 away from the main body portion of the base 630, thereby better utilizing the pilot valve 600 to absorb the impact force of the fluid, so that the damping force of the shock absorber 1 is more stable.

[0531] Further, the groove bottom of the base avoiding groove 637 is a circular ring plane, i.e., the base avoiding groove 637 can be configured as a groove shape, which not only simplifies the structure of the base avoiding groove 637 and facilitates processing, but also can have a larger volume, and the base avoiding groove 637 can better avoid the second elastic member 650, so that the second elastic member 650 can have a larger deformable space.

[0532] Alternatively, as shown in FIG. 49, the groove bottom of the base avoiding groove 637 is a conical surface away from the second elastic member 650 in the direction outward in the radial direction of the second body portion 631.

[0533] In this way, the distance between the groove bottom of the base avoiding groove 637 and the second elastic member 650 gradually increases along the radial direction of the second body part 631. When the outer ring body 651 of the second elastic member 650 is deformed towards the base 630, the base avoiding groove 637 can effectively avoid the second elastic member 650, so that the second elastic member 650 deforms. In addition, the thickness of the second body part 631 at the position of the base avoiding groove 637 gradually decreases. The influence of the base avoiding groove 637 on the structural strength of the second body part 631 can be minimized, which is beneficial to ensure the structural strength of the base 630, so that the structure of the pilot valve 600 is more stable and reliable.

[0534] In this way, when the fluid flows out of the flow control valve 400 and impacts the pilot valve plug 640, the pilot valve plug 640 can be opened and closed multiple times instantaneously, and part of the fluid can flow upwards from the second balance hole 634, thereby reducing the impact force of the fluid on the base 630, more effectively reducing the impact force of the fluid on the valve core assembly 500, and the damping force of the damper 1 can be more stable.

[0535] It should be noted that the radial outer side of the second elastic member 650 and the radial outer side of the pilot valve plug 640 can be spaced apart from the radial inner side of the base flow guide part 632, so that the fluid can flow from the gap between the pilot valve plug 640 and the second flow guide part 632, and from the gap between the second elastic member 650 and the second flow guide part 632 to the second balance hole 634.

[0536] Further, as shown in FIG. 47, the second balance hole 634 is a plurality of second balance holes 634, and the plurality of second balance holes 634 are spaced apart in the circumferential direction of the second body part 631. In this way, the fluid can be discharged upwards through the plurality of second balance holes 634 at the same time, further reducing the impact force of the fluid on the base 630, and the buffering effect is better.

[0537] In some embodiments of the present application, the base flow guide part is annular, and the pilot valve plug and the second elastic member are located in the inner ring of the base flow guide part.

[0538] In some embodiments of the present application, as shown in FIGS. 43-62, along the radial direction of the pilot valve plug 640, the side of the pilot valve plug 640 facing the base 630 gradually moves away from the base 630.

[0539] In other words, the distance between the radially outer side of the pilot valve plug 640 and the base 630 is smaller than the distance between the radially inner side of the pilot valve plug 640 and the base 630 along the axial direction of the cylinder 100. Moreover, the distance between the radially outer side of the pilot valve plug 640 and the base 630 is small, so that the position of the pilot valve plug 640 close to the outer edge can abut against the base 630, and the distance between the part of the pilot valve plug 640 close to the central axis and the base 630 is maximum.

[0540] That is, the side of the pilot valve plug 640 facing the base 630 can be formed with a groove, so that the outer edge of the pilot valve plug 640 can abut against the second elastic member 650, and the middle part of the pilot valve plug 640 can be spaced apart from the second elastic member 650, so that the pilot valve 600 can be formed with an elastic arm structure, and the deformable amount of the pilot valve plug 640 can be larger. When the fluid flowing out of the sixth flow channel 314 impacts the pilot valve 600 and instantaneously opens and closes the pilot valve plug 640 multiple times, the pilot valve plug 640 can more effectively buffer the impact force of the fluid, further reducing the impact force of the fluid on the valve core assembly 500, so as to make the damping force of the shock absorber 1 more stable.

[0541] In some embodiments of the present application, as shown in FIG. 1 and FIG. 8, the valve core assembly 500 according to the embodiments of the present application comprises a valve core 520 and a static core 430.

[0542] The valve core 520 is movably arranged in the piston 200 of the shock absorber 1, the static core 430 is arranged on the side of the valve core 520 facing the flow regulating valve 300 of the shock absorber 1, and the side of the static core 430 facing the valve core 520 is provided with a sink 432; wherein, when the flow regulating valve 300 is in the open valve state, the side of the valve core 520 facing the static core 430 is located in the sink 432 along the axial direction of the valve core assembly 500.

[0543] In the present application, the flow regulating valve 300 in the open valve state refers to the initial state when the flow regulating valve 300 is not extruded by external pressure and there is no fluid flowing in the flow regulating valve 300; and the flow regulating valve 300 in the closed valve state refers to the initial state when the flow regulating valve 300 is extruded by external force and the overflow valve seat and the overflow valve body of the flow regulating valve 300 abut and close.

[0544] For example, in some embodiments, the spool assembly 500 is energized to press the flow regulating valve 300, and at this time, the flow regulating valve 300 is in an open valve state at an initial position, that is, an initial state of being opened when the spool assembly 500 is not energized and no fluid flows in the flow regulating valve 300, and at this time, the flow regulating valve 300 is in a balanced state; and the flow regulating valve 300 is in a closed valve state at the initial position, that is, an initial state of being closed when the spool assembly 500 is energized and the overflow valve seat 320 and the overflow valve body 310 of the flow regulating valve 300 abut.

[0545] Alternatively, in other embodiments, the spool assembly 500 is not energized to press the flow regulating valve 300, and at this time, the flow regulating valve 300 is in an open valve state at an initial position, that is, an initial state of being opened when the spool assembly 500 is energized and no fluid flows in the flow regulating valve 300, and at this time, the flow regulating valve 300 is in a balanced state; and the flow regulating valve 300 is in a closed valve state at the initial position, that is, an initial state of being closed when the spool assembly 500 is not energized and the overflow valve seat 320 and the overflow valve body 310 of the flow regulating valve 300 abut.

[0546] According to the shock absorber 1 of the embodiment of the present application, by using the pilot valve 600 according to the above-mentioned embodiment of the present application, the shock absorber 1 can open and close the pilot valve 600 multiple times instantaneously, and can effectively buffer the impact force of the fluid, thereby reducing the impact force on the spool assembly 500

[0547] It should be noted that, considering the convenience of algorithm and adjustment, the FV (damping force-velocity) curve of the shock absorber 1 often has the following characteristics: 1. The damping force changes linearly with the current at the same speed point; 2. The damping force changes linearly with the speed within a certain range at the same current. These two linearities have high requirements for the proportional characteristics of the electromagnetic force: 1. The electromagnetic force has high linearity at different currents; 2. The electromagnetic force has good linearity within the movement stroke of the valve body 230 (preferably, the slope of the electromagnetic force-stroke curve is ≥0, that is, the electromagnetic force gradually increases or remains unchanged during the energization opening process of the coil assembly 410, which is beneficial to maintaining stable pressure).

[0548] In some specific embodiments of the present application, as shown in FIG. 53, the second elastic member 650 includes an outer ring body 651 and a plurality of inner elastic arms 652.

[0549] The outer ring body 651 abuts against the pilot valve plug 640, and the plurality of inner elastic arms 652 are connected to the inner periphery of the outer ring body 651 and are arranged at intervals in the circumferential direction, and the inner end of each inner elastic arm 652 abuts against the base 630.

[0550] The side of the base 630 facing the second elastic member 650 can gradually approach the second elastic member 650 in the radial direction of the base 630, so that the deformable space of the second elastic member 650 is larger, and when the fluid flowing out of the sixth flow channel 314 impacts the pilot valve 600 and instantaneously opens and closes the pilot valve plug 640 multiple times, the second elastic member 650 can also more effectively buffer the impact force of the fluid, further reducing the impact force of the fluid on the valve core assembly 500, so that the damping force of the damper 1 is more stable.

[0551] In some embodiments of the application, as shown in FIG. 1, the valve core assembly 500 includes a valve core 520, a static iron core 430, a coil assembly 410, and a guide rod 530.

[0552] The valve core 520 is movably arranged in the piston 200, the static iron core 430 is arranged in the piston 200, the coil assembly 410 is mounted in the piston 200, and when the coil assembly 410 is energized, the valve core 520 generates magnetism and is attracted to the static iron core 430, the guide rod 530 is arranged through the valve core 520 and connected with the valve core 520, and the pilot valve 600 is connected to one end of the guide rod 530 facing the flow regulating valve 300.

[0553] The side of the pilot valve plug 640 facing the valve core assembly 500 can be provided with a mounting groove, and the end of the pilot valve 600 can be inserted and connected in the mounting groove.

[0554] In this way, when the valve core 520 moves, the valve core 520 and the guide rod 530 can move together relative to the iron core cover 510, so that the guide rod 530 can drive the pilot valve 600 to move, so as to control the fluid flow of the flow regulating valve 300 by using the pilot valve 600.

[0555] In addition, the guide rod 530 can also guide the axial movement of the valve core 520, avoiding radial shaking of the valve core 520, and the movement is more stable.

[0556] In some embodiments of the application, as shown in FIG. 8, the valve core 520 is provided with a first recess 522 and a second recess 523 at the axial ends thereof.

[0557] The third elastic member 540 is arranged in the first recess 522 and abuts between the bottom of the first recess 522 and the iron core cover 510 of the damper 1, and the fourth elastic member 550 is arranged in the second recess 523 and abuts between the bottom of the second recess 523 and the static iron core 430.

[0558] By setting the first groove 522 and the second groove 523, the first groove 522 can fix the first valve core elastic member 540 and radially position the third elastic member 540, avoiding the third elastic member 540 from radially shaking, which is beneficial to improve the fixing stability of the third elastic member 540, and the second groove 523 can fix the fourth elastic member 550 and radially position the fourth elastic member 550, avoiding the fourth elastic member 550 from radially shaking, which is beneficial to improve the fixing stability of the fourth elastic member 550.

[0559] In some embodiments of the application, as shown in Figure 8, the static iron core 430 is provided with a through hole, a guide sleeve 531 is arranged in the through hole, and the guide rod 530 penetrates the guide sleeve 531, so that the movement of the guide rod 530 can be guided by the guide sleeve 531, so that the guide rod 530 can move in the axial direction of the damper 1, and the guide sleeve 531 can avoid mutual abrasion between the guide rod 530 and the static iron core 430.

[0560] In some specific embodiments of the application, the coil assembly 410 is arranged in the piston 200, and when the coil assembly 410 is energized, the valve core 520 generates magnetism and is attracted to the static iron core 430, the guide rod 530 is movably penetrated in the static iron core 430, and the guide rod 530 is penetrated in the valve core 520 and connected with the valve core 520.

[0561] In this way, when the valve core 520 moves, the valve core 520 and the guide rod 530 can move together relative to the iron core cover 510, so that the guide rod 530 can drive the pilot valve 600 to move, so as to control the fluid flow of the flow regulating valve 300 by the pilot valve 600. Moreover, the guide rod 530 can guide the axial movement of the valve core 520, avoiding the valve core 520 from radially shaking, and the movement is more stable.

[0562] According to the magnetic field strength obtained by the Ampere loop theorem in the Maxwell equation set, the electromagnetic force is obtained by solving the relationship among the magnetic flux density, the magnetic flux and the magnetic field strength. The proportional electromagnet contains the magnetic ring 420, so that the magnetic flux is inversely proportional to the magnetic resistance under the premise that the current and the coil are constant, that is, the total magnetic field strength is constant. In order to make the axial force constant in the movement stroke of the valve core 520, the magnetic resistance ratio in the axial force and the radial force direction needs to be kept constant or gradually reduced in the process of opening the valve core 520 in the movement direction. The magnetic resistance of the two directions is inversely proportional to the air gap D and proportional to the contact length L.

[0563] Therefore, by arranging the side of the valve core 520 facing the static core 430 in the sink groove 432 when the flow regulating valve 300 is in the open valve state, the end of the valve core 520 facing the static core 430 can always be located in the sink groove 432 when the valve core 520 moves towards the static core 430, and thus the magnetic resistance ratio of the valve core 520 in the axial direction can be kept constant, so that the electromagnetic force acting on the valve core 520 when the valve core 520 moves along the axial direction of the shock absorber 1 can be kept constant, which is conducive to improving the stability of the damping force of the shock absorber 1, and the linearity of the change of the damping force of the shock absorber 1 can be better, so as to facilitate the adjustment of the damping force of the shock absorber 1.

[0564] Therefore, by arranging the side of the valve core 520 facing the static core 430 in the sink groove 432 when the flow regulating valve 300 is in the open valve state, the end of the valve core 520 facing the static core 430 can always be located in the sink groove 432 when the valve core 520 moves towards the static core 430, and thus the magnetic resistance ratio of the valve core 520 in the axial direction can be kept constant, so that the electromagnetic force acting on the valve core 520 when the valve core 520 moves along the axial direction of the shock absorber 1 can be kept constant, which is conducive to improving the stability of the damping force of the shock absorber 1, and the linearity of the change of the damping force of the shock absorber 1 can be better, so as to facilitate the adjustment of the damping force of the shock absorber 1.

[0565] In some embodiments of the present application, as shown in FIG. 8, when the flow regulating valve 300 is in the open valve state, the distance between the side of the valve core 520 facing the static core 430 and the slot opening of the sink groove 432 along the axial direction of the valve core assembly 500 is L1, and L1 satisfies: 0.5mm>L1>0.1mm. For example, L1 can be 0.2mm, 0.3mm or 0.4mm.

[0566] In some embodiments of the present application, as shown in FIG. 8, when the flow regulating valve 300 is in the open valve state, the distance between the side of the valve core 520 facing the static core 430 and the slot opening of the sink groove 432 along the axial direction of the valve core assembly 500 is L1, and L1 satisfies: 0.5mm>L1>0.1mm. For example, L1 can be 0.2mm, 0.3mm or 0.4mm.

[0567] In some embodiments of the present application, as shown in FIG. 8, when the flow regulating valve 300 is in the open valve state, the distance between the side of the valve core 520 facing the static core 430 and the slot opening of the sink groove 432 along the axial direction of the valve core assembly 500 is L1, and L1 satisfies: 0.5mm>L1>0.1mm. For example, L1 can be 0.2mm, 0.3mm or 0.4mm.

[0568] In this way, the valve core 520 can be far away from the bottom wall of the sink 432 in the initial position, so as to reserve sufficient space for the movement of the valve core 520 in the sink 432, and avoid the waste of space caused by the excessive distance between the valve core 520 and the bottom wall of the sink 432.

[0569] In some embodiments of the present application, as shown in FIG. 1, the piston 200 includes a valve body 230, and the control valve 400 further includes a core cover 510 and a magnetic isolation ring 420.

[0570] The coil assembly 410 is installed in the piston 200, and the core cover 510 is installed on the coil assembly 410. The magnetic isolation ring 420 is installed in the piston 200, located between the core cover 510 and the valve body 230, and separates the coil assembly 410 and the valve body 230. The static core 430 is supported between the magnetic isolation ring 420 and the valve body 230.

[0571] The inner wall of the positioning support and the core cover 510 can be provided with a guide sleeve 531, and the guide rod 530 is movably arranged in the guide sleeve 531.

[0572] The valve body 230 can be made of a magnetic material, and the valve core 520 can also be made of a magnetic material, for example, the valve body 230 and the valve core 520 can be made of metal iron. In this way, after the coil assembly 410 is energized, the valve core 520 can generate magnetism to attract the valve body 230, so that the valve core 520 can move towards the valve body 230.

[0573] In addition, the core cover 510 can fix the relative position of the coil component and the valve core 520, and can limit the movement direction of the valve core 520. The core cover 510 can be made of a magnetic material, for example, the core cover 510 can be made of metal iron. In this way, the core cover 510 will also generate magnetism under the action of the coil assembly 410. The core cover 510 contacts the valve core 520, and the magnetic force between the valve core 520 and the valve body 230 can be stronger.

[0574] In some embodiments of the present application, as shown in FIG. 8, the top of the core cover 510 is provided with a mounting sink 511, and the second guide sleeve 512 is arranged in the mounting sink 511. The guide rod 530 of the valve core assembly 500 penetrates the second guide sleeve 512. In this way, the movement of the guide rod 530 can be guided by the second guide sleeve 512, so that the guide rod 530 can move along the axial direction of the shock absorber 1, and the second guide sleeve 512 can avoid the mutual abrasion between the guide rod 530 and the core cover 510.

[0575] In some embodiments of the present application, as shown in FIG. 8, the inner circumferential surface of the core cover 510 is provided with a first step portion 513, the outer circumferential surface of the valve core 520 is provided with a second step portion 524, and the first step portion 513 is stopped at the side of the second step portion 524 away from the static core 430. By stopping and limiting the second step portion 524 by the first step portion 513, the axial movement of the valve core 520 can be limited, that is, when the valve core 520 moves to the limit position away from the static core 430, the second step portion 524 can be stopped by the first step portion 513, and the structure is more reasonable.

[0576] In some embodiments of the present application, as shown in FIG. 1, the piston 200 includes a piston rod 210, a piston valve assembly 220, and a valve body 230.

[0577] The piston valve assembly 220 divides the compression chamber 111 and the recovery chamber 112 in the cylinder body 100, the piston valve assembly 220 and the piston rod 210 are connected through the valve body 230, the flow regulating valve 300 is installed in the valve body, and the pilot valve 600 extends into the valve body 230 and cooperates with the flow regulating valve 300.

[0578] For example, the piston valve assembly 220 can be sleeved on the outer circumferential surface of the valve body 230 and threadedly connected with the outer circumferential surface of the valve body 230, and the piston rod 210 can be sleeved on the outer circumferential surface of the valve body 230 and threadedly connected with the outer circumferential surface of the valve body 230.

[0579] By dividing the piston 200 into the piston rod 210 and the valve body 230 of the piston 200, the installation of the control valve 400 and the flow regulating valve 300 is more convenient, and the piston valve assembly 220 and the piston rod 210 are connected through the valve body 230, which is convenient for disassembly and assembly.

[0580] In some specific embodiments of the present application, as shown in FIG. 8, the side of the static core 430 facing the valve core 520 is provided with a sink 432, and when the flow regulating valve 300 is in the valve closing state, along the axial direction of the cylinder body 100, the side of the valve core 520 facing the pilot valve 600 is located in the sink 432.

[0581] Specifically, when the flow regulating valve 300 is in the valve closing state, along the axial direction of the cylinder body 100, the distance between the side of the valve core 520 facing the pilot valve 600 and the slot opening of the sink 432 is L1, and L1 satisfies: 0.5mm>L1>0.1mm; the distance between the side of the valve core 520 facing the pilot valve 600 and the bottom wall of the sink 432 is L2, and L2 satisfies: 2mm>L1>0.7mm.

[0582] In addition, the outer diameter of the valve core 520 is D1, and the inner diameter of the sink groove 432 is D2. Wherein, when the valve core 520 moves close to the static core 430, the distance between the inner side wall of the sink groove 432 and the outer peripheral wall of the valve core 520 is constant or gradually increases, so that (D2-D1) x (L1+L2) is constant or gradually increases.

[0583] Wherein, it should be noted that considering the convenience of algorithm and adjustment, the FV (damping force-velocity) curve of the shock absorber 1 often has: 1, the damping force changes linearly with the current at the same speed point; 2, the damping force changes linearly with the speed within a certain range at the same current.

[0584] These two linearities put higher requirements on the proportional characteristics of the electromagnetic force: 1, the electromagnetic force has high linearity at different currents; 2, the electromagnetic force has good linearity within the movement stroke of the valve body 230 (preferably, the slope of the electromagnetic force-stroke curve is greater than or equal to 0, that is, the electromagnetic force gradually increases or remains unchanged during the energization opening process of the coil assembly 410, which is conducive to maintaining stable pressure).

[0585] According to the magnetic field strength obtained from the Ampere loop theorem in Maxwell's equations, the electromagnetic force is obtained by the relationship between the magnetic flux density, the magnetic flux, and the magnetic field strength. The proportional electromagnet contains a magnetic ring 420, so under the premise that the current and the coil are constant, that is, the total magnetic field strength is constant, the magnetic flux is inversely proportional to the magnetic resistance. In order to make the axial force constant within the movement stroke of the valve core 520, the magnetic resistance ratio in the axial force and radial force directions remains constant or gradually decreases during the opening process of the valve core 520 in the movement direction. The magnetic resistance in the direction is inversely proportional to the air gap D and proportional to the contact length L.

[0586] Specifically, the gap D between the bottom surface of the valve body 230 and the static core 430 is (D2-D1). By setting this way, after the coil assembly 410 is energized, the value of the air gap D x the height of the sink groove 432 remains almost constant or gradually increases during the movement of the valve core 520, so that the axial electromagnetic force of the valve core assembly 500 remains constant or gradually increases during the movement of the valve core 520, ensuring that the FV graph force value of the shock absorber 1 has high linearity at different speeds and different currents, and the damping force stability is high.

[0587] In some embodiments of the present application, the outer diameter of the valve core 520 is D1, the inner diameter of the sink groove 432 is D2, and the depth of the sink groove 432 is L. Wherein, the depth L of the sink groove 432 is L1+L2.

[0588] Wherein, when the valve core 520 moves towards the direction of approaching the static iron core 430, the distance between the inner side wall of the sink groove 432 and the outer peripheral wall of the valve core 520 remains unchanged, so that (D2-D1) x L remains unchanged; or, when the valve core 520 moves towards the direction of approaching the static iron core 430, the distance between the inner side wall of the sink groove 432 and the outer peripheral wall of the valve core 520 gradually increases, so that (D2-D1) x L gradually increases.

[0589] In this way, after the coil assembly 410 is energized, the value of the air gap D x the depth L of the sink groove 432 remains almost unchanged or gradually increases during the movement of the valve core 520, so that the axial electromagnetic force of the valve core assembly 500 remains unchanged or gradually increases during the movement of the valve core 520, ensuring that the FV diagram force value of the shock absorber 1 has high linearity at different speeds and different currents, and the indicator diagram curve fluctuates little, so that the damping force stability of the shock absorber 1 is higher, thereby facilitating the adjustment of the damping force of the shock absorber 1.

[0590] In some embodiments of the present application, as shown in FIGS. 1 and 8, the valve core 520 is provided with an eighth flow channel 521 which penetrates through opposite sides of the valve core 520 along the axial direction of the valve core 520. In this way, when the valve core 520 moves, the air pressure of the spaces on both sides of the movement direction of the valve core 520 can be balanced through the eighth flow channel 521, so that the movement of the valve core 520 is more stable, and the movement of the pilot valve 600 is more stable.

[0591] In some embodiments of the present application, as shown in FIGS. 1 and 8, the valve core assembly 500 further comprises a third elastic member 540 and a fourth elastic member 550.

[0592] The third elastic member 540 and the fourth elastic member 550 are sleeved on the guide rod 530 and are respectively arranged on both sides of the movement direction of the valve core 520, and the third elastic member 540 and the fourth elastic member 550 apply elastic force to the valve core 520 to keep the position of the valve core 520 stable. In this way, under the action of the third elastic member 540 and the fourth elastic member 550, if the valve core 520 is not subjected to external force, the two sides of the movement direction of the valve core 520 will not be in contact with other objects, thereby avoiding the eighth flow channel 521 being blocked, and ensuring the smoothness of the gas.

[0593] The following illustrates the fluid flow path of the shock absorber 1 in the recovery working condition and the compression working condition when the flow regulating valve 300 is in the open valve state:

[0594] I. As shown in Fig. 2, when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the recovery condition, the piston rod 210 vibrates upward, the pressure in the recovery cavity 112 increases, at this time the elastic force of the first elastic member 360 supports the overflow valve body 310, and the pressure in the second cavity increases to make the overflow valve disc 330 adhere to the overflow valve seat 320. The fluid in the recovery cavity 112 can flow to the compression cavity 111 through the second flow channel 311, the communication hole 331 and the first flow channel 321, and the flow of the fluid is large and the fluid damping is small, so the shock absorber 1 behaves as "soft", and at the same time the fluid in the liquid storage cavity 121 can also flow into the compression cavity 111.

[0595] II. As shown in Fig. 3, when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the compression condition, the piston rod 210 vibrates downward, the pressure in the compression cavity 111 increases, the pressure in the first flow channel 321 increases, the overflow valve body 310 and the overflow valve disc 330 move away from the overflow valve seat 320, and the overflow valve disc 330 adheres to the overflow valve body 310. The fluid in the compression cavity 111 can flow into the recovery cavity 112 from the third flow channel 322 and the first flow channel 321, and the flow of the fluid is large and the fluid damping is small, so the shock absorber 1 behaves as "soft", and at the same time the fluid in the compression cavity 111 can also flow into the liquid storage cavity 121.

[0596] The following illustrates the fluid flow paths when the flow regulating valve 300 is in the open state and the shock absorber 1 is in the recovery condition and the compression condition:

[0597] It should be noted that in the present application, the flow regulating valve 300 in the open state refers to the state of the flow regulating valve 300 when it is not extruded by external pressure, for example, the flow regulating valve 300 is not subjected to the force of the valve core assembly 500; and the flow regulating valve 300 in the closed state refers to the state of the flow regulating valve 300 when it is extruded by external force, for example, the flow regulating valve 300 is subjected to the force of the valve core assembly 500.

[0598] I. As shown in Fig. 2, when the flow regulating valve 300 is in the open state and the shock absorber 1 is in the recovery condition, the piston rod 210 vibrates upward, the pressure in the recovery cavity 112 increases, at this time the elastic force of the first elastic member 360 supports the overflow valve body 310, and the pressure in the second cavity increases to make the overflow valve disc 330 adhere to the overflow valve seat 320. The fluid in the recovery cavity 112 can flow to the compression cavity 111 through the second flow channel 311, the communication hole 331 and the first flow channel 321, and the flow of the fluid is large and the fluid damping is small, so the shock absorber 1 behaves as "soft", and at the same time the fluid in the liquid storage cavity 121 can also flow into the compression cavity 111.

[0599] II. When the flow regulating valve 300 is in the open state and the shock absorber 1 is in the compression condition, the piston rod 210 vibrates downward, the pressure in the compression chamber 111 increases, the pressure in the first flow passage 321 increases, the overflow valve body 310 and the overflow valve disc 330 move away from the overflow valve seat 320, and the overflow valve disc 330 is attached to the overflow valve body 310. The fluid in the compression chamber 111 can flow from the third flow passage 322 and the first flow passage 321 into the recovery chamber 112, and the flow of the fluid is large and the fluid damping is small, and the shock absorber 1 behaves as "soft", and the fluid in the compression chamber 111 can also flow into the liquid storage chamber 121.

[0600] The following illustrates the fluid flow path when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the recovery condition and the compression condition:

[0601] I. As shown in FIG. 4, when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the recovery condition, the valve body 230 pushes the pilot valve 600, the overflow valve body 310, and the overflow valve disc 330 against the overflow valve seat 320, the second flow passage 311 and the third flow passage 322 are closed, the piston rod 210 vibrates upward, the pressure in the recovery chamber 112 increases, and the fluid flows from the recovery chamber 112 and the liquid storage chamber into the compression chamber 111;

[0602] In the first stage, the overflow valve body 310 abuts against the overflow valve disc 330, and the overflow valve disc 330 abuts against the overflow valve seat 320, at this time the second flow passage 311 and the third flow passage 322 are closed, the fluid in the recovery chamber 112 flows from the overflow hole 339 or the overflow gap 3133 to the compression chamber 111, the flow of the fluid is small, the damping is large, and the shock absorber 1 behaves as "hard";

[0603] In the second stage, the fluid in the recovery chamber 112 flows into the first chamber 241 through the fourth flow passage 243, and the pressure in the first chamber 241 increases, the fluid pushes away the pilot valve plug 640 against the electromagnetic force and flows into the second chamber 242, and then flows into the compression chamber 111 through the seventh flow passage 315 and the first flow passage 321, and the damping is reduced;

[0604] In the third stage, a large amount of fluid is accumulated between the overflow valve disc 330 and the overflow valve body 310, when the pressure is greater than the electromagnetic force, the fluid pushes away the overflow valve body 310, the fluid flows out from between the overflow valve body 310 and the overflow valve disc 330, i.e. the fluid in the recovery chamber 112 flows into the compression chamber 111 through the second flow passage 311 and the first flow passage 321, and the damping is further reduced.

[0605] II. As shown in Fig. 5, when the flow regulating valve 300 is in the closed state and the shock absorber 1 is in the compression mode, the valve body 230 is pushed by the magnetic force to push the pilot valve 600, the overflow valve body 310, the overflow valve plate 330 abuts against the overflow valve seat 320, the second flow channel 311 and the third flow channel 322 are closed, the piston rod 210 vibrates downward, the pressure in the compression chamber 111 increases, and the fluid flows from the compression chamber 111 into the recovery chamber 112 and the liquid storage chamber 121;

[0606] In the first stage, the overflow valve body 310 abuts against the overflow valve plate 330, and the overflow valve plate 330 abuts against the overflow valve seat 320, at this time, the second flow channel 311 and the third flow channel 322 are closed, the fluid in the compression chamber 111 flows from the overflow hole 339 or the overflow gap 3133 to the recovery chamber 112, the fluid flow is small, the damping is large, and the shock absorber 1 behaves as "hard";

[0607] In the second stage, the fluid is accumulated in the first flow channel 321, when the pressure is greater than the electromagnetic force, the flow can push away the overflow valve plate 330 and the overflow valve body 310, and the fluid flows out from between the overflow valve seat 320 and the overflow valve plate 330, that is, the flow in the compression chamber 111 flows into the recovery chamber 112 through the first flow channel 321 and the third flow channel 322, and the damping is reduced.

[0608] The vehicle according to the embodiments of the present application is described below with reference to the accompanying drawings.

[0609] According to the vehicle of the embodiments of the present application, by using the shock absorber 1 according to the above-mentioned embodiments of the present application, the shock absorber 1 can continuously adjust the damping force by adjusting the fluid flow between the compression chamber 111 and the recovery chamber 112, which is beneficial to improve the riding comfort and the handling performance of the vehicle, and the structure of the shock absorber 1 is simple and convenient to adjust; the flow regulating valve 300 can separate the overflow valve seat 320 and the overflow valve body 310 by using the valve body elastic member 360 to facilitate the opening of the flow regulating valve 300, and further facilitate the adjustment of the damping force of the shock absorber 1.

[0610] The other configurations and operations of the shock absorber 1 and the vehicle according to the embodiments of the present application are known to those skilled in the art, and will not be described in detail here.

[0611] In the description of the present specification, the description referring to the terms "specific embodiments", "specific examples" and the like means that the specific features, structures, materials or characteristics described in connection with the embodiments or examples are contained in at least one embodiment or example of the present application. In the present specification, the illustrative expressions of the above-mentioned terms do not necessarily refer to the same embodiments or examples.

[0612] While embodiments of the application have been shown and described, it is to be understood that the embodiments described are merely exemplary of the principles and application of the present application. Numerous modifications and changes can be made by those skilled in the art without departing from the spirit and scope of the application. The scope of the application is not to be limited by the embodiments shown and described, but only by the claims and their equivalents.

Claims

1. A damper (1), characterized in that The application relates to a cylinder (100), a piston (200) movably arranged in the cylinder (100) and separating a compression chamber (111) and a recovery chamber (112) in the cylinder (100), a flow regulating valve (300) arranged in the piston (200) and communicating with the compression chamber (111) and the recovery chamber (112) respectively, and a control valve (400) arranged in the piston (200) and regulating the fluid flow between the compression chamber (111) and the recovery chamber (112) by controlling the flow regulating valve (300). The flow regulating valve (300) comprises an overflow valve body (310) movably arranged in the piston (200), an overflow valve seat (320) arranged in the piston (200) and located on the side of the overflow valve body (310) away from the control valve (400), the overflow valve seat (320) being provided with a first flow channel (321) communicating with the compression chamber (111), and an overflow valve plate (330) movably arranged between the overflow valve body (310) and the overflow valve seat (320), the overflow valve plate (330) and the overflow valve body (310) forming a second flow channel (311) therebetween, and the overflow valve plate (330) and the overflow valve seat (320) forming a third flow channel (322) therebetween, the second flow channel (311) and the third flow channel (322) communicating with the first flow channel (321) and the recovery chamber (112) respectively, wherein the second flow channel (311) and / or the third flow channel (322) are opened and closed by the movement of the overflow valve body (310). The overflow valve plate (330) is provided with overflow channels (370), and when the overflow valve seat (320) and the overflow valve body (310) respectively abut against the overflow valve plate (330), the overflow channels (370) respectively communicate with the first flow channel (321) and the recovery chamber (112) of the shock absorber (1). The overflow channels (370) are arranged in a plurality of groups along the circumference of the overflow valve plate (330). The overflow valve body (310) is movably arranged on one side of the overflow valve seat (320).

2. The damper (1) according to claim 1, characterized in that The overflow valve plate (330) is provided with at least one communication hole (331), and the second flow channel (311) communicates with the first flow channel (321) through the communication hole (331). ​ ​ ​ ​ 3. The damper (1) according to claim 2, characterized in that ​ 4. The damper (1) according to claim 3, characterized in that ​ 5. The damper (1 ) according to any one of claims 2-4, characterized in that ​ 6. A damper (1 ) according to any one of claims 2-5, characterized in that ​ 7. A damper (1 ) according to any one of claims 2-6, characterized in that One of the overflow valve body (310) and the overflow valve seat (320) is provided with a support column (340) extending in the axial direction of the cylinder body (100), and the overflow valve plate (330) is movably sleeved on the support column (340) to move in the axial direction of the cylinder body (100) under the guidance of the support column (340).

8. The damper (1) according to claim 7, characterized in that The cross-sectional area of the free end of the support column (340) decreases in the direction close to the overflow valve body (310).

9. The damper (1) according to claim 7, characterized in that The cross-sectional area of the free end of the support column (340) decreases in the direction close to the overflow valve seat (320).

10. The damper (1) according to claim 7, characterized in that The overflow valve body (310) is provided with the support column (340), one end of the support column (340) towards the overflow valve seat (320) is configured as a guide section (345), and the guide section (345) decreases in cross-sectional area in the axial direction of the support column (340) close to the overflow valve seat (320); or, The overflow valve seat (320) is provided with the support column (340), one end of the support column (340) towards the overflow valve body (310) is configured as a guide section (345), and the guide section (345) decreases in cross-sectional area in the axial direction of the support column (340) close to the overflow valve body (310).

11. The damper (1) according to claim 10, characterized in that The overflow valve body (310) is provided with the support column (340), and the gap between the overflow valve plate (330) and the guide section (345) increases in the axial direction of the support column (340) close to the overflow valve seat (320); or, The overflow valve seat (320) is provided with the support column (340), and the gap between the overflow valve plate (330) and the guide section (345) increases in the axial direction of the support column (340) close to the overflow valve body (310).

12. The damper (1) according to claim 10 or 11, characterized in that The overflow valve seat (320) comprises: A first seat body (323) forms the third flow passage (322) with the overflow valve plate (330); A second seat body (324) is supported on the side of the first seat body (323) away from the overflow valve plate (330) and connected with the piston (200), and the second seat body (324) and the first seat body (323) jointly define the first flow passage (321).

13. The damper (1) according to claim 12, characterized in that The overflow valve plate (330) is arranged between the first seat body (323) and the overflow valve body (310); wherein one of the first seat body (323) and the second seat body (324) is configured as the support column (340).

14. The damper (1) according to claim 12 or 13, characterized in that The first seat body (323) and the second seat body (324) jointly define the first flow passage (321) adapted to communicate with the compression chamber (111) of the shock absorber (1).

15. A damper (1 ) according to any one of claims 12-14, characterized in that The first seat body (323) is configured with a through hole (3231), the second seat body (324) is configured with at least one flow channel hole (3241), and the second seat body (324) is configured with the support column (340) which extends into the through hole (3231); Wherein, the through hole (3231) and the flow channel hole (3241) constitute the first flow channel (321).

16. A damper (1 ) according to any one of claims 7-15, characterized in that The overflow valve piece (330) comprises: A main body part (332) which is arranged between the overflow valve body (310) and the overflow valve seat (320); A guide part (333) which is connected to the main body part (332) and protrudes from at least one side of the main body part (332) in the axial direction of the cylinder body (100), the guide part (333) and the main body part (332) together define a guide hole (334), and the support column (340) is arranged in the guide hole (334), so that the overflow valve piece (330) moves along the axial direction of the cylinder body (100) under the guidance of the support column (340).

17. A damper (1) according to claim 16, characterized in that The guide part (333) is provided with a first fillet surface (3331) which extends along the circumference of the guide hole (334), and the side of the guide part (333) away from the main body part (332) and the inner side wall of the guide hole (334) are arc transitioned by the first fillet surface (3331).

18. A damper (1 ) according to claim 16 or 17, characterized in that The main body part (332) is provided with a second fillet surface (3321) which extends along the circumference of the guide hole (334), and the side of the main body part (332) away from the guide part (333) and the inner side wall of the guide hole (334) are arc transitioned by the second fillet surface (3321).

19. A damper (1 ) according to any one of claims 16-18, characterized in that The guide part (333) is connected to the main body part (332) and protrudes from at least one side of the main body part (332) in the thickness direction, and the overflow valve piece (330) is movably sleeved on the support column (340) through the guide hole (334).

20. A damper (1 ) according to any one of claims 16-19, characterized in that In the axial direction of the overflow valve piece (330), the length of the guide part (333) is L, and the thickness of the main body part (332) is W; Wherein, L and W satisfy L>2W; and / or The support column (340) is in clearance fit with the guide hole (334), and the distance between the outer peripheral surface of the support column (340) and the inner side wall of the guide hole (334) is D, D satisfies 0.02mm≤D≤0.15mm.

21. A damper (1) according to any one of claims 16-20, characterized in that The guide part (333) is arranged on one side of the main body part (332) in the thickness direction; or The guide part (333) is a plurality of, and the plurality of guide parts (333) comprise a first guide part and a second guide part, the first guide part is arranged on one side of the main body part (332) in the thickness direction, and the second guide part is arranged on the other side of the main body part (332) in the thickness direction.

22. A damper (1 ) according to any one of claims 16-21, characterized in that The first guide part is provided with a third fillet surface extending along the circumference of the guide hole (334), and the side of the first guide part away from the main body part (332) and the inner side wall of the guide hole (334) are arc transitioned by the third fillet surface; and / or, The second guide part is provided with a fourth fillet surface extending along the circumference of the guide hole (334), and the side of the second guide part away from the main body part (332) and the inner side wall of the guide hole (334) are arc transitioned by the fourth fillet surface.

23. A damper (1 ) according to any one of claims 2-22, characterized in that The flow regulating valve (300) further comprises: A magnetic attraction member (350) is arranged on the side of the overflow valve seat (320) facing the overflow valve sheet (330), and the magnetic attraction member (350) generates a magnetic attraction force attracting the overflow valve sheet (330).

24. A damper (1) according to claim 23, characterized in that The overflow valve seat (320) is configured with at least one flow channel hole (3241), and the magnetic attraction member (350) is adjacent to the flow channel hole (3241), and the flow channel hole (3241) is configured as an arc-shaped flow channel hole extending around the magnetic attraction member (350).

25. The damper (1) according to claim 23 or 24, characterized in that The flow regulating valve (300) further comprises: A limiting member (380) is arranged on the support column (340) and located on the side of the magnetic attraction member (350) adjacent to the overflow valve sheet (330) to limit the magnetic attraction member (350) and the overflow valve sheet (330); Wherein, the support column (340) is formed with a clamping groove (344), and the limiting member (380) is clamped in the clamping groove (344).

26. A damper (1 ) according to any one of claims 23-25, characterized in that The flow regulating valve (300) further comprises: A magnetic force adjusting member (352) is arranged on the side of the magnetic attraction member (350) facing the overflow valve sheet (330), and the magnetic force adjusting member (352) is used for adjusting the magnetic attraction force of the magnetic attraction member (350) to the overflow valve sheet (330).

27. A damper (1) according to claim 26, characterized in that The magnetic force adjusting member (352) comprises at least one magnetic force adjusting sheet (351), at least one of the magnetic force adjusting sheets (351) is arranged in layers, and the magnetic force adjusting sheet (351) adjusts the magnetic attraction force of the magnetic attraction member (350) to the overflow valve sheet (330) by adjusting the number of the magnetic force adjusting sheet (351), and an adsorption gap is formed between adjacent two magnetic force adjusting sheets (351); and / or The magnetic force adjusting member (352) comprises a magnetic force adjusting block, which adjusts the magnetic attraction force of the magnetic attraction member (350) to the overflow valve sheet (330) by adjusting the height of the magnetic force adjusting block along the axis of the cylinder (100), and the magnetic force adjusting block is provided with an adsorption hole.

28. A damper (1 ) according to any one of claims 2-27, characterized in that The side of the overflow valve body (310) facing the overflow valve sheet (330) is provided with a first abutting ring table (312), and the side of the overflow valve seat (320) facing the overflow valve sheet (330) is provided with a second abutting ring table (325), and the inner diameter of the first abutting ring table (312) is smaller than the inner diameter of the second abutting ring table (325).

29. A damper (1) according to claim 28, characterized in that The second abutting ring table (325) is arranged on the side of the overflow valve seat (320) facing the overflow valve body (310).

30. A damper (1 ) according to claim 28 or 29, characterized in that The first abutting ring table (312) and the second abutting ring table (325) are staggered in the radial direction of the flow regulating valve (300). The overflow valve piece (330) is configured with an overflow channel (370), and at least part of the overflow channel (370) is located between the first abutting ring table (312) and the second abutting ring table (325) in the radial direction of the overflow valve piece (330).

31. A damper (1) according to claim 29, characterized in that At least part of the overflow channel (370) is located between the outer peripheral surface of the first abutting ring table (312) and the inner peripheral surface of the second abutting ring table (325).

32. A damper (1 ) according to any one of claims 28-31, characterized in that The end of the overflow valve body (310) away from the overflow valve seat (320) is provided with a sealing sink (316), the valve body (230) of the piston (200) is provided with a sealing ring table (244), and the sealing ring table (244) is arranged apart from the inner side wall of the valve body (230) in the radial direction of the cylinder body (100). The overflow valve body (310) and the inner side wall of the valve body (230) are dynamically sealed, and the sealing sink (316) and the outer side wall of the sealing ring table (244) are dynamically sealed. The inner diameter of the sealing sink (316) is smaller than the inner diameter of the second abutting ring table (325).

33. A damper (1) according to claim 32, characterized in that The inner cross-sectional area of the second abutting ring table (325) is S1, and the inner cross-sectional area of the sealing sink (316) is S2, S1 and S2 satisfy: S2≤S1≤1.3×S2.

34. A damper (1 ) according to claim 32 or 33, characterized in that The outer diameter of the first abutting ring table (312) is smaller than the inner diameter of the second abutting ring table (325).

35. A damper (1) according to any one of claims 32-34, characterized in that The side surface of the overflow valve piece (330) facing the overflow valve body (310) is configured with a valve body abutting surface (335), the valve body abutting surface (335) is adapted to abut with the first abutting ring table (312), and the valve body abutting surface (335) and the outer peripheral edge of the overflow valve piece (330) form a valve body pressure bearing surface (336).

36. A damper (1 ) according to claims 32-35, characterized in that The overflow valve piece (330) is configured with at least one overflow hole (339), and the overflow hole (339) is located between the outer peripheral surface of the first abutting ring table (312) and the inner peripheral surface of the second abutting ring table (325) in the radial direction of the overflow valve piece (330), and the overflow hole (339) respectively communicates with the compression cavity (111) and the recovery cavity (112) when the flow regulating valve (300) is in the closed valve state.

37. A damper (1 ) according to any of claims 2-36, characterized in that At least one of the side of the overflow valve body (310) facing the overflow valve piece (330), the side of the overflow valve seat (320) facing the overflow valve piece (330), and the overflow valve piece (330) is configured with an overflow notch (3133), and the overflow notch (3133) respectively communicates with the compression cavity (111) and the recovery cavity (112).

38. A damper (1 ) according to any of claims 2-37, characterized in that One of the overflow valve body (310) and the overflow valve seat (320) is provided with a support column (340), and the other of the overflow valve body (310) and the overflow valve seat (320) is provided with a first elastic member (360) between the support column (340).

39. A damper (1) according to claim 38, characterized in that The overflow valve body (310) is provided with the support column (340), and an end of the support column (340) towards the overflow valve seat (320) is configured with a support ring table (341), and the first elastic member (360) abuts against the support ring table (341); or The overflow valve seat (320) is provided with the support column (340), and an end of the support column (340) towards the overflow valve body (310) is configured with a support ring table (341), and the first elastic member (360) abuts against the support ring table (341).

40. A damper (1) according to claim 39, characterized in that The support ring table (341) comprises: a connecting section (342) connected with the support column (340); and a transition section (343) connected to an end of the connecting section (342) away from the support column (340), and an outer diameter of the transition section (343) is smaller than an outer diameter of the connecting section (342); Wherein, the first elastic member (360) is interference fit with the connecting section (342), and there is a gap between the first elastic member (360) and the transition section (343).

41. A damper (1) according to any of claims 2-40, characterized in that A side of the overflow valve seat (320) towards the overflow valve piece (330) is provided with a second abutting ring table (325) and a flow guide surface (326), the second abutting ring table (325) abuts against the overflow valve piece (330), and the flow guide surface (326) is located radially outside the second abutting ring table (325); Wherein, along the radial direction of the overflow valve seat (320), the distance between any point of the flow guide surface (326) and the radially outer side of an end of the second abutting ring table (325) towards the overflow valve piece (330) is X; Along the axial direction of the overflow valve seat (320), the distance between the any point of the flow guide surface (326) and the radially outer side of the end of the second abutting ring table (325) towards the overflow valve piece (330) is Y; X and Y satisfy: Y / X>0.

5.

42. A damper (1) according to claim 41, characterized in that The flow guide surface (326) is provided on a side of the overflow valve seat (320) towards the overflow valve body (310), and the flow guide surface (326) is located radially outside the second abutting ring table (325).

43. The damper (1) according to claim 41 or 42, characterized in that The flow guide surface (326) comprises: a first step surface (328) connected to the radially outer side of the second abutting ring table (325) and extending along the radial direction of the overflow valve seat (320), and the second abutting ring table (325) exceeds the first step surface (328) in the direction close to the overflow valve body (310); and a second step surface (329) connected to the radially outer side of the first step surface (328) and extending along the radial direction of the overflow valve seat (320), and the second abutting ring table (325) exceeds the second step surface (329) in the direction close to the overflow valve body (310). a second step surface (329) connected to a radially outer side of the first step surface (328) and extending along a radial direction of the spool valve seat (320), and the first step surface (328) exceeds the second step surface (329) in a direction close to the spool valve body (310); or the flow guide surface (326) comprises: a third step surface (3262) connected to a radially outer side of the second abutting ring (325) and extending along a radial direction of the spool valve seat (320), and the second abutting ring (325) exceeds the third step surface (3262) in a direction close to the spool valve body (310); or a slope surface (3261) connected to a radially outer side of the third step surface (3262) and extending outward along a radial direction of the spool valve seat (320), the slope surface (3261) gradually moves away from the spool valve body (310); or the flow guide surface (326) comprises a slope surface (3261) connected to a radially outer side of the second abutting ring (325) and extending outward along a radial direction of the spool valve seat (320), the slope surface (3261) gradually moves away from the spool valve body (310); wherein, in an axial direction of the spool valve seat (320) close to the spool valve body (310), an end of the second abutting ring (325) adjacent to the spool valve body (310) exceeds an end of the slope surface (3261) adjacent to the spool valve body (310); or the flow guide surface (326) comprises a slope surface (3261) connected to a radially outer side of the second abutting ring (325) and extending outward along a radial direction of the spool valve seat (320), the slope surface (3261) gradually moves away from the spool valve body (310); wherein, in an axial direction of the spool valve seat (320), an end of the slope surface (3261) adjacent to the spool valve body (310) is flush with an end of the second abutting ring (325) facing the spool valve body (310).

44. A damper (1 ) according to any one of claims 41 -43, characterized in that In an axial direction of the spool valve seat (320) close to the spool valve body (310), a dimension B of an end of the second abutting ring (325) adjacent to the spool valve body (310) exceeds an end of the flow guide surface (326) adjacent to the spool valve body (310), and B satisfies: 0.4mm≤B≤0.6mm.

45. A damper (1) according to claim 43, characterized in that An included angle between the slope surface (3261) and a radial direction of the spool valve seat (320) is β, and β satisfies: 35°≤β≤55°.

46. A damper (1 ) according to any of claims 41 - 45, characterized in that In a radial direction of the spool valve seat (320), a radial thickness of the second abutting ring (325) is ≤0.2mm.

47. A damper (1) according to claim 46, characterized in that In a radial direction of the spool valve seat (320), a radial thickness of the second abutting ring (325) is >0.15mm.

48. A damper (1 ) according to any of claims 2-47, characterized in that the piston (200) comprises: a piston rod (210); a piston valve assembly (220) separating the compression chamber (111) and the recovery chamber (112) in the cylinder (100); A valve body (230) is connected with the piston valve assembly (220) and the piston rod (210), the overflow valve body (310) and the overflow valve seat (320) are installed in the valve body (230), and the control valve (400) extends into the valve body (230) and cooperates with the flow regulating valve (300).

49. The damper (1) according to claim 48, characterized in that The overflow valve body (310) is movably arranged in the valve body (230), and the overflow valve body (310) and the valve body (230) define a first chamber (241) and a second chamber (242), the control valve (400) extends into the second chamber (242) to control the opening and closing of the first chamber (241) and the second chamber (242).

50. A damper (1) according to claim 49, characterized in that The side of the overflow valve body (310) away from the overflow valve seat (320) is provided with a sealing groove (316), the valve body (230) is provided with a sealing ring table (244), and along the radial direction of the cylinder body (100), the sealing ring table (244) is arranged apart from the inner side wall of the valve body (230), the overflow valve body (310) is dynamically sealed with the inner side wall of the valve body (230), and the sealing groove (316) is dynamically sealed with the outer side wall of the sealing ring table (244). The inner side wall of the valve body (230), the outer side wall of the sealing ring table (244) and the overflow valve body (310) define the first chamber (241), and the inner side wall of the sealing ring table (244) and the overflow valve body (310) define the second chamber (242).

51. Damper (1) according to claim 49 or 50, characterized in that The side wall of the valve body (230) is provided with a fourth flow channel (243) and a fifth flow channel (251), the fourth flow channel (243) is respectively communicated with the first chamber (241) and the recovery cavity (112), one end of the fifth flow channel (251) is communicated with the recovery cavity (112), and the other end is respectively communicated with the second flow channel (311) and the third flow channel (322); and The overflow valve body (310) is provided with a sixth flow channel (314) and a seventh flow channel (315), one end of the sixth flow channel (314) is communicated with the first chamber (241), the other end of the sixth flow channel (314) is communicated with the second chamber (242), and the control valve (400) cooperates with the other end of the sixth flow channel (314), one end of the seventh flow channel (315) away from the overflow valve seat (320) is communicated with the second chamber (242), and the other end of the seventh flow channel (315) is communicated with the first flow channel (321), the fluid flow of the sixth flow channel (314) and the fluid flow of the seventh flow channel (315) are controlled by the opening and closing of the control valve (400).

52. A damper (1) according to claim 51, characterized in that The valve body (230) comprises: an upper valve body (240) connected to the piston rod (210), the spill valve body (310) movably arranged in the upper valve body (240), and the spill valve body (310) and the upper valve body (240) defining the first chamber (241) and the second chamber (242); a lower valve body (250) connected between the piston valve assembly (220) and the upper valve body (240), and the spill valve seat (320) arranged in the lower valve body (250); wherein a side wall of the upper valve body (240) is provided with the fourth flow passage (243), and a side wall of the lower valve body (250) is provided with the fifth flow passage (251).

53. The damper (1 ) according to any one of claims 1 -52, characterized in that The control valve (400) comprises: a spool assembly (500) arranged in the piston (200); a pilot valve (600) connected to the spool assembly (500), and the spool assembly (500) controlling the flow regulating valve (300) through the pilot valve (600) to regulate the fluid flow between the compression chamber (111) and the recovery chamber (112).

54. A damper (1) according to claim 53, characterized in that The pilot valve (600) comprises: a first body portion (610) connected to the spool assembly (500), and the first body portion (610) being provided with at least one first balance hole (611) and a sealing protrusion (612), the sealing protrusion (612) being arranged on a side of the first body portion (610) facing the flow regulating valve (300), and the sealing protrusion (612) cooperating with the flow regulating valve (300); wherein the flow regulating valve (300) comprises a spill valve body (310) movably mounted in the piston (200), and the spill valve body (310) being configured with a sixth flow passage (314) and a seventh flow passage (315), the pilot valve (600) cooperating with the sixth flow passage (314) through the sealing protrusion (612) to control the opening and closing of the sixth flow passage (314) and the seventh flow passage (315).

55. A damper (1) according to claim 54, characterized in that In the axial direction of the pilot valve (600) extending away from the body portion (610), the sealing protrusion (612) is configured in the shape of a truncated cone with decreasing cross-sectional area.

56. A damper (1 ) according to claim 54 or 55, characterized in that The sixth flow passage (314) communicates with the recovery chamber (112), and the seventh flow passage (315) communicates with the compression chamber (111), the sealing protrusion (612) cooperating with the sixth flow passage (314) to control the opening and closing of the sixth flow passage (314) and the seventh flow passage (315).

57. A damper (1 ) according to any of claims 54-56, characterized in that The body part (610) is further provided with a first balance hole (611) penetrating the body part (610) along the axial direction of the pilot valve (600) and along the radial direction of the body part (610), and the first balance hole (611) is located between the first flow guide part (620) and the sealing protrusion (612). The first balance hole (611) is multiple, and the multiple first balance holes (611) are arranged in a circumferential direction of the body part (610); and / or The sealing protrusion (612) protrudes from the first flow guide part (620) along the axial direction of the pilot valve (600); and / or A body flow guide surface (613) is formed between the sealing protrusion (612) and the first flow guide part (620) on a side surface of the body part (610) facing the flow regulating valve (300); The body flow guide surface (613) is configured as a truncated conical surface with a decreasing cross-sectional area along the axial direction of the pilot valve (600) extending away from the body part (610).

58. A damper (1 ) according to any of claims 54-57, characterized in that The first body part (610) projects on the overflow valve body (310) along the axial direction of the cylinder (100) and covers at least part of the seventh flow channel (315).

59. A damper (1 ) according to any of claims 54-58, characterized in that The pilot valve (600) further comprises: A first flow guide part (620) extending along the circumferential direction of the first body part (610), the first flow guide part (620) extending from the outer periphery of the first body part (610) to one side of the flow regulating valve (300), and the first balance hole (611) is located between the first flow guide part (620) and the sealing protrusion (612).

60. A damper (1 ) according to any of claims 54-59, characterized in that The inner diameter of the end of the sixth flow channel (314) facing the pilot valve (600) is d1; The angle between the radial outer side of the sealing protrusion (612) and the axial direction of the cylinder (100) is ; and Along the axial direction of the cylinder (100), the first flow guide part (620) exceeds the length of the first body part (610) by h in the direction close to the overflow valve body (310), and the inner diameter of the first flow guide part (620) is d2; Wherein, H, d1 and d2 satisfy: h.

61. A damper (1) according to any of claims 54-60, characterized in that The pilot valve (600) comprises: A base (630) connected to the valve core assembly (500); A pilot valve plug (640) provided on the side of the base (630) facing the flow regulating valve (300) and movable relative to the base (630), and the pilot valve plug (640) cooperates with the flow regulating valve (300); A second elastic member (650) provided between the base (630) and the pilot valve plug (640) to provide an elastic force of the pilot valve plug (640) away from the base (630).

62. A damper (1) according to claim 61, characterized in that The base (630) further comprises: A ring-shaped boss (638) is arranged on a side of the second body portion (631) away from the second elastic member (650), and the ring-shaped boss (638) is formed with a guide rod connecting groove (639).

63. The damper (1) according to claim 62, characterized in that The guide rod connecting groove (639) is arranged on a side of the body portion (610) facing the spool assembly (500), and the spool assembly (500) is connected to the guide rod connecting groove (639).

64. A damper (1 ) according to any of claims 61 - 63, characterized in that In a compression range of the second elastic member (650), the pilot valve plug (640) is movable relative to the base (630) along an axial direction of the base (630) between a first position and a second position, and the second elastic member (650) provides an elastic force of 10N-50N to the pilot valve plug (640).

65. A damper (1 ) according to any of claims 61 -64, characterized in that The pilot valve plug (640) comprises: A plug sheet (641) is arranged on a side edge of the plug sheet (641) facing the second elastic member (650) and is formed with a plug sheet avoiding groove (642) on a radially inner side of the plug sheet (641); A plug head (643) is arranged on a middle part of a side of the plug sheet (641) away from the second elastic member (650).

66. A damper (1) according to claim 65, characterized in that A groove bottom of the plug sheet avoiding groove (642) is a circular ring plane; or A groove bottom of the plug sheet avoiding groove (642) is a conical surface that is inclined and approaches the second elastic member (650) in a radially outward direction of the plug sheet (641).

67. A damper (1 ) according to any of claims 61 - 66, characterized in that In an axial direction of the cylinder body (100), a distance between a radially outer side of the pilot valve plug (640) and the base (630) is smaller than a distance between a radially inner side of the pilot valve plug (640) and the base (630).

68. A damper (1 ) according to any of claims 61 -67, characterized in that The second elastic member (650) comprises: An outer ring body (651) abuts against the pilot valve plug (640); A plurality of inner elastic arms (652) are connected to an inner periphery of the outer ring body (651) and are arranged at intervals in a circumferential direction, and inner ends of each of the inner elastic arms (652) abut against the base (630).

69. A damper (1) according to claim 68, characterized in that Inner ends of the plurality of inner elastic arms (652) are all planes, and the inner ends of the plurality of inner elastic arms (652) are circumscribed by a same circle.

70. A damper (1) according to claim 68 or 69, characterized in that A width of the inner elastic arm (652) decreases in a direction of being radially inward of the outer ring body (651).

71. A damper (1) according to any of claims 61-70, characterized in that The base (630) comprises: A second body portion (631) is connected to the spool assembly (500), and the second body portion (631) is provided with at least one second balance hole (634); A second flow guide portion (632) extends along a circumferential direction of the second body portion (631), and the second flow guide portion (632) extends from an outer periphery of the second body portion (631) to a side of the flow regulating valve (300).

72. A damper (1) according to claim 71, characterized in that The second flow guide portion (632) is configured with a stop structure (633) that stops a side of the pilot valve plug (640) away from the body portion.

73. Damper (1) according to claim 72, characterized in that The stop structures (633) are multiple, and the multiple stop structures (633) are spaced along the circumference of the base flow guide portion (632).

74. A damper (1 ) according to any of claims 53-73, characterized in that The control valve (400) comprises a valve core assembly (500), which comprises: a valve core (520) movably arranged in the piston (200); a static iron core (430) arranged in the piston (200); a coil assembly (410) mounted in the piston (200), and when the coil assembly (410) is energized, the valve core (520) generates magnetism and is attracted to the static iron core (430); a guide rod (530) penetrating the valve core (520) and connected with the valve core (520), and the pilot valve (600) is connected to one end of the guide rod (530) facing the flow regulating valve (300).

75. A damper (1) according to claim 74, characterized in that The guide rod (530) penetrates the valve core (520) and is connected with the valve core (520).

76. A damper (1) according to claim 74 or 75, characterized in that The static iron core (430) is arranged on the side of the valve core (520) facing the flow regulating valve (300), and a sink (432) is arranged on the side of the static iron core (430) facing the valve core (520); When the flow regulating valve (300) is in an open valve state at an initial position, along the axial direction of the valve core assembly (500), the side of the valve core (520) facing the static iron core (430) is located in the sink (432), and along the axial direction of the valve core assembly (500), the distance between the side of the valve core (520) facing the static iron core (430) and the bottom wall of the sink (432) is L2, and L2 satisfies: 2mm>L2>0.7mm.

77. A damper (1 ) according to any one of claims 74-76, characterized in that The piston (200) comprises a valve body (230); The control valve (400) further comprises: an iron core cover (510) fixed in the piston (200); a magnetic isolation ring (420) mounted in the piston (200), located between the iron core cover (510) and the valve body (230), and separating the coil assembly (410) and the valve body (230).

78. A damper (1) according to claim 77, characterized in that The top of the iron core cover (510) is provided with a mounting sink (511), and a second guide sleeve (512) is arranged in the mounting sink (511), and the guide rod (530) of the valve core assembly (500) penetrates the second guide sleeve (512).

79. A damper (1) according to claim 77 or 78, characterized in that The inner circumferential surface of the iron core cover (510) is provided with a first step portion (513), and the outer circumferential surface of the valve core (520) is provided with a second step portion (524), and the first step portion (513) is stopped on the side of the second step portion (524) facing the iron core cover (510).

80. A damper (1 ) according to any one of claims 77-79, characterized in that The first groove (522) and the second groove (523) are arranged at the axial two ends of the valve core (520), the third elastic member (540) is arranged in the first groove (522) and abuts between the groove bottom of the first groove (522) and the core cover (510) of the shock absorber (1), and the fourth elastic member (550) is arranged in the second groove (523) and abuts between the groove bottom of the second groove (523) and the static core (430).

81. A damper (1) according to any of claims 74-80, characterized in that The side of the static core (430) facing the valve core (520) is provided with a sink (432). When the flow regulating valve (300) is in the closed valve state, the side of the valve core (520) facing the pilot valve (600) is located in the sink (432) along the axial direction of the cylinder body (100).

82. A damper (1) according to claim 81, characterized in that When the flow regulating valve (300) is in the closed valve state, the distance between the side of the valve core (520) facing the pilot valve (600) and the slot opening of the sink (432) is L1, and L1 satisfies: 0.5mm>L1>0.1mm. The distance between the side of the valve core (520) facing the pilot valve (600) and the bottom wall of the sink (432) is L2, and L2 satisfies: 2mm>L2>0.7mm.

83. Damper (1) according to claim 82, characterized in that When the flow regulating valve (300) is in the open valve state at the initial position, the distance between the side of the valve core (520) facing the static core (430) and the slot opening of the sink (432) is L1 along the axial direction of the valve core assembly (500), and L1 satisfies: 0.5mm>L1>0.1mm.

84. A damper (1) according to claim 82 or 83, characterized in that The outer diameter of the valve core (520) is D1, and the inner diameter of the sink (432) is D2. When the valve core (520) moves to be close to the static core (430), the distance between the inner side wall of the sink (432) and the outer peripheral wall of the valve core (520) is constant or gradually increases, so that (D2-D1)×(L1+L2) is constant or gradually increases.

85. A damper (1) according to claim 84, characterized in that The outer diameter of the valve core (520) is D1, the inner diameter of the sink (432) is D2, and the depth of the sink (432) is L. When the valve core (520) moves to be close to the static core (430), the distance between the inner side wall of the sink (432) and the outer peripheral wall of the valve core (520) is constant, so that (D2-D1)×L is constant; or, When the valve core (520) moves to be close to the static core (430), the distance between the inner side wall of the sink (432) and the outer peripheral wall of the valve core (520) gradually increases, so that (D2-D1)×L gradually increases.

86. Damper (1) according to claim 84 or 85, characterized in that The valve core (520) is provided with an eighth flow channel (521) penetrating through the opposite sides of the valve core (520) along the axial direction of the valve core (520).

87. A damper (1 ) according to any of claims 84-86, characterized in that The valve core assembly (500) further comprises: A third elastic member (540) and a fourth elastic member (550) are sleeved on the guide rod (530) and arranged on both sides of the moving direction of the valve core (520) respectively, and the third elastic member (540) and the fourth elastic member (550) apply elastic force to the valve core (520) together to keep the position of the valve core (520) stable.

88. A vehicle characterized by A damper (1) according to any one of claims 1-87.

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