Double-valve multi-stage electric control shock absorber with energy accumulator

Abstract

The invention relates to a double-valve multi-stage electric control shock absorber with an energy accumulator. The double-valve multi-stage electric control shock absorber comprises a piston part, a damping part and an energy storage part. The damping part comprises a damping valve shell which is internally provided with two cavities which are arranged in parallel to accommodate the first damping valve and the second damping valve respectively, a through hole is formed in the wall of the cavity between the two damping valves to form an oil way for hydraulic oil to flow in the damping valve shell, and the energy storage part is connected with an adjusting hole of the damping valve shell. The piston part comprises a working cylinder, an outer barrel and a base, the outer barrel and the base are connected to form a barrel body arranged outside the working cylinder in a sleeving mode, and a hollow interlayer between the barrel body and the working cylinder is blocked by a second sealing assembly. A first oil passing channel communicated with the first oil passing hole of the first damping valve and a second oil passing channel communicated with the second oil passing hole of the second damping valve are formed in the two sides of the second sealing assembly respectively.

Description

Technical Field

[0001] The present invention relates to the technical field of shock absorbers, and in particular, to a dual-valve multi-stage electronically controlled shock absorber with an accumulator. Background Art

[0002] The damping characteristics of vehicle shock absorbers have a decisive impact on the handling stability and ride comfort of the chassis suspension. For traditional passive shock absorbers, their damping coefficients are fixed and cannot be dynamically adjusted according to driving conditions and the driver's needs, making it difficult to find an ideal balance between pursuit of handling performance and ride comfort. To solve this problem, adjustable shock absorbers emerged. They can select appropriate damping coefficients according to actual needs, thereby achieving more refined adjustment between maneuverability and comfort, and significantly improving the comprehensive performance of the suspension system. This is undoubtedly an important direction for the development of vehicle shock absorption technology.

[0003] In recent years, with the rapid development of electronic control technology, electronically controlled adjustable shock absorbers have received extensive attention in the automotive industry. Major automakers have shown strong interest in suspension systems equipped with electronically controlled shock absorbers. Currently, the mainstream electronically controlled shock absorber products on the market mostly use a single proportional flow valve to achieve continuous adjustment of damping. Although this design can provide a certain degree of damping force adjustment ability, its manufacturing requirements are stringent, the cost is high, and the control difficulty is large. More critically, the compression damping and rebound damping of such shock absorbers cannot be independently controlled, limiting their adaptability and adjustment accuracy under different road conditions. In addition, the oil-gas mixed structural design affects the anti-foaming performance of the shock absorber oil to a certain extent, which not only affects the shock absorption effect but also has a negative impact on the vehicle ride experience. Therefore, although electronically controlled adjustable shock absorbers have made certain progress in technology, they still face many challenges and need further technological innovation and optimization to meet the pursuit of high-performance suspension systems in the future automotive industry.

[0004] CN110886804A discloses an in-built solenoid valve type semi-active damping continuously adjustable shock absorber, including a shock absorber body and a shock absorber control system. The shock absorber body includes a working cylinder, an oil storage cylinder, a shock absorber dust cover, a bottom valve assembly, a piston assembly, and a solenoid valve assembly. The oil storage cylinder semi-surrounds the working cylinder. The upper port of the oil storage cylinder and the working cylinder are sealed and connected with a fixed sealing ring. A piston rod passing through the working cylinder and the shock absorber dust cover is arranged in the middle of the working cylinder top cover. An O-ring is used to connect the working cylinder and the piston rod. The outside of the piston rod and the working cylinder and the oil storage cylinder form a closed structure. Hydraulic oil is provided inside both the working cylinder and the oil storage cylinder. The shock absorber dust cover covers the outside of the working cylinder and is fixedly connected to the piston rod. The piston rod is threadedly connected to the upper suspension ear. The bottom of the oil storage cylinder and the lower suspension ear are fixedly connected with a lower suspension ear fastening nut.

[0005] However, there are certain defects in the shock absorber of this patent. Since the heat generated during the operation of the shock absorber needs to be effectively dissipated; and integrating the solenoid valve into the piston working cylinder may limit the heat dissipation channels, thereby leading to poor heat dissipation. The high-precision requirements and complex integration process of the built-in solenoid valve design may increase the manufacturing cost, and once the solenoid valve fails, the built-in design may require the disassembly of more shock absorber components for repair and replacement, making the repair work complicated and time-consuming. In addition, placing the solenoid valve in the working cylinder poses higher requirements for sealing technology. Any leakage may lead to a decline in shock absorption performance, and at the same time, it is necessary to ensure the waterproof and dustproof performance of the solenoid valve components.

[0006] In addition, on the one hand, there are differences in the understanding of those skilled in the art; on the other hand, when the applicant made this invention, a large number of documents and patents were studied, but due to space limitations, all details and contents were not listed in detail. However, this does not mean that this invention does not possess the features of these prior arts. On the contrary, this invention already possesses all the features of the prior arts, and the applicant reserves the right to add relevant prior arts in the background art. Summary of the Invention

[0007] In view of the deficiencies of the prior art, the present invention provides a dual-valve multi-stage electronically controlled shock absorber with an accumulator to solve at least some of the above technical problems.

[0008] The present invention relates to a dual-valve multi-stage electronically controlled shock absorber with an accumulator, including a piston part, a damping part, and an energy storage part. The damping part includes a damping valve housing with two chambers arranged in parallel inside to accommodate a first damping valve and a second damping valve respectively. A through hole is opened on the chamber wall between the two damping valves to form an oil passage for the hydraulic oil to flow through in the damping valve housing. The energy storage part is connected to the adjustment hole of the damping valve housing. The piston part includes a working cylinder and a cylinder body sleeved outside the working cylinder formed by connecting an outer cylinder and a base. The hollow interlayer between the cylinder body and the working cylinder is blocked by a second sealing component, so that a first oil passage communicating with the first oil hole of the first damping valve and a second oil passage communicating with the second oil hole of the second damping valve are respectively formed on both sides of the second sealing component.

[0009] The shock absorber proposed by the present invention adopts a parallel configuration of double damping valves, which are connected to the compression chamber and the stretching chamber in the working cylinder through independent liquid flow channels. This design effectively reduces the space required for the valve body compared with the traditional separated double damping valve layout. The outer cylinder of the shock absorber is connected to the base to form a cylinder structure sleeved outside the working cylinder, thereby creating an annular cavity for the hydraulic oil to flow between the working cylinder and the cylinder. The annular cavity is divided into two independent parts by a seal. One part forms a liquid flow channel connecting the compression chamber to the first damping valve, and the other part constitutes a liquid flow channel connecting the stretching chamber to the second damping valve. Through such an arrangement, the shock absorber can realize the differential pressure release of the hydraulic oil through its respective damping valves during the compression stage and the stretching stage. The present invention realizes a wide range of independent damping regulation for the compression and stretching processes by assigning different damping parameters to the two damping valves. In addition, an accumulator is attached outside the damping valve to optimize the oil-gas separation and reduce the phenomenon of hydraulic oil cavitation caused by gas precipitation, thereby improving the performance of the shock absorber.

[0010] According to a preferred embodiment, a piston rod and a piston head fixedly connected to the bottom end of the piston rod are arranged inside the working cylinder. The piston head divides the working cylinder into a compression chamber and a stretching chamber. Among them, the first oil passage is connected to the compression chamber, and the second oil passage is connected to the stretching chamber through a communication hole provided on the working cylinder. Through such a design, the damping valve realizes the independent control of the hydraulic oil flow in the two chambers, thereby optimizing the performance of the working cylinder during the compression and stretching processes and improving the flexibility and efficiency of the shock absorber.

[0011] According to a preferred embodiment, the energy storage part includes an accumulator body connected to the base through a third sealing component. The accumulator body is provided with an oil injection port aligned with the adjustment hole, and a movable accumulator piston is installed inside it. The accumulator piston divides the interior of the accumulator body into two chambers for adjusting the pressure of the shock absorber. Among them, the chamber close to the oil injection port is the oil chamber, and the other chamber is the gas chamber. The accumulator piston in the accumulator body divides the internal space into an oil chamber and a gas chamber. By aligning the oil injection port with the adjustment hole, the hydraulic oil volume in the oil chamber can be effectively controlled with the participation of the gas pressure in the gas chamber, thereby optimizing the performance of the shock absorber and improving its ability to adapt to different working conditions.

[0012] According to a preferred embodiment, both the first damping valve and the second damping valve are provided with a basic valve system for providing a fixed damping force and an adjustable valve system for providing a variable damping force. Among them, the basic valve system includes a basic valve seat, a connecting member, and a check valve group, and the adjustable valve system includes an overflow valve seat, an overflow valve core, and an overflow spring. The basic valve system provides a fixed damping force through the basic valve seat, the connecting member, and the check valve group, ensuring the stability and reliability of the damping system under standard operating conditions. At the same time, the adjustable valve system can adjust the damping force according to different working conditions by using the overflow valve seat, the overflow valve core, and the overflow spring, providing variable damping and enhancing the adaptability of the system when facing different loads or dynamic response requirements.

[0013] According to a preferred embodiment, the basic valve seat for fixing the basic valve system in the damping valve housing can divide the hydraulic oil chamber in the damping valve housing into two cavities. Among them, the cavity close to the working cylinder is the first cavity, and the cavity far from the working cylinder is the second cavity. The basic valve seat is provided with a through hole that can be controllably opened and closed by the check valve group to connect the hydraulic oil in the first cavity and the second cavity. This technical solution divides two independent hydraulic oil cavities in the damping valve housing through the basic valve seat, realizing precise control of the fluid flow inside the damping valve. The through hole on the basic valve seat ensures the connection of the hydraulic oil between the first cavity and the second cavity, enabling the damping valve to adjust the flow of hydraulic oil according to the requirements of the working cylinder, thereby effectively controlling the magnitude and response speed of the damping force.

[0014] According to a preferred embodiment, the check valve group includes a first stiffness check valve disposed in the first cavity and a second stiffness check valve disposed in the second cavity. The first stiffness is less than the second stiffness. The first stiffness check valve includes a first spring and a first valve plate. The first spring can drive the first valve plate away from the basic valve seat when the hydraulic oil flows from the second cavity to the first cavity, thereby opening the through hole blocked by the first valve plate on the basic valve seat. The second stiffness check valve includes a second spring, a second valve plate, and a gasket disposed between the two. The second spring can drive the second valve plate away from the basic valve seat to open the through hole when the hydraulic oil flows from the first cavity to the second cavity, and generate a damping force on the hydraulic oil during this process. By respectively disposing the first stiffness check valve and the second stiffness check valve in the two cavities of the damping valve, precise control of the flow direction and damping force of the hydraulic oil is achieved. The first stiffness check valve allows the hydraulic oil to flow from the second cavity to the first cavity, while the second stiffness check valve controls the flow of the hydraulic oil from the first cavity to the second cavity. Through the combination of the spring and the valve plate, when allowing the hydraulic oil to flow from the second cavity to the first cavity, it can provide a damping force to the hydraulic oil flowing from the first cavity to the second cavity.

[0015] According to a preferred embodiment, the connecting member includes a first connecting member and a second connecting member. Among them, the first connecting member is disposed in the first cavity and the second cavity in the form of passing through the base valve seat, and the second connecting member is fixedly connected to the first connecting member and disposed in the second cavity. Such a setting enhances the structural stability and sealing performance of the internal components of the damping valve. In addition, the through-type arrangement of the first connecting member makes the connection between the first cavity and the second cavity more stable. At the same time, the fixed connection of the second connecting member ensures the close fit between components, reduces the risk of hydraulic oil leakage, and improves the overall reliability and durability of the shock absorber.

[0016] According to a preferred embodiment, the overflow valve seat and the overflow valve core are coaxially arranged, and both are connected to the end of the second connecting member. The overflow spring located between the overflow valve seat and the overflow valve core can impose a constraint on the movement range of the overflow valve core. In this technical solution, the coaxial arrangement of the overflow valve seat and the overflow valve core and their connection design to the end of the second connecting member provide a compact and efficient overflow control mechanism. The overflow spring is located between the overflow valve seat and the overflow valve core. This configuration not only enhances the structural compactness but also ensures that the overflow valve core operates within a predetermined movement range, thereby precisely controlling the flow of hydraulic oil above the pressure threshold.

[0017] According to a preferred embodiment, the adjustable valve system includes a solenoid valve seat, a solenoid valve body, and a solenoid coil. The solenoid valve seat is coaxially arranged with the overflow valve seat. One end of the solenoid valve seat expands along the axial and radial directions and is equipped with a fourth sealing assembly that closes the gap between this end and the damping valve housing. The solenoid valve body and the solenoid coil are installed on the side of the solenoid valve seat away from the base valve system. This technical solution realizes the precise adjustment and control of the performance of the damping valve by introducing the adjustable valve system. The coaxial arrangement of the solenoid valve seat and the overflow valve seat and the axial and radial expansion design of its end enhance the sealing performance. The configuration of the fourth sealing assembly further closes the gap between the solenoid valve seat and the damping valve housing, preventing hydraulic oil leakage. The installation positions of the solenoid valve body and the solenoid coil, isolated by the fourth sealing assembly, ensure the independent operation of the solenoid valve, enabling it to adjust the damping force according to system requirements, thereby optimizing the performance and response speed of the shock absorber.

[0018] According to a preferred embodiment, the solenoid coil is arranged around the outside of the solenoid valve body. After being energized, it can control the opening or closing of the solenoid valve body, thereby realizing the adjustability of controlling the damping force by adjusting the hydraulic oil flow path. By arranging the solenoid coil around the outside of the solenoid valve body, it can effectively control the opening or closing state of the solenoid valve body after being energized. Such a configuration allows for precise adjustment of the hydraulic oil flow path, and the damping force can be adjusted according to different working conditions and performance requirements, thereby significantly improving the adaptability and flexibility of the shock absorber. Brief Description of the Drawings

[0019] Figure 1 It is a schematic diagram of the overall appearance of a shock absorber according to a preferred embodiment of the present invention;

[0020] Figure 2 It is a schematic sectional view of the structure of a shock absorber according to a preferred embodiment of the present invention;

[0021] Figure 3 It is a schematic diagram of the structure of a damping part according to a preferred embodiment of the present invention;

[0022] Figure 4 is Figure 1 A schematic sectional view of the structure of the base and the accumulator of the A-A section shown in;

[0023] Figure 5 It is a schematic diagram of the structure of a damping valve according to a preferred embodiment of the present invention;

[0024] Figure 6 It is a schematic diagram of the flow of the oil in the damping part under the compression stroke according to a preferred embodiment of the present invention;

[0025] Figure 7 It is a schematic diagram of the flow of the oil in the damping part under the tensile stroke according to a preferred embodiment of the present invention;

[0026] Figure 8 It is a schematic diagram of the structure of the first alternative shock absorber of the present invention;

[0027] Figure 9 It is a schematic diagram of the structure of the second alternative shock absorber of the present invention;

[0028] Figure 10 It is a schematic diagram of the structure of the third alternative shock absorber of the present invention;

[0029] Figure 11 It is a schematic diagram of the structure of the fourth alternative shock absorber of the present invention.

[0030] List of reference numerals

[0031] 100: Piston part; 101: Piston rod; 102: Piston head; 103: Oil seal guide assembly; 104: Working cylinder; 105: Outer cylinder; 106: Base; 106a: First annular seal seat; 106b: Second annular seal seat; 107: Mounting lug; 108: Compression chamber; 109: First oil passage; 110: Tension chamber; 111: Communication hole; 112: Second oil passage; 113: First seal assembly; 114: Second seal assembly; 115: Third seal assembly; 200: Damping part; 200a: Damping valve housing; 201: First damping valve; 202: Second damping valve; 203: Basic valve system; 204: Adjustable valve system; 205: First oil hole; 206: Second oil hole; 207: Through hole; 208: Adjusting hole; 209: Basic valve seat; 209a: First passage; 209b: Second passage; 210: First connecting piece; 211: Second connecting piece; 212: First spring; 213: First valve plate; 214: Second spring; 215: Gasket; 216: Second valve plate; 217: Third oil hole; 218: Overflow valve seat; 218a: Overflow hole; 218b: Overflow port; 219: Overflow valve core; 219a: Valve core through hole; 220: Overflow spring; 221: Solenoid valve seat; 221a: Valve seat opening; 221b: Valve seat through hole; 222: Solenoid valve body; 222a: Solenoid valve opening; 222b: Solenoid valve through hole; 223: Electromagnetic coil; 224: Fourth seal assembly; 300: Energy storage part; 301: Oil filling port; 302: Accumulator body; 303: Accumulator piston; 304: Gas chamber; 305: Oil chamber. Detailed implementation mode

[0032] The following is a detailed description with reference to the accompanying drawings.

[0033] Embodiment 1

[0034] Combined with Figure 1 and Figure 2 As shown, the present invention provides a double-valve multi-stage electronically controlled shock absorber with an accumulator, which according to the present invention includes a piston part 100, a damping part 200 and an energy storage part 300. In the upper region of Figure 1 is shown a piston part 100 having a cylindrical structure and forming a hydraulic oil flow path inside, which is the part of the shock absorber that performs compression or stretching movement along the axial direction of the outer cylinder 105 by means of the piston rod 101. The piston part 100 is used to realize the dynamic response to the external load of the shock absorber applied on the piston rod 101. Figure 1 In the lower left region of Figure 1The lower right region shows an energy storage portion 300 that is arranged side by side with the piston portion 100 and is connected to the same side wall of the damping portion 200. By forming a hydraulic oil flow path with the damping portion 200, the energy storage portion 300 can temporarily store or release a part of the hydraulic oil from the piston portion 100 in the damping portion 200 during the compression or stretching process of the piston rod 101, thereby optimizing the working performance of the shock absorber.

[0035] Figure 2 Shows a longitudinal sectional view of a shock absorber according to an embodiment of the present invention. The sectional plane is parallel to the axis of the piston portion 100 and simultaneously cuts through two oil holes at the interface between the piston portion 100 and the damping portion 200. Figure 2 The piston portion 100 is shown at the middle position, which includes a hierarchical structure for the flow of hydraulic oil constructed by a working cylinder 104 and an outer cylinder 105 with different diameters sleeved with each other from the inside to the outside and arranged coaxially. Among them, the outer cylinder 105 is the outermost structure of the piston portion 100, and it partially wraps the working cylinder 104 in a non-contact form to build an annular hollow sandwich for the flow of hydraulic oil between its inner wall and the outer wall of the working cylinder 104. At the bottom of the working cylinder 104 and the outer cylinder 105, there is a base 106 which is a special-shaped integral housing structure of the damping portion 200, and it receives the working cylinder 104 and the outer cylinder 105 in a sleeved manner through an opening on the top surface. The outer cylinder 105 is preferably independently held on the first annular seal seat 106a of the base 106 by means of a first seal assembly 113, and the working cylinder 104 is held at the second annular seal seat 106b of the base 106 which is closer to the inside relative to the first annular seal seat 106a. Among them, a second seal assembly 114 is provided at the second annular seal seat 106b for sealing and fixing the working cylinder 104.

[0036] Preferably, as Figure 2 shown, the piston rod 101 is movably arranged coaxially inside the working cylinder 104. The piston head 102 disposed at the end of the piston rod 101 divides the internal space of the working cylinder 104 into a stretching chamber 110 on the side of the piston rod 101 and a compression chamber 108 on the far side of the piston rod 101. The second seal assembly 114 provided at the second annular seal seat 106b divides the annular sandwich space between the inner walls of the outer cylinder 105 and the base 106 and the outer wall of the working cylinder 104 into a first oil passage 109 on the side closer to the compression chamber 108 and a second oil passage 112 on the side closer to the stretching chamber 110. With this design, the hydraulic oil can be interconnected between the compression chamber 108 and the first oil passage 109. Similarly, the stretching chamber 110 is connected to the second oil passage 112 through a communication hole 111 opened on the outer wall of the working cylinder 104, thereby promoting the effective flow and exchange of hydraulic oil between the compression chamber 108 and the stretching chamber 110.

[0037] Figure 2The arrows marked in the piston part 100 illustrate the flow of hydraulic oil when the shock absorber of the present invention is in the compression stroke stage. Specifically, in the compression stroke, that is, when the piston rod 101 drives the piston head 102 to move downward, the volume of the compression chamber 108 becomes smaller, and the hydraulic oil starts from the compression chamber 108 and flows into the first oil passage 109 located at the bottom thereof, and then enters the first oil passage hole 205 connected to the end of the first oil passage 109 arranged at the lower side of the damping part 200. Figure 2 The right area is shown in the internal space of the damping part 200 whose housing is formed by the base 106. The hydraulic oil entering the damping part 200 passes through the throttling of the damping valve (hereinafter referred to as Figure 6 Detailed description) The hydraulic oil enters the second oil passage 112 connected thereto through the second oil hole 206 arranged on the upper side of the damping part 200. This part of the hydraulic oil flows upward along the second oil passage 112 and is finally injected into the stretching chamber 110 after passing through the connecting hole 111 on the outer wall of the working cylinder 104.

[0038] Preferably, Figure 4 It is for Figure 1 The AA cross-sectional view of FIG. 2 shows the damping part 200 and the energy storage part 300 in order to show the structural connection relationship between the two. Figure 4 As shown, a damping valve housing 200a having two independent hydraulic oil chambers is integrated inside the base 106, wherein the side wall of the hydraulic oil chamber located at the bottom is connected to the first oil hole 205, and the side wall of the hydraulic oil chamber located at the top is connected to the second oil hole 206. Figure 3 A first damping valve 201 connected to the first oil hole 205 and a second damping valve 202 connected to the second oil hole 206 are respectively installed in different hydraulic oil chambers of the damping valve housing 200a. The two chambers are separated by a chamber wall to ensure that the two damping valves remain independent in structure and avoid contact with each other, thereby achieving independent damping adjustment functions. By wrapping the first damping valve 201 and the second damping valve 202 inside the damping valve housing 200a, the overall structure of the shock absorber can be made tighter. In addition, since the damping valve housing 200a is located outside the working cylinder 104, when adjusting the damping valve, it is more convenient to replace the valve plate than in a traditional shock absorber in which the damping valve is set on the piston. Preferably, as Figure 2 , Figure 3As shown, a through hole 207 is provided on the chamber wall of the damping valve housing 200a that serves as a partition to enable the flow of hydraulic oil between two independent hydraulic oil chambers. At one end of the base 106 close to the outer cylinder 105, a first oil passage hole 205 and a second oil passage hole 206 are respectively opened and connected to the ports of the first oil passage 109 and the second oil passage 112. This design allows when the volume of the compression chamber 108 of the working cylinder 104 decreases, the hydraulic oil therein can flow in through the first oil passage 109, enter the hydraulic oil chamber in the damping valve housing 200a where the first damping valve 201 is installed through the first oil passage hole 205. Under the action of the first damping valve 201, after the hydraulic oil undergoes damping treatment, it flows through the through hole 207 to the hydraulic oil chamber where the second damping valve 202 is located, and flows into the second oil passage 112 through the second oil passage hole 206, and finally reaches the stretching chamber 110 of the working cylinder 104 through the communication hole 111. Conversely, when the volume of the stretching chamber 110 of the working cylinder 104 decreases, the hydraulic oil therein will enter the second oil passage 112 through the communication hole 111, and then flow into the hydraulic oil chamber in the damping valve housing 200a where the second damping valve 202 is installed through the second oil passage hole 206. Under the damping action of the second damping valve 202, the hydraulic oil undergoes damping treatment, flows through the through hole 207 to the hydraulic oil chamber where the first damping valve 201 is located, and returns to the first oil passage 109 through the first oil passage hole 205, and finally flows back into the compression chamber 108 of the working cylinder 104. Through this design of the hydraulic circuit, the flow of hydraulic oil in a predetermined direction and damping adjustment during the compression and stretching processes of the working cylinder 104 are achieved.

[0039] Preferably, Figure 5 shows a sectional view of the first damping valve 201 in the embodiment of the present invention as an example. Figure 3 Figure 5 The first damping valve 201 shown adopts a composite valve structure of a basic valve system 203 and an adjustable valve system 204 connected to each other. The basic valve system 203 is mainly responsible for providing basic flow control and pressure balance functions to ensure the stable operation of the system under normal working conditions. The adjustable valve system 204 has the ability to finely adjust the flow rate and pressure according to preset parameters to adapt to the dynamically changing working condition requirements and achieve more precise and flexible system control. Specifically, the basic valve system 203 is a combined component composed of a basic valve seat 209, a connecting member, and a check valve group. Among them, the circular basic valve seat 209 can fix the basic valve system 203 of the first damping valve 201 at a predetermined position in the damping valve housing 200a by means of its outer diameter corresponding to the internal dimensions of the hydraulic oil chamber. The hollow part of the basic valve seat 209 is blocked by the connecting member, thereby dividing the hydraulic oil chamber where it is located into two small cavities. For the convenience of explanation, as Figure 6As shown in the figure, the cavity close to the first oil passage hole 205 in the two cavities is called the first cavity, and the other cavity is called the second cavity. A mutual flow path of hydraulic oil is established outside the damping valve between the first cavity and the second cavity by means of a first passage 209a and a second passage 209b penetrating through the base valve seat 209.

[0040] Preferably, as Figure 5 , Figure 6 shown in the figure, the connecting members in the base valve system 203 include a first connecting member 210 and a second connecting member 211. Among them, the first connecting member 210 is an element for blocking the hollow part of the base valve seat 209 and is located in both the first cavity and the second cavity in the form of penetrating through the base valve seat 209. The second connecting member 211 is located in the second cavity, and its stability of the base valve system 203 is ensured by sleeving on the outer surface of the first connecting member 210.

[0041] Preferably, as Figure 5 shown in the figure, the check valve group in the base valve system 203 includes a first stiffness check valve and a second stiffness check valve, and the first stiffness is less than the second stiffness. The first stiffness check valve is arranged in the first cavity and is used to ensure the smooth passage of the hydraulic oil outside the damping valve. In the hydraulic oil chamber where the first damping valve 201 is located, the first stiffness check valve can allow the hydraulic oil in the second cavity to enter the first cavity through the second passage 209b on the base valve seat 209. The first stiffness check valve includes a first spring 212 and a first valve plate 213. Among them, the first valve plate 213 can block the second passage 209b on the base valve seat 209, and the first spring 212 can press the first valve plate 213 on the base valve seat 209 with a relatively small pre-tightening force. The second stiffness check valve is arranged in the second cavity and is arranged opposite to the first stiffness check valve, and is used to impede the flow of hydraulic oil to generate a damping force. In the hydraulic oil chamber where the first damping valve 201 is located, the second stiffness check valve can prevent the hydraulic oil in the first cavity from entering the second cavity through the first passage 209a on the base valve seat 209. The second stiffness check valve includes a second spring 214, a second valve plate 216 and a gasket 215. The gasket 215 is arranged between the second valve plate 216 and the second spring 214 and is used to ensure that the second spring 214 can press the second valve plate 216 on the base valve seat 209 with a relatively large pre-tightening force to realize blocking the first passage 209a on the base valve seat 209.

[0042] Preferably, as Figure 5As shown, the adjustable valve system 204 of the damping valve includes an overflow valve seat 218, an overflow valve core 219, and an overflow spring 220, all of which are arranged in the second cavity. The overflow valve seat 218 and the overflow valve core 219 are movably connected. The two sleeved with each other are coaxial with the second connecting member 211 and maintain the connection with its end. The overflow spring 220 located between the overflow valve seat 218 and the overflow valve core 219 places a limit on the movement range of the overflow valve core 219 within the overflow valve seat 218, so that the overflow valve core 219 can be constrained to move left and right under the shape limitation of the overflow valve seat 218 and the elastic force limitation of the overflow spring 220. An overflow hole 218a corresponding to the end face of the overflow valve core 219 and the right end face of the second connecting member 211 is axially provided on the left end face of the overflow valve seat 218. The overflow hole 218a is configured to allow hydraulic oil to pass through, and it becomes the gateway for the oil flow path connecting the basic valve system 203 and the adjustable valve system 204. The circumferential side wall of the overflow valve seat 218 is configured with an overflow port 218b that can communicate its internal and external spaces. The overflow port 218b is configured to be controllably blocked by the overflow valve core 219. Specifically, the overflow port 218b can be gradually opened during the process of the overflow valve core 219 moving to the right, thereby communicating the internal and external spaces of the overflow valve seat 218; the overflow port 218b can also be completely blocked when the overflow valve core 219 moves to the left to the end point, thereby isolating the internal and external spaces of the overflow valve seat 218. A valve core through hole 219a is axially arranged on the left end face of the overflow valve core 219 corresponding to the overflow hole 218a of the overflow valve seat 218. Such a configuration enables the hydraulic oil entering the overflow valve seat 218 through the overflow hole 218a to further enter and fill the internal space surrounded by the overflow valve core 219.

[0043] Preferably, as Figure 5 shown, the adjustable valve system 204 further includes a solenoid valve seat 221, a solenoid valve body 222, and a solenoid coil 223. The solenoid valve seat 221 is coaxially arranged with the overflow valve seat 218. One end of it far from the overflow valve seat 218 expands radially along the axis, so as to be in close contact with the inner wall of the hydraulic oil chamber in the damping valve housing 200a. The solenoid valve seat 221 is equipped with a fourth sealing assembly 224 to seal the gap between it and the damping valve housing 200a and prevent hydraulic oil from leaking to the other end of the solenoid valve seat 221.

[0044] Preferably, as Figure 5As shown, on the left end face of the solenoid valve seat 221 close to the overflow valve seat 218, a valve seat opening 221a is axially formed along its axis, which is in communication with the internal space surrounded by the overflow valve core 219. The valve seat opening 221a is configured to have a diameter slightly smaller than the diameter of the spring coils of the overflow spring 220, so that the end of the overflow spring 220 can be stably connected to the left end face of the solenoid valve seat 221 around the valve seat opening 221a. A plurality of valve seat through holes 221b are provided on the radial outer periphery of the solenoid valve seat 221. These valve seat through holes 221b allow hydraulic oil to pass through when the solenoid valve body 222 is opened, thereby forming a fluid passage connecting the internal and external spaces of the solenoid valve seat 221. The left part of the solenoid valve body 222 close to the valve seat opening 221a bulges radially, so that the left part with a cylindrical structure can closely fit the inner wall of the solenoid valve seat 221. The solenoid valve opening 222a formed at the end face of the left part close to the valve seat opening 221a can be controllably opened and closed under the action of the solenoid valve to connect or block the hydraulic oil flowing in through the valve seat opening 221a.

[0045] Preferably, as Figure 5 shown, the radial dimension of the middle part of the solenoid valve body 222 adjacent to the left part and also having a cylindrical structure is smaller than that of the left part. The middle part and the left part are coaxially arranged and fluidly connected, and a plurality of solenoid valve through holes 222b are provided on its circumferential side wall. When the solenoid valve opening 222a at the end face of the left part of the solenoid valve body 222 is opened, the hydraulic oil from the internal space surrounded by the overflow valve core 219 can flow through the valve seat opening 221a and the solenoid valve opening 222a in sequence, flow out from the solenoid valve through holes 222b and enter the space between the solenoid valve body 222 and the solenoid valve seat 221, and finally flow out of the adjustable valve system 204 from the valve seat through holes 221b.

[0046] Preferably, as Figure 5As shown, a third oil passage hole 217 is provided along the axis of the first connecting member 210 and the second connecting member 211 in the basic valve system 203, which constructs a hydraulic oil flow passage between the first cavity and the second cavity. When the hydraulic oil enters the damping valve through the third oil passage hole 217, if the solenoid valve body 222 is in the open state, the hydraulic oil will push the overflow valve core 219 in the second cavity to move to the right, compress the overflow spring 220, open the overflow hole 218a and enter the space surrounded by the overflow valve seat 218 through this hole, and flow through the overflow port 218b provided on the circumferential side wall of the overflow valve seat 218 to reach the outside of the damping valve. At this time, the adjustable valve system 204 exhibits a small damping; on the contrary, if the solenoid valve body 222 is in the closed state, the hydraulic oil cannot effectively push the overflow valve core 219, resulting in the inability to open the overflow hole 218a, and the hydraulic oil cannot be discharged to the outside of the damping valve through the regulating valve device. At this time, the adjustable valve system 204 exhibits a large damping. The solenoid valve body 222 and the electromagnetic coil 223 are installed on one side of the solenoid valve seat 221 isolated by the fourth sealing assembly 224. The electromagnetic coil 223 is arranged outside the solenoid valve body 222 in a surrounding manner, and after being energized, it can control the opening or closing of the solenoid valve body 222, thereby realizing the adjustability of controlling the damping force by adjusting the hydraulic oil flow path. Thus, the minimum and maximum two-stage damping forces of the shock absorber can be achieved by simply energizing and stopping energizing the solenoid valve body 222 respectively, abandoning the complex electronic control while making the adjustment of the damping force more accurate.

[0047] Preferably, Figure 6 shows the hydraulic oil flow directions in different hydraulic oil chambers of the damping valve housing 200a when the shock absorber is in the compression stroke. In Figure 6 , the hydraulic oil flowing into the hydraulic oil chamber where the first damping valve 201 is located will first be blocked by the basic valve seat 209 and stay in the first cavity, and the hydraulic oil in the first cavity will generate different flow paths as Figure 6 shown according to the opening and closing conditions of the solenoid valve body 222 in the adjustable valve system 204. For the convenience of overview, only the base 106 is sectioned in the figure, and the first channel 209a and the second channel 209b of the solenoid valve basic valve system 203 in the figure are marked in dotted lines. Specifically, in combination with Figure 5 and Figure 6When the solenoid valve body 222 is opened under the control of the electromagnetic coil 223, the hydraulic oil in the first cavity has three flow paths. A part of the hydraulic oil presses the second valve plate 216 in the basic valve system 203, enabling the second valve plate 216 to move to the right to open the first passage 209a on the basic valve seat 209. Then, this part of the hydraulic oil can pass through the basic valve seat 209 and enter the second cavity. The second part of the hydraulic oil enters the third oil passing hole 217. By pressing the overflow valve core 219 in the adjustable valve system 204, the overflow hole 218a on the overflow valve seat 218 can be opened. Then, this part of the hydraulic oil can pass through the overflow hole 218a on the overflow valve seat 218 and enter the second cavity. The third part of the hydraulic oil is the part of the second part of the hydraulic oil with another flow distribution at the position of the overflow valve core 219. This part of the hydraulic oil first enters and fills the internal space surrounded by the overflow valve core 219 through the valve core through hole 219a axially arranged on the left end face of the overflow valve core 219. Secondly, this part of the hydraulic oil flows through the valve seat opening 221a axially opened on the left end face of the solenoid valve seat 22 and communicating with the internal space surrounded by the overflow valve core 219. Then, this part of the hydraulic oil flows out through a plurality of solenoid valve through holes 222b opened on the circumferential side wall of the middle part of the solenoid valve body 222 and enters the space between the solenoid valve body 222 and the solenoid valve seat 221. Finally, the third part of the hydraulic oil can flow out of the adjustable valve system 204 through a plurality of valve seat through holes 221b arranged on the radial outer periphery of the solenoid valve seat 221 and converge with the first part of the hydraulic oil and the second part of the hydraulic oil in the second cavity. The converged hydraulic oil can flow through the through hole 207 and into the second cavity of the hydraulic oil chamber where the second damping valve 202 is located. This part of the hydraulic oil presses the first valve plate 213 in the basic valve system 203, enabling the first valve plate 213 to move to the left to open the second passage 209b on the basic valve seat 209. Then, this part of the hydraulic oil can pass through the basic valve seat 209 and enter the first cavity of the hydraulic oil chamber where the second damping valve 202 is located.

[0048] When the solenoid valve body 222 is closed under the control of the electromagnetic coil 223, since the hydraulic oil cannot pass through the hydraulic oil path provided by the adjustable valve system 204, all the hydraulic oil in the first cavity will pass through the first passage 209a of the basic valve seat 209 and enter the second cavity. Due to the downward pressure of the piston rod 101, its volume in the working cylinder 104 increases, and correspondingly, the volume of the hydraulic oil that can be accommodated in the working cylinder 104 decreases. A part of the hydraulic oil entering the second cavity enters the hydraulic oil cavity where the second damping valve 202 is located through the through hole 207, and finally is injected into the stretching chamber 110 after passing through the second oil passing hole 206 and the second oil passing channel 112. Another part enters the accumulator body 302 through the adjusting hole 208. The oil compresses the accumulator piston 303, causing it to move upward to compress the nitrogen. By controlling the opening and closing of the solenoid valve body 222, the throttling effect of the adjustable valve system 204 on the hydraulic oil is changed, so as to realize the adjustment and control of the compression damping force of the shock absorber.

[0049] Preferably, Figure 7 The figure shows the flow direction of the hydraulic oil in different hydraulic oil chambers of the damping valve housing 200a when the shock absorber is in the stretching stroke. The difference in the hydraulic oil flow lies only in the sequence of passing through the first damping valve 201 and the second damping valve 202, and the flow mode will not be elaborated here.

[0050] Preferably, as Figure 1 、 Figure 2 shown, one end of the piston rod 101 away from the piston head 102 penetrates through the top end of the working cylinder 104, and an oil seal guiding assembly 103 is provided at this top end. This oil seal guiding assembly 103 is concentric with the axis of the piston rod 101. It not only ensures the linear movement track of the piston rod 101, but also plays a sealing role, eliminating the gap between the piston rod 101 and the working cylinder 104 and preventing the hydraulic oil in the working cylinder 104 from leaking along the piston rod 101. In addition, the top end of the outer cylinder 105 is also hermetically connected to the oil seal guiding assembly 103, so that its top end is kept substantially horizontal with the top end of the working cylinder 104.

[0051] Preferably, as Figure 1 、 Figure 2As shown, a communication hole 111 is provided on the outer wall of the working cylinder 104 near one end of the oil seal guiding assembly 103. This communication hole 111 realizes the communication between the inner cavity of the working cylinder 104 and the peripheral annular sandwich space, enabling the internal hydraulic oil to freely flow to the annular sandwich and vice versa. A ring-shaped second sealing assembly 114 is assembled on the inner side walls of the base 106 and the outer cylinder 105. This sealing assembly 114 effectively divides the annular sandwich space into two independent parts, namely: the part near the compression chamber 108 is defined as the first oil passage 109, and the part near the stretching chamber 110 is defined as the second oil passage 112. With this design, the hydraulic oil can be interconnected between the compression chamber 108 and the first oil passage 109. Similarly, the stretching chamber 110 is connected to the second oil passage 112 through the communication hole 111, thus promoting the effective flow and exchange of hydraulic oil.

[0052] Preferably, as Figure 2 、 Figure 3 shown, an installation lug 107 is fixed to the bottom of the base 106 by welding. This lug serves as the connection node between the shock absorber and the vehicle chassis, used to transmit and absorb various forces and vibrations borne by the shock absorber. The installation lug 107 is usually made of high-strength metal material and is designed as a sturdy circular ring structure to ensure its sufficient load-bearing capacity and durability to cope with various dynamic stresses and loads. Inside the circular ring structure, a rubber bushing can be embedded to enhance its shock absorption performance.

[0053] Preferably, as Figure 4 shown, the damping valve housing 200a is provided with an adjustment hole 208 at the end away from the working cylinder 104 for adjusting the flow of hydraulic oil. This adjustment hole 208 can be located at the end of the hydraulic oil chamber where the first damping valve 201 is located ( Figure 4 shown in), or at the end of the hydraulic oil chamber where the second damping valve 202 is located. The adjustment hole 208 is designed to communicate with the energy storage part 300, enabling the hydraulic oil in the damping valve housing 200a to flow into the energy storage part 300 and allowing the energy storage part 300 to participate in the flow and pressure regulation of the hydraulic oil. With such a configuration, the dynamic response ability of the shock absorber can be enhanced, ensuring more effective and flexible hydraulic oil pressure management.

[0054] Preferably, as Figure 4As shown, the energy storage unit 300 includes an accumulator body 302, on which there is an oil filling port 301 aligned with the adjustment hole 208, so that hydraulic oil flows into the accumulator body 302 from the damper valve housing 200a successively through the adjustment hole 208 and the oil filling port 301. The accumulator body 302 and the base 106 are tightly connected through a third sealing assembly 115 to prevent hydraulic oil from leaking at the joint surface between the two. Inside the accumulator body 302, there is a movable accumulator piston 303, which divides the interior of the body into two chambers: the oil chamber 305 near the oil filling port 301 for receiving hydraulic oil; and the gas chamber 304 far from the oil filling port 301, filled with nitrogen. During the compression stroke of the shock absorber, the piston rod 101 pushes the piston head 102 to move downward in the working cylinder 104, resulting in a decrease in the volume of the compression chamber 108, an increase in the pressure of the hydraulic oil, and the hydraulic oil flowing through the damper part 200 into the tension chamber 110. Since the piston rod 101 occupies space in the tension chamber 110, the increased volume of the tension chamber 110 is less than the decreased volume of the compression chamber 108. Therefore, the excess hydraulic oil pushes the accumulator piston 303 and enters the oil chamber 305 of the accumulator body 302. On the contrary, during the extension stroke of the shock absorber, the piston rod 101 drives the piston head 102 to move upward in the working cylinder 104, the volume of the tension chamber 110 decreases, the pressure of the hydraulic oil increases, and the hydraulic oil flows through the damper part 200 into the compression chamber 108. As the piston rod 101 withdraws from the tension chamber 110, the decreased volume of the tension chamber 110 is less than the increased volume of the compression chamber 108, resulting in a negative pressure in the compression chamber 108. At this time, the nitrogen pressure in the gas chamber 304 pushes the accumulator piston 303 to supplement the hydraulic oil in the oil chamber 305 to the compression chamber 108 to balance the pressure of the shock absorber.

[0055] Embodiment 2

[0056] This embodiment is a further improvement of Embodiment 1, and the repeated content will not be elaborated.

[0057] As Figure 8As shown, in this embodiment, the settings of the components of the shock absorber are optimized. Specifically, in the piston part 100, the working cylinder 104 and the base 106 are cancelled, and the piston rod 101 and the piston head 102 thereon are placed into the inner cavity of the outer cylinder 105. Due to the cancellation of the working cylinder 104 and the base 106, the hollow sandwich layer in the structure jointly formed by the outer cylinder 105 and these two also no longer exists. Therefore, the first oil passage 109 and the second oil passage 112 in this embodiment are also cancelled. In addition, the first oil hole 205 and the second oil hole 206 opened on the damper valve housing 200a will directly communicate with the compression chamber 108 and the tension chamber 110 in the outer cylinder 105. Thus, the damper valve housing 200a is also configured into two independent parts, which are respectively located at the positions corresponding to the first oil hole 205 and the second oil hole 206, so as to respectively accommodate the first damper valve 201 and the second damper valve 202. Just because of the separated setting of the damper valve housing 200a, the through holes on the chamber wall of the original damper valve housing 200a are replaced by the through channels connecting the two damper valves, and the energy storage part 300 can be connected to this through channel to realize the adjustment function of the hydraulic oil.

[0058] In this embodiment, the flow direction and principle of the hydraulic oil in the compression stroke and the tension stroke of the shock absorber are the same as those in the previous embodiment, and will not be elaborated here.

[0059] Embodiment 3

[0060] This embodiment is a further improvement of the previous embodiment, and the repeated content will not be elaborated here.

[0061] As Figure 9 shown, in this embodiment, the installation position of the accumulator body 302 can be set inside the outer cylinder 105, and the specific position is adjacent to the compression chamber 108, so that it can directly complete the function of compensating the volume of the hydraulic oil in the compression stroke or the tension stroke of the shock absorber inside the outer cylinder 105. In particular, the accumulator body 302 can adopt a piston type or an airbag type.

[0062] In this embodiment, the flow direction and principle of the hydraulic oil in the compression stroke and the tension stroke of the shock absorber are the same as those in the previous embodiment, and will not be elaborated here.

[0063] Embodiment 4

[0064] This embodiment is a further improvement of the previous embodiment, and the repeated content will not be elaborated here.

[0065] As Figure 10As shown, in this embodiment, the basic valve system 203 of the damping valve can be arranged on the piston head 102, and the adjustable valve system 204 is the same as that in the previous embodiment and is still arranged outside the piston portion 100. When the solenoid valve body 222 in the adjustable valve system 204 is closed, the shock absorber uses the basic valve system 203 on the piston head 102 for damping during the compression stroke and the extension stroke; when the solenoid valve body 222 in the adjustable valve system 204 is opened, the shock absorber uses the basic valve system 203 on the piston head 102 and the adjustable valve system 204 outside the piston portion 100 to achieve damping adjustment during the compression stroke and the extension stroke.

[0066] In this embodiment, the flow direction and principle of the hydraulic oil during the compression stroke and the extension stroke of the shock absorber are the same as those in the previous embodiment and will not be elaborated here.

[0067] Embodiment 5

[0068] This embodiment is a further improvement of the previous embodiment, and the repeated content will not be elaborated here.

[0069] As Figure 11 shown, in this embodiment, the installation position of the accumulator body 302 can be arranged inside the outer cylinder 105, and the specific position is adjacent to the compression chamber 108.

[0070] In this embodiment, the flow direction and principle of the hydraulic oil during the compression stroke and the extension stroke of the shock absorber are the same as those in the previous embodiment and will not be elaborated here.

[0071] It should be noted that the above specific embodiments are exemplary. Those skilled in the art can come up with various solutions inspired by the disclosed content of the present invention, and these solutions also fall within the scope of the disclosure of the present invention and within the protection scope of the present invention. Those skilled in the art should understand that the specification and drawings of the present invention are illustrative and do not constitute a limitation on the claims. The protection scope of the present invention is defined by the claims and their equivalents. The specification of the present invention contains multiple inventive concepts. For example, "preferably" or "according to a preferred embodiment" indicates that the corresponding paragraph discloses an independent concept. The applicant reserves the right to file divisional applications according to each inventive concept. Throughout the text, the features guided by "preferably" are only optional ways and should not be understood as must be provided. Therefore, the applicant reserves the right to waive or delete relevant preferred features at any time.

Claims

1. A dual-valve multi-stage electronically controlled shock absorber with an accumulator, comprising: The piston part (100), the damping part (200) and the energy storage part (300) are characterized in that: The damping part (200) comprises a damping valve housing (200a) having two chambers arranged in parallel therein for accommodating a first damping valve (201) and a second damping valve (202) respectively; a through hole (207) is provided on the chamber wall between the two damping valves to form an oil path for hydraulic oil to flow in the damping valve housing (200a); the energy storage part (300) is connected to the adjustment hole (208) of the damping valve housing (200a); The piston part (100) includes a working cylinder (104) and a cylinder body formed by interconnecting an outer cylinder (105) and a base (106) and being sleeved outside the working cylinder (104). The hollow interlayer between the cylinder body and the working cylinder (104) is blocked by a second sealing component (114), thereby forming a first oil passage (109) connected to the first oil passage hole (205) of the first damping valve (201) and a second oil passage (112) connected to the second oil passage hole (206) of the second damping valve (202) on both sides of the second sealing component (114).

2. The shock absorber according to claim 1, characterized in that: The working cylinder (104) is internally provided with a piston rod (101) and a piston head (102) fixedly connected to the bottom end of the piston rod (101); the piston head (102) separates the working cylinder (104) into a compression chamber (108) and a stretching chamber (110); wherein the first oil passage (109) is connected to the compression chamber (108), and the second oil passage (112) is connected to the stretching chamber (110) via a connecting hole (111) provided on the working cylinder (104).

3. The vibration absorber according to claim 1 or 2, characterized in that: The energy storage unit (300) comprises an accumulator body (302) connected to the base (106) via a third sealing assembly (115); the accumulator body (302) is provided with an oil injection port (301) aligned with the adjustment hole (208); a movable accumulator piston (303) is installed inside the accumulator body (302); the accumulator piston (303) divides the inside of the accumulator body (302) into two chambers for adjusting the pressure of the shock absorber, wherein the chamber close to the oil injection port (301) is an oil chamber (305), and the other chamber is an air chamber (304).

4. The vibration absorber according to any one of claims 1 to 3, characterized in that: The first damping valve (201) and the second damping valve (202) are both provided with a basic valve system (203) for providing a fixed damping force and an adjustable valve system (204) for providing a variable damping force, wherein the basic valve system (203) includes a basic valve seat (209), a connecting piece and a one-way valve group, and the adjustable valve system (204) includes an overflow valve seat (218), an overflow valve core (219) and an overflow spring (220).

5. The vibration absorber according to any one of claims 1 to 4, characterized in that: The basic valve seat (209) used for fixing the basic valve system (203) in the damping valve housing (200a) can separate the hydraulic oil chamber in the damping valve housing (200a) into two chambers, wherein the chamber close to the working cylinder (104) is the first chamber, and the chamber away from the working cylinder (104) is the second chamber. The basic valve seat (209) is provided with a through hole that can be controllably opened and closed by the one-way valve group to connect the hydraulic oil in the first chamber and the second chamber.

6. The shock absorber according to any one of claims 1 to 5, characterized in that: The one-way valve group includes a first rigidity one-way valve disposed in the first cavity and a second rigidity one-way valve disposed in the second cavity, the first rigidity being smaller than the second rigidity. The first stiffness one-way valve comprises a first spring (212) and a first valve plate (213); the first spring (212) can drive the first valve plate (213) away from the basic valve seat (209) when the hydraulic oil flows from the second cavity to the first cavity, thereby opening the through hole of the basic valve seat (209) blocked by the first valve plate (213); The second stiffness one-way valve comprises a second spring (214), a second valve plate (216) and a gasket (215) arranged therebetween. The second spring (214) can drive the second valve plate (216) away from the basic valve seat (209) to open the through hole when the hydraulic oil flows from the first cavity to the second cavity, and in the process generate a damping force on the hydraulic oil.

7. The vibration absorber according to any one of claims 1 to 6, characterized in that: The connecting member comprises a first connecting member (210) and a second connecting member (211), wherein the first connecting member (210) is arranged in the first cavity and the second cavity in the form of penetrating the basic valve seat (209), and the second connecting member (211) is fixedly connected to the first connecting member (210) and arranged in the second cavity.

8. The vibration absorber according to any one of claims 1 to 7, characterized in that: The overflow valve seat (218) and the overflow valve core (219) are coaxially arranged, and both are connected to the end of the second connecting member (211). The overflow spring (220) located between the overflow valve seat (218) and the overflow valve core (219) can impose constraints on the range of movement of the overflow valve core (219).

9. The vibration absorber according to any one of claims 1 to 8, characterized in that: The adjustable valve system (204) comprises an electromagnetic valve seat (221), an electromagnetic valve body (222) and an electromagnetic coil (223); the electromagnetic valve seat (221) is coaxially arranged with the overflow valve seat (218); one end of the electromagnetic valve seat (221) expands along the axial radial direction and is provided with a fourth sealing component (224) for sealing the gap between the end and the damping valve housing (200a); the electromagnetic valve body (222) and the electromagnetic coil (223) are installed on a side of the electromagnetic valve seat (221) away from the basic valve system (203).

10. The vibration absorber according to any one of claims 1 to 9, characterized in that: The electromagnetic coil (223) is arranged on the outside of the electromagnetic valve body (222) in a surrounding manner, and can control the opening or closing of the electromagnetic valve body (222) after being energized, thereby achieving adjustability of the damping force by adjusting the flow path of the hydraulic oil.

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