Magneto-rheological shock absorber and vehicle

Abstract

The invention relates to a magneto-rheological shock absorber and a vehicle. The magneto-rheological shock absorber comprises an outer cylinder; the guide seat assembly is arranged in the cavity of the outer cylinder near the end part of the opening of the outer cylinder in a state that the assembly is completed, and the guide seat assembly comprises a guide seat body; the piston assembly comprises a piston rod and a piston assembly, the piston assembly is arranged below the guide seat assembly in the cavity of the outer cylinder, and the piston rod is fixedly connected with the piston assembly; wherein at least one annular protruding structure protruding inwards from the inner wall in the radial direction is arranged on the inner wall of the outer cylinder, the protruding structure can be connected with at least one annular containing groove formed in the guide seat body in a clamped mode, and a cushion containing part used for containing a cushion is formed in the lower end of the guide seat body. And the buffer pad accommodating part can be clamped with the buffer pad in a shape locking manner.

Description

Technical Field

[0001] The present disclosure relates to a magnetorheological damper and a vehicle including the magnetorheological damper. Background Art

[0002] In the field of motor vehicles, shock absorbers are components used to accelerate the attenuation of frame and body vibrations to improve the ride comfort of the car. Magnetorheological shock absorbers are semi-active shock absorbers with magnetorheological materials as the medium. They can adjust the mechanical properties of the shock absorber, such as damping and stiffness, according to changes in the external environment, under the drive of changing currents, to achieve an optimized vibration reduction effect. A typical magnetorheological shock absorber includes a cylindrical working cylinder, a guide assembly and a piston assembly. The piston assembly includes a piston assembly and a piston rod connected to the piston assembly, and an electromagnetic coil is arranged in the piston assembly. In addition, a magnetorheological fluid is arranged in the working cylinder. The magnetorheological fluid is a magnetic soft particle suspension. When the liquid is injected into the electromagnetic coil in the shock absorber piston assembly, the magnetic field of the coil will change its rheological properties. Therefore, the magnetorheological fluid shock absorber has the characteristics of compact structure and small external input energy.

[0003] The guide assembly of the magnetorheological damper is usually fixedly installed in the retaining spring groove at the outlet of the working cylinder by a retaining spring to achieve a fixed connection with the working cylinder. However, this structure has the following disadvantages: during the process of filling and oiling the retaining spring groove, when the guide seat passes through the corresponding area, leakage may occur.

[0004] In addition, the piston rod and guide seat are generally made of metal. When the shock absorber is at its stretching limit, the piston rod drives the piston to hit the guide seat. In order to reduce the instantaneous impact force, a buffer pad needs to be set on the guide seat. How to ensure that the buffer pad can be firmly and easily installed on the guide is also an issue worth considering. Summary of the invention

[0005] Therefore, an object of the present application is to provide a magnetorheological damper and a vehicle including the magnetorheological damper, which at least partially solve the problems in the prior art.

[0006] According to a first aspect of the present application, a magnetorheological damper is provided, comprising: an outer cylinder, the outer cylinder being a cylindrical structure with one end open and the other end closed and forming a cavity therein;

[0007] A guide seat assembly, which is arranged in the cavity of the outer tube near the end of the opening of the outer tube in an assembled state, and comprises a guide seat body;

[0008] A piston assembly, the piston assembly comprising a piston rod and a piston assembly. In an assembled state, the piston assembly is arranged in the cavity of the outer cylinder below the guide seat assembly, and the piston rod is fixedly connected to the piston assembly;

[0009] Wherein, at least one protruding structure is provided on the inner wall of the outer cylinder, protruding radially inwardly from the inner wall in an annular manner, and the protruding structure can be engaged with at least one annular receiving groove formed on the guide seat body, and

[0010] Wherein, a buffer pad receiving portion for receiving a buffer pad is formed at the lower end portion of the guide seat body, and the buffer pad receiving portion and the buffer pad can be engaged with each other in a form-locking manner.

[0011] According to the magnetorheological damper of the present application, on the one hand, by replacing the structure of the retaining spring and the retaining spring groove, at least one protruding structure preferably integrally riveted inward from the inner wall of the outer cylinder is engaged with the annular groove on the guide seat body, which can save processing costs and reduce assembly difficulty in addition to avoiding the disadvantage of leakage of the retaining spring groove during the gas filling and oil filling process. In addition, by designing the buffer pad receiving portion below the guide seat body to be engaged with the buffer pad in a form-locking manner, the assembly difficulty can be further reduced and the buffer pad can be more conveniently disassembled and assembled, for example, for replacement purposes.

[0012] According to some embodiments of the present application, the protruding structure is constituted by a plurality of discrete, regularly or irregularly arranged protruding parts, and the plurality of protruding parts can be respectively engaged with the annular receiving groove. According to other embodiments, the protruding structure can also be constituted by a continuous annular flange, and the annular flange can be engaged with the annular receiving groove.

[0013] According to some embodiments of the present application, two annular sealing grooves are formed on the outer side wall of the guide seat body, and a sealing ring is respectively accommodated in the two sealing grooves, and either of the two annular sealing grooves can be used as the annular receiving groove. The advantage of this embodiment is that it is not necessary to process an annular receiving groove for receiving the protruding structure on the guide seat body, but the sealing groove used to install the sealing ring is used as the annular receiving groove, which not only has the advantage of saving processing costs, but also the protruding structure squeezes the sealing ring when it is inserted into the sealing groove, thereby enhancing the sealing effect.

[0014] According to some embodiments of the present application, two protruding structures are provided, and the two protruding structures are respectively engaged with the two sealing grooves. This embodiment further enhances the axial fixing effect and sealing effect of the guide seat assembly.

[0015] According to some embodiments of the present application, the buffer pad receiving portion is configured as an L-shaped embedding groove in the cross section, and the upper portion of the buffer pad is correspondingly configured as an inverted L-shaped clip in the cross section that is locked with the L-shaped embedding groove. This structure is easier to process and can well realize the snap-on and disassembly of the buffer pad.

[0016] According to some embodiments of the present application, the buffer pad is constructed to include a cylindrical first part with a consistent outer diameter and a hollow truncated cone-shaped second part whose outer diameter gradually decreases along the axial direction of the guide seat body and in the direction away from the guide seat body. Thus, when the piston assembly hits the guide seat assembly, the piston assembly first hits the hollow truncated cone-shaped second part, which is first compressed and buffers the impact force, and the buffered impact force continues to be transmitted to the cylindrical first part, which is compressed and deformed and buffers the impact force again, thereby on the one hand being able to increase the service life of the shock absorber, and on the other hand being able to achieve a "soft first and hard later" body feeling compared to a cylindrical buffer pad with consistent upper and lower diameters, thereby improving the passenger's riding experience. Preferably, the inner diameter of the hollow truncated cone-shaped second part is constructed to gradually decrease along the axial direction of the guide seat body and in the direction away from the guide seat, and the axial length of the first part is less than the axial length of the second part, thereby being able to achieve a better passenger body feeling.

[0017] According to some embodiments of the present application, the piston assembly includes a piston winding assembly, and the piston winding assembly includes a magnetic core, the magnetic core is provided with at least one coil groove for winding a coil, and an upper mounting hole and a lower mounting hole that are connected to each other are provided inside the magnetic core, the upper mounting hole is used to receive the lower end of the piston rod, and the lower mounting hole is used to receive a conductive connection part for conductively connecting the wire in the piston rod to the coil, wherein the upper mounting hole and the lower mounting hole are respectively provided with an upper expansion part and a lower expansion part with gradually increasing inner diameters at the outward ends. The upper expansion part and the lower expansion part will not damage the related parts to be installed in the upper mounting hole and the lower mounting hole when assembling the piston assembly through the upper expansion part and the lower expansion part. The design of the upper expansion part and the lower expansion part can make the assembly of the shock absorber according to the present application more convenient.

[0018] The piston assembly also includes a piston housing and two piston pressure plates arranged above and below the piston housing. A pressure plate retaining spring groove for receiving the retaining spring is arranged on the upper piston pressure plate. The surface of the pressure plate retaining spring groove in contact with the retaining spring is configured as a conical surface. Thus, when the upper piston pressure plate is inserted into the piston rod from top to bottom, the conical surface of the conical retaining spring groove in contact with the retaining spring can continuously apply a clamping force to the retaining spring, thereby making the connection between the piston rod and the piston assembly more secure.

[0019] According to some embodiments of the present application, the piston pressure plate includes a pressure edge and a top portion, a plurality of through holes are provided between the pressure edge and the top portion, and adjacent through holes are separated by a plurality of connecting bridges, the plurality of connecting bridges respectively connect the pressure edge and the top portion, and the through holes are in fluid communication with a main flow channel provided in the piston assembly. With the above structure, the volume and weight of the piston pressure plate can be reduced while the strength of the piston pressure plate can be ensured.

[0020] According to some embodiments of the present application, the piston pressure plate is provided with at least one bypass hole on the top, and at least one of the at least one bypass hole is in fluid communication with a bypass channel provided in the piston winding assembly. The bypass channel and the bypass hole can assist the flow of fluid inside the piston assembly.

[0021] According to some embodiments of the present application, a positioning mark, such as a positioning hole, is provided on the piston pressure plate for assisting positioning. The positioning mark can make it easier to align the positions of the through holes of the upper and lower piston pressure plates.

[0022] According to some embodiments of the present application, the outer cylinder is configured as a two-piece structure and includes an outer cylinder body located above and a reinforcing cylinder located below the outer cylinder body and having an increased wall thickness relative to the outer cylinder body. Preferably, the outer diameter of the outer cylinder body is the same as the outer diameter of the reinforcing cylinder, and the lower end of the outer cylinder body is sealed and connected to the upper end of the reinforcing cylinder by welding.

[0023] According to some embodiments of the present application, the lower end of the outer cylinder body is provided with a first groove, and the upper end of the reinforcing cylinder is provided with a flange, and the flange can be accommodated in the first groove and welded thereto. Through this two-piece design with different wall thicknesses, on the one hand, the strength of the outer cylinder at the connection with the stabilizer bracket can be improved, and on the other hand, the overall wall thickness of the outer cylinder does not need to be increased in order to increase the connection strength, thereby reducing the weight and processing cost of the outer cylinder.

[0024] According to some embodiments of the present application, flange structures are provided on the upper and lower parts of the piston housing, and the flange structures are configured to receive and fix the pressure edge of the piston pressure plate. The flange structures can achieve simpler assembly of the piston assembly.

[0025] According to a second aspect of the present application, a vehicle is provided, the vehicle comprising the magnetorheological damper according to the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] The exemplary embodiments of the present application are explained in more detail below in conjunction with the accompanying drawings. In the drawings:

[0027] Figure 1A schematic cross-sectional view showing a magnetorheological damper according to an embodiment of the present application;

[0028] Figure 2 A schematic exploded view of a magnetorheological damper according to one embodiment of the present application is shown;

[0029] Figure 3 An exploded view of the guide seat assembly 1000 is shown;

[0030] Figure 4 A schematic diagram showing the guide seat assembly in a completed assembly state;

[0031] Figure 5 Show Figure 4 A cross-sectional view of the middle guide seat assembly;

[0032] Figure 6 An exploded view of the piston assembly 4000 is shown;

[0033] Figure 7 A schematic diagram showing the piston assembly in a completed assembly state;

[0034] Figure 8 A cross-sectional view showing a portion of the piston assembly together with the piston rod;

[0035] Fig. 9 A schematic perspective view of a piston winding assembly 410 is shown;

[0036] Fig.10 A cross-sectional view of a piston winding assembly 410 is shown;

[0037] Fig.11 A schematic perspective view showing a piston pressure plate 420 according to an embodiment of the present application;

[0038] Fig.12 A cross-sectional view of the piston pressure plate 420 is shown;

[0039] Fig.13 The partial details of the lower end portion of the piston rod 210 connected to the piston assembly 4000 or the piston winding assembly 410 are shown;

[0040] Fig.14 A two-piece structure including an outer cylinder body and a reinforcing cylinder is schematically shown. DETAILED DESCRIPTION

[0041] The following is a description of exemplary embodiments of the present application in conjunction with the accompanying drawings, including various details of the embodiments of the present application to facilitate understanding, which should be considered as merely exemplary. Therefore, it should be recognized by those of ordinary skill in the art that various changes and modifications can be made to the embodiments described herein without departing from the scope and spirit of the present application. Similarly, for the sake of clarity and conciseness, the description of well-known functions and structures is omitted in the following description.

[0042] Figure 1 A schematic cross-sectional view of a magnetorheological damper according to an embodiment of the present application is shown, Figure 2 A schematic exploded view of a magnetorheological damper according to an embodiment of the present application is shown. Figure 1 and Figure 2 It can be seen that the magnetorheological damper 1 according to one embodiment of the present application includes an outer cylinder 230, which is a cylindrical structure with one end open and the other end closed, preferably a cylindrical structure, for example Figure 1 and 2 In the embodiment, the outer cylinder 230 is constructed as a cylindrical structure which is closed at the lower end and open at the upper end. A columnar cavity is formed inside the outer cylinder 230. In the installed state, the guide seat assembly 1000 is installed at the open end of the magnetorheological damper 1 and thus its open end is closed by the guide seat assembly.

[0043] In addition, Figure 1 It can be seen that in the above-mentioned cavity, the piston assembly 4000 and the floating piston 220 are sequentially installed below the guide seat assembly 1000. The piston assembly is connected to a piston rod 210, which passes through the guide seat assembly and extends to the outside of the outer cylinder 230. The piston rod is hollow and contains a wire 214. In the installed state, the space between the closed end (the lower end in the figure) of the outer cylinder 230 and the floating piston 220 is filled with a high-pressure gas such as nitrogen, so that the space forms a high-pressure gas chamber 2313. The space between the guide seat assembly 1000 and the floating piston 220 is filled with a magnetorheological fluid, so that the space forms a liquid storage cavity. The piston assembly 4000 divides the liquid storage cavity into an upper chamber 2315 and a lower chamber 2317. The upper chamber and the lower chamber are fluidically connected through a flow channel provided inside the piston assembly.

[0044] The piston rod 210 can drive the piston assembly 4000 to reciprocate in the liquid storage chamber of the outer cylinder 230, so that the magnetorheological fluid also flows back and forth between the upper chamber 2315 and the lower chamber 2317 and generates hydraulic damping. When the coil set in the piston assembly 4000 is energized through the wire 214, the magnetic field generated by the energization of the coil will affect the viscosity of the magnetorheological fluid and further affect its hydraulic damping. By changing the magnitude of the energized current, the magnitude of the hydraulic damping can be changed, thereby meeting the vibration reduction requirements under different road conditions. In addition, when the piston assembly 4000 reciprocates in the outer cylinder 230, the relative up and down movement of the floating piston 220 can compensate for the volume change caused by the piston rod 210 entering and exiting the liquid storage chamber. In the meaning of this application, the entirety of the piston rod 210 and the piston assembly 4000 after being connected is called a piston assembly.

[0045] Refer to the following Figures 3 to 5 The detailed structure of the guide seat assembly 1000 is described, wherein: Figure 3 An exploded view of the guide seat assembly 1000 is shown, Figure 4 A schematic diagram showing the guide seat assembly in the assembled state. Figure 5 Show Figure 4 Cross-sectional view of the middle guide seat assembly.

[0046] The guide seat assembly 1000 includes a guide seat body 100, Figure 4 and Figure 5 It can be seen that the guide seat body 100 is configured as a substantially cylindrical structure and has a through hole 103 extending from its upper surface to its lower surface formed therein, through which the piston rod 210 can pass and be guided. Figure 5 A sleeve 120 is provided near the upper end of the through hole 103. The inner wall of the sleeve contacts the piston rod and is therefore coated with a wear-resistant coating. The wear-resistant coating may be, for example, a polytetrafluoroethylene coating. Preferably, the sleeve 120 is interference fit with the through hole 103, so that the sleeve 120 will not be moved when the piston rod 210 moves up and down. Of course, other methods may also be considered to fix the sleeve and the through hole, which will not be described here. An oil seal 130 and an oil seal pressure plate 140 are provided below the sleeve 120 near the lower end of the through hole. The oil seal pressure plate 140 fixes the oil seal 13 to the lower part of the hole 103. The oil seal acts as a seal inside the guide seat to prevent the magnetorheological fluid from invading the interior of the guide seat assembly as the piston rod moves.

[0047] A dust seal 110 is provided above the sleeve 120 to prevent dust and dirt from entering the shock absorber. The dust seal is partially received in the through hole 103 and extends upward from the through hole 103 to the outside of the guide seat body 100 .

[0048] Depend on Figure 4It can be further seen that two annular sealing grooves 101 are formed on the outer wall of the guide seat body 100, and a sealing ring 160 is respectively accommodated in the two sealing grooves 101. When the guide seat assembly is installed in the outer tube 230, the sealing ring contacts the inner wall of the outer tube and has a sealing effect.

[0049] In addition, a buffer pad receiving portion 102 is formed at the lower end of the guide seat body 100. According to a preferred embodiment, Figure 5 It can be seen that the buffer pad receiving portion is constructed in the form of an L-shaped embedding groove in the cross section, and the upper part of the buffer pad is correspondingly constructed in the form of an inverted L-shaped clip in the cross section that is form-locked with the L-shaped embedding groove and can therefore be form-locked with the L-shaped embedding groove. This snap-fit ​​structure can not only achieve firm fixation but also facilitate installation and disassembly.

[0050] In the prior art, the buffer pad used for the guide seat assembly is usually constructed as a cylindrical structure with a uniform diameter. However, the compression deformation stroke of the cylindrical buffer pad is very short and therefore its instantaneous impact force is still large, which can easily damage the piston or the guide seat and reduce the service life of the shock absorber. According to the preferred embodiment of the present application, Figure 5 As shown, the buffer pad 150 is constructed to include a cylindrical first portion 152 with a uniform outer diameter and a hollow frustum-shaped second portion 153 whose outer diameter gradually decreases along the axial direction of the guide seat assembly 1000. Therefore, when the piston assembly 4000 hits the guide seat assembly 1000, the piston assembly 4000 first hits the hollow frustum-shaped second portion 153, and the second portion 153 is first compressed and buffers the impact force. The buffered impact force continues to be transmitted to the cylindrical first portion 152, and the first portion 152 is compressed and deformed and buffers the impact force again, thereby on the one hand being able to increase the service life of the shock absorber, and on the other hand being able to achieve a "soft first and hard later" feel compared to a cylindrical buffer pad with uniform upper and lower diameters, thereby improving the passenger's riding experience. In a preferred embodiment, as Figure 5 As shown, the inner diameter of the second portion 153 also gradually decreases along the axial direction of the guide seat assembly 1000, but those skilled in the art can design it to have a uniform inner diameter or other shapes according to different load conditions. Here, the direction in which the outer diameter and the inner diameter gradually decrease is along the axial direction of the guide seat assembly 1000 or the guide seat body 100 away from the guide seat body.

[0051] In a preferred embodiment, the axial length of the second portion 153 is greater than the axial length of the first portion 152, thereby achieving better cushioning performance for passengers.

[0052] Furthermore, the outer diameter of the first portion 152 is preferably designed to be the same as the outer diameter of the guide seat body 100 adjacent thereto, thereby achieving a consistent overall appearance.

[0053] In the prior art, in order to prevent the guide seat assembly from slipping out of the outer cylinder, a retaining spring is usually used to fix it at its upper end. The retaining spring is designed as a circular ring-shaped component, which is installed in the retaining spring groove processed in the inner wall of the outer cylinder and protrudes radially inward to form a stopper for the guide seat assembly. However, this design has the following disadvantages: on the one hand, the structure of the retaining spring and the retaining spring groove requires processing the retaining spring groove and adapting the corresponding retaining spring, which has high time cost and processing cost. On the other hand, during the installation process of the magnetorheological damper, it needs to be inflated and injected with liquid. During this process, when the guide seat passes through the area where the retaining spring groove is located, liquid leakage will occur, resulting in waste of magnetorheological fluid and the need for costly cleaning.

[0054] To this end, according to a preferred embodiment of the present application, for example, see Figure 2 A protruding structure 233 protruding radially inward from the inner wall of the outer cylinder 230 is processed on the outer cylinder 230. The protruding structure 233 is annular and can be engaged with at least one annular receiving groove formed on the guide seat body 100 to achieve axial fixation of the guide seat assembly 1000.

[0055] According to the preferred embodiment of the present application, Figure 2 As shown, the annular protruding structure 233 is constituted as a circle of discrete, regularly or irregularly arranged protrusions, such as bumps. However, it is also conceivable to design the protruding structure 233 as an annular continuous structure, such as a continuous annular flange. Importantly, the protruding structure can be snapped into an annular receiving groove provided in the guide seat body and achieve a fixing effect.

[0056] According to a preferred embodiment of the present application, the protruding structure 233 can be directly inserted into, for example, Figure 4 In one of the two sealing grooves 101 shown, the advantage of this design is that, on the one hand, it is not necessary to process an additional annular receiving groove, and on the other hand, the sealing effect can be further improved by squeezing the sealing ring 160 in the sealing groove through the protruding structure.

[0057] Of course, it is also conceivable that an annular receiving groove specifically used for receiving the protruding structure is provided on the guide seat body 100 .

[0058] In the above preferred embodiment, only one protruding structure 233 is provided. However, in order to enhance the fixing effect, it is also possible to consider using two or more protruding structures 233. For example, when two protruding structures 233 are used, they can correspond to the two annular receiving grooves on the guide seat body 100. These two annular receiving grooves can be the two sealing grooves 101, or two additionally processed annular receiving grooves, or one sealing groove 101 and one additionally processed annular receiving groove.

[0059] Preferably, the protruding structure 233 is integrally formed by riveting the outer tube 230 inward, but other processing methods may also be considered and will not be described in detail here.

[0060] The structure of the piston assembly 4000 of the piston assembly will be described below with reference to the accompanying drawings. Figure 6 An exploded view of the piston assembly 4000 is shown, Figure 7 A schematic diagram showing the piston assembly in the assembled state, Figure 8 A cross-sectional view of a portion of the piston assembly together with the piston rod 210 is shown.

[0061] Reference Figure 6 and Figure 7 The piston assembly 4000 includes a piston housing 400 , a piston winding assembly 410 and two upper and lower piston pressure plates 420 , and the piston winding assembly 410 is sleeved in the piston housing 400 .

[0062] In the installed state, the piston assembly 4000 is arranged in the outer cylinder 230. In order to prevent the magnetorheological fluid from flowing through the gap between the piston shell 400 and the inner wall of the outer cylinder 230, the piston assembly 4000 also includes a piston ring sleeve 430. A groove 401 is provided on the outer wall of the piston shell 400. The piston ring sleeve 430 is sleeved on the groove 401. The outer diameter of the piston ring sleeve 430 is larger than the outer diameter of the piston shell 400 and its outer surface is coated with a wear-resistant coating, so as to reduce the friction loss between the piston assembly and the inner wall of the shock absorber. The wear-resistant coating can be, for example, a polytetrafluoroethylene coating. In order to facilitate the piston ring sleeve 430 to be sleeved in the groove 401 and reduce the possibility of the magnetorheological fluid flowing through the gap between the piston shell 400 and the inner wall of the outer cylinder 230, an opening 431 is provided on the piston ring sleeve 430. The opening 431 runs through the upper and lower end faces of the piston ring sleeve 430 from the upper left to the lower right in the figure.

[0063] Fig. 9 and Fig.10 The structure of the piston winding assembly 410 is shown, wherein: Fig. 9 A schematic diagram showing a piston winding assembly 410 is shown, Fig.10 A cross-sectional view of piston winding assembly 410 is shown.

[0064] The piston winding assembly 410 includes a magnetic core 450, which is provided with two coil grooves 451. The coil grooves 451 are used to wind the coil, and after the winding is completed, the coil is encapsulated with a non-magnetic material, such as PA66, by a process such as injection molding. The magnetic core 450 is provided with an upper mounting hole 452 and a lower mounting hole 453 that pass through the upper and lower parts. The upper mounting hole 452 is used to receive the lower end of the piston rod 210, and the lower mounting hole is used to receive the conductive connection part 443 that will be described later and is used to connect the wire 214 in the piston rod to the coil. Fig.10 It can be seen that the outward ends of the upper mounting hole 452 and the lower mounting hole 453 are respectively provided with an upper expansion portion 454 and a lower expansion portion 455 with gradually increasing inner diameters. Figure 8 It can be seen that a conductive connection part 443 is installed in the lower mounting hole 453, and the coil is conductively connected to the conductive connection part 443. The conductive connection part 443 is connected to an external power source through a wire 214 arranged inside the hollow piston rod 210, so as to supply current to the coil. A lower sealing ring 442 is preferably installed on the conductive connection part 443, which can further enhance the sealing of the piston assembly. During assembly, the coil is first wound in the coil groove 451, and then the conductive connection part 443 is installed in the lower mounting hole 453 from bottom to top. Since a lower expansion part 455 is provided at the lower mounting hole 453, scratches on the lower sealing ring 442 can be avoided when the conductive connection part 443 is inserted.

[0065] Fig.13 The lower end of the piston rod 210 connected to the piston assembly 4000 or the piston winding assembly 410 is shown in detail. It can be seen that the piston rod 210 is provided with an upper sealing ring groove 211 and a retaining ring groove 212, which are used to install the upper sealing ring 441 and the retaining ring 440 (see FIG. Figure 8 ).Depend on Fig.13It can be seen that the lower end of the piston rod 210 is divided into two sections with different diameters on the right side of the upper sealing ring groove 211, namely the first section 213 and the second section 215, and the first section transitions to the second section through the transition section 217, preferably smoothly. The diameter of the first section is D2, and the diameter of the second section is D1, and the diameters D1 and D2 are designed so that D1 is slightly larger than D2. It can be seen that the upper sealing ring groove 211 is arranged on the first section 213 with a smaller diameter, and the retaining ring groove is arranged on the second section 215 with a larger diameter. Therefore, when the piston rod 210 is inserted into the upper mounting hole 452, it can be assembled more easily because the upper mounting hole 452 is provided with an upper expansion chamfer 454, and the first section 213 with a reduced diameter exists on the other hand. In the installed state, there is a gap between the first section 213 and the inner wall of the upper mounting hole 452, and the part of the second section 215 inserted into the upper mounting hole 452 has an interference fit with the inner wall of the upper mounting hole 452. Therefore, it is difficult for the magnetorheological fluid to pass between the interference-fit second section 215 and the inner wall of the upper mounting hole 452. Even if a small amount of magnetorheological fluid penetrates in, it will be blocked by the sealing ring 441 arranged in the upper sealing ring groove 211, thereby achieving a better sealing effect.

[0066] Fig.11 A schematic perspective view of a piston pressure plate 420 according to an embodiment of the present application is shown. Fig.12 A cross-sectional view of the piston pressure plate is shown.

[0067] According to an embodiment of the present application, the piston pressure plate 420 is substantially in the shape of a hollow truncated cone. The piston pressure plate 420 includes a pressure edge portion 421 and a top portion 422. A plurality of through holes 424 are provided between the pressure edge portion 421 and the top portion 422. A plurality of bridge portions 423 are provided between two through holes 424. The plurality of bridge portions connect the pressure edge portion 421 and the top portion 422, respectively. Through the plurality of bridge portions 423, the volume of the piston pressure plate 420 is reduced while the strength of the piston pressure plate 420 is ensured. Two identically constructed piston pressure plates 420 are respectively arranged above and below the piston winding assembly 410. The piston rod 210 passes through the upper piston pressure plate 420 and extends into the piston winding assembly 410 and is connected thereto.

[0068] The piston housing 400 is, for example, constructed in a cylindrical shape as a whole. Figure 8It can be seen that in a preferred embodiment, the upper and lower parts of the piston housing 400 are provided with a flange structure 402, and the flange structure 402 is used to fix the pressure edge portion 421 of the piston pressure plate 420 in the piston housing 400. Preferably, in order to facilitate the installation of the piston pressure plate 420 in the piston housing 400, the upper and lower parts of the pressure edge portion 421 are chamfered. Of course, those skilled in the art can also think of using other methods besides flanges to fix the piston pressure plate to the piston housing, which will not be repeated here.

[0069] An exemplary assembly method is as follows: after the magnetic core 450 is subjected to the injection molding process described above, the lower piston pressing plate is first fixed in the piston housing 400 by flanging with a flanging machine, and then the magnetic core 450 is placed in the piston housing 400 and the piston rod 210 is pressed into the magnetic core, and then the upper piston pressing plate 420 is inserted into the piston rod from top to bottom, and the upper piston pressing plate is fixed in the piston housing 400 by means of flanging 402 with the flanging machine. In order to prevent the piston rod 210 from falling out of the piston assembly 4000, a retaining spring 440 is installed on the retaining spring groove 212 of the piston rod 210, and correspondingly, a retaining spring groove 427 for the retaining spring 440 is provided in the upper piston pressing plate (see Fig.12 ), the retaining spring 440 is clamped in the retaining spring groove 427. According to a preferred embodiment of the present application, the retaining spring groove 427 is configured to be conical, so that when the upper piston pressure plate is inserted into the piston rod from top to bottom, the conical surface of the conical retaining spring groove 427 in contact with the retaining spring can continuously apply a pressing force to the retaining spring 440, so that the connection between the piston rod 210 and the piston assembly 4000 is more secure.

[0070] In a preferred embodiment according to the present application, Fig.11 As shown, the through hole 424 is designed as a waist-shaped hole. For the convenience of processing and a more harmonious appearance, all the through holes 424 are preferably constructed in the same way and evenly distributed around the axis of the piston pressure plate 420. Figure 1 and Figure 8 The upper chamber 2315 and the lower chamber 2317 separated by the piston assembly 4000 are fluidically connected to the main flow channel 403 through the through hole 424.

[0071] In a preferred embodiment of the present application, the pressure plate 420 is provided with a plurality of bypass holes 425 on its top 422 in addition to the through holes 424. Figure 8As shown, the bypass hole 425 penetrates the piston platen 420, and the bypass hole 425 is in fluid communication with the bypass channel 412. Through the through hole 424 and the bypass hole 425, when the piston assembly 4000 moves up and down, the magnetorheological fluid can not only stably flow through the through hole 424 and the main through channel 403, but also flow through the bypass hole 425 and the bypass channel 412. Preferably, all the bypass holes 425 are constructed in the same manner and are evenly distributed around the axis of the piston platen 420. It is further preferred that, as Fig.13 As shown, the bypass holes and the bridge portions 421 are arranged one-to-one in number and circumferential position. For example, four bridge portions 421 are provided here, and four bypass holes 425 are arranged one-to-one in circumferential direction on the top 422 of the piston cover plate 420 in correspondence with the four bridge portions. Note that the number and position of the bypass holes and the bridge portions are not limited to those shown in the figure, but can be adjusted according to actual needs. For example, only one bypass hole can be provided, but four bridge portions are still provided.

[0072] In order to design the volume of the piston assembly 4000 to be relatively compact, and because it is necessary to reserve a design space for the upper mounting hole 452 for the magnetic core 450, the bypass channel 412 is designed to include an upper deflected section 4121 and a lower vertical section 4122. In addition, in order to make the positions of the through holes 424 on the two piston pressure plates 420 and the bypass holes 425 on the two piston pressure plates 420 correspond one to another, the piston pressure plates 420 are preferably provided with positioning marks, such as positioning holes 426, which play a role in assisting positioning during installation.

[0073] The outer cylinder of the shock absorber is usually fixedly connected to a stabilizer, and the stabilizer is connected to the lateral stabilizer bar of the vehicle suspension through, for example, a stabilizer bar ball head. The outer cylinder in the prior art is basically constructed as a cylindrical structure with a uniform wall thickness, and the stabilizer is connected to the lower part of the outer cylinder, which makes it easy for some problems to occur at the connection. For example, when the working conditions are bad, greater stress is generated, and there is a risk of fracture. For this reason, there is a solution in the prior art to thicken the wall thickness of the outer cylinder as a whole, but this solution is more expensive and more difficult to process. According to a preferred embodiment of the present application, Fig.14 As shown, the outer cylinder 230 is constituted as a two-piece structure, including an outer cylinder body 229 with a conventional wall thickness and a reinforcing cylinder 231 with an increased wall thickness, the outer cylinder body 229 and the reinforcing cylinder 231 are both cylindrical, for example, and the lower end of the outer cylinder body 229 and the upper end of the reinforcing cylinder 231 can be sealed and connected by welding, for example. In an exemplary embodiment, the lower end of the outer cylinder body 229 is provided with a first groove 2301, and the upper end of the reinforcing cylinder 231 is provided with a flange 2311, and the flange 2311 can be accommodated in the first groove 2301 and welded thereto.

[0074] like Fig.14 As shown, the outer cylinder body 229 and the reinforcing cylinder 231 have the same outer diameter, so that the appearance of the outer cylinder is more integrated, and the wall thickness of the reinforcing cylinder 231 is greater than the wall thickness of the outer cylinder body 229. In other words, the inner diameter of the reinforcing cylinder 231 is smaller than the inner diameter of the outer cylinder body 229. Here, the wall thickness of the outer cylinder body 229 can be selected as 2 mm, for example, and the wall thickness of the reinforcing cylinder 231 is not less than 5 mm. The stabilizer bracket 232 is fixedly mounted on the reinforcing cylinder 231 shown, and the bottom of the reinforcing cylinder is provided with a bottom cover 300, and the bottom cover 300 is sealed and connected with the reinforcing cylinder 231, for example, by welding. The other end of the reinforcing cylinder 231 is provided with a second circular groove 2312, and the outer wall of the bottom cover 300 is fitted with the inner wall of the second circular groove 2312, and the bottom cover 300 is sealed and connected with the reinforcing cylinder 231 by welding. In an exemplary embodiment, the magnetorheological shock absorber also includes a connecting rod 310 and a lower insert arm 320, and the two ends of the connecting rod 310 are fixedly connected to the bottom cover 300 and the lower insert arm 320 respectively, thereby, the outer cylinder 230 is fixedly connected to the lower insert arm 320 through the bottom cover 300 via the connecting rod 310, and the lower insert arm 320 can be connected to the frame of the vehicle.

[0075] This design can, on the one hand, improve the strength of the outer cylinder at the connection with the stabilizer bracket 232 and reduce the risk of breakage at the connection. On the other hand, it is not necessary to increase the wall thickness of the outer cylinder 230 as a whole in order to increase the connection strength, thereby reducing the weight and processing cost of the outer cylinder 230.

[0076] The technical solution of the present application is explained above with exemplary preferred implementation modes. It should be noted that the above implementation modes are only used to illustrate the technical solution of the present application, rather than to limit it; although the present application is described in detail with reference to the aforementioned implementation modes, a person of ordinary skill in the art should understand that: it is still possible to modify the technical solutions described in the aforementioned implementation modes, or to replace some or all of the technical features therein by equivalents; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the various implementation modes of the present application, and they should all be included in the scope of the claims and specification of the present application. In particular, as long as there is no structural conflict, the various technical features mentioned in each implementation mode can be combined in any way. The present application is not limited to the specific implementation modes disclosed herein, but includes all technical solutions that fall within the scope of the claims.

Claims

1. A magnetorheological damper (1), characterized in that: The magnetorheological damper comprises: An outer cylinder (230), the outer cylinder being a cylindrical structure with one end open and the other end closed and forming a cavity inside; A guide seat assembly (1000), which is arranged in the cavity of the outer cylinder near the open end of the outer cylinder in an assembled state, and comprises a guide seat body (100); A piston assembly, the piston assembly comprising a piston rod (210) and a piston assembly (4000); in an assembled state, the piston assembly is arranged below the guide seat assembly (1000) in the cavity of the outer cylinder, and the piston rod is fixedly connected to the piston assembly; Wherein, at least one protruding structure (233) is provided on the inner wall of the outer cylinder and protrudes radially inward from the inner wall in an annular manner, and the protruding structure can be engaged with at least one annular receiving groove formed on the guide seat body (100), and A buffer pad receiving portion (102) for receiving a buffer pad (150) is formed at the lower end of the guide seat body (100), and the buffer pad receiving portion can be engaged with the buffer pad in a form-locking manner.

2. The magnetorheological damper according to claim 1, characterized in that: The protruding structure (233) is constituted of a plurality of discrete, regularly or irregularly arranged protruding portions, and each of the plurality of protruding portions can be snap-fitted with the annular receiving groove.

3. The magnetorheological damper according to claim 1, characterized in that: The protruding structure (233) is configured as a continuous annular flange, which can be snap-fitted into the annular receiving groove.

4. The magnetorheological damper according to any one of claims 1 to 3, characterized in that: Two annular sealing grooves (101) are formed on the outer side wall of the guide seat body (100), and a sealing ring (160) is respectively accommodated in the two sealing grooves. Either of the two annular sealing grooves (101) can be used as the annular receiving groove.

5. The magnetorheological damper according to claim 4, characterized in that: The buffer pad receiving portion is configured in the form of an L-shaped embedding groove in cross section, and the upper portion of the buffer pad is correspondingly configured in the form of an inverted L-shaped clip in cross section that is positively locked with the L-shaped embedding groove.

6. The magnetorheological damper according to any one of claims 1 to 3, characterized in that: The buffer pad is constructed to include a cylindrical first part (152) with a uniform outer diameter and a hollow truncated cone-shaped second part (153) with an outer diameter gradually decreasing along the axial direction of the guide seat body and in a direction away from the guide seat body.

7. The magnetorheological damper according to claim 6, characterized in that: The inner diameter of the hollow truncated cone-shaped second part (153) is configured to gradually decrease along the axial direction of the guide seat body and in a direction away from the guide seat, and the axial length of the first part is smaller than the axial length of the second part.

8. The magnetorheological damper according to any one of claims 1 to 3, characterized in that: The piston assembly (4000) includes a piston winding assembly (410), which includes a magnetic core (450), the magnetic core is provided with at least one coil groove (451) for winding a coil, and an upper mounting hole (452) and a lower mounting hole (453) that are connected to each other are provided inside the magnetic core, the upper mounting hole is used to receive the lower end of the piston rod, and the lower mounting hole is used to receive a conductive connecting portion (443) for conductively connecting the wire (214) in the piston rod to the coil, wherein the upper mounting hole (452) and the lower mounting hole (453) are respectively provided with an upper expansion portion (454) and a lower expansion portion (455) with gradually increasing inner diameters at the outward ends.

9. The magnetorheological damper according to claim 8, characterized in that: The piston assembly (4000) further includes a piston housing (400) and two piston pressure plates (420) arranged above and below the piston housing, and a pressure plate retaining spring groove (427) for receiving a retaining spring (440) is arranged on the upper piston pressure plate, and the surface of the pressure plate retaining spring groove that contacts the retaining spring (440) is configured as a conical surface.

10. The magnetorheological damper according to claim 9, characterized in that: The piston pressure plate (420) includes a pressure edge portion (421) and a top portion (422), a plurality of through holes (424) are provided between the pressure edge portion and the top portion, adjacent through holes (424) are separated by a plurality of connecting bridge portions (423), the plurality of connecting bridge portions respectively connect the pressure edge portion and the top portion, and the through holes (424) are fluidically connected to a main flow channel (403) provided in the piston assembly (4000).

11. The magnetorheological damper according to claim 10, characterized in that: The piston pressure plate (420) is provided with at least one bypass hole (425) on the top (422), and at least one of the at least one bypass hole is in fluid communication with a bypass channel (412) provided in the piston winding assembly (410).

12. The magnetorheological damper according to claim 10, characterized in that: A positioning mark (426) for assisting positioning is provided on the piston pressure plate.

13. The magnetorheological damper according to any one of claims 1 to 3, characterized in that: The outer cylinder (230) is constructed as a two-piece structure and comprises an outer cylinder body (229) located at the top and a reinforcing cylinder (231) located at the bottom of the outer cylinder body and having an increased wall thickness relative to the outer cylinder body.

14. The magnetorheological damper according to claim 13, characterized in that: The outer diameter of the outer cylinder body (229) is the same as the outer diameter of the reinforcing cylinder (231), and the lower end of the outer cylinder body is sealed and connected to the upper end of the reinforcing cylinder by welding.

15. The magnetorheological damper according to claim 14, characterized in that: The lower end of the outer cylinder body is provided with a first groove (2301), and the upper end of the reinforcing cylinder (231) is provided with a flange (2311), and the flange can be accommodated in the first groove and welded thereto.

16. The magnetorheological damper according to claim 9, characterized in that: Flanging structures (402) are provided at the upper and lower parts of the piston housing (400), and the flanging structures are configured to receive and fix the pressing edge portion (421) of the piston pressure plate (420).

17. A vehicle comprising the magnetorheological damper according to any one of claims 1 to 16.

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