Shock absorber

Abstract

The invention relates to the technical field of passenger car suspensions, and provides a shock absorber which comprises a first working cylinder, a second working cylinder, a third working cylinder, a fourth working cylinder, a piston rod assembly arranged in the first working cylinder, a guider oil seal assembly located at the end of the fourth working cylinder, a bottom valve, a transition ring and an energy accumulator communicated with a fourth working cavity. The first working cylinder, the second working cylinder, the third working cylinder and cavities among the first working cylinder, the second working cylinder and the third working cylinder form an inner cavity valve path through a plurality of oil passing holes and transition rings, the fifth working cavity is communicated with the fourth working cavity through a compression electromagnetic valve, the fourth working cavity is communicated with the third working cavity through a recovery electromagnetic valve, and physical separation and independent control of compression and recovery flow paths in the inner cavity are achieved. According to the structure, a large number of external flanges, hoses and connectors are replaced with a built-in valve way and multi-cavity shunting, the axial / radial size occupation and leakage risk are remarkably reduced, the valve response speed and damping adjusting precision are improved, the pressure difference of a single sealing piece is reduced, the service life of sealing and mechanical pieces is prolonged, and therefore reliability, maintainability, NVH and the riding comfort of the whole vehicle are improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of passenger car suspensions, and in particular to a shock absorber. BACKGROUND

[0002] With the development of active suspensions and high-performance chassis control technology of the whole vehicle, the full-active shock absorber becomes a key actuator for improving the handling and comfort of the vehicle due to its variable damping force and active energy management capability. At present, the mainstream full-active shock absorber adopts a single-cylinder or double-cylinder structure.

[0003] The shock absorber with the existing structure occupies more space, and such space occupation is difficult to adapt to low suspension structures or vehicle platforms with limited space, thereby limiting the application of the full-active shock absorber on compact, ultra-low chassis or limited model vehicles. SUMMARY

[0004] In view of the above-mentioned shortcomings of the prior art, the purpose of the present application is to provide a shock absorber to improve the applicability of the shock absorber.

[0005] To achieve the above-mentioned purpose and other related purposes, the present application provides a shock absorber, comprising:

[0006] a first working cylinder;

[0007] a piston rod assembly arranged in the first working cylinder, the piston rod assembly comprising a piston and a piston rod, the piston dividing an internal cavity of the first working cylinder into a compression cavity and a recovery cavity;

[0008] a second working cylinder arranged outside the first working cylinder, a cavity between the second working cylinder and the first working cylinder constituting a second working cavity, the first working cylinder being provided with a first oil passage hole for connecting the recovery cavity and the second working cavity;

[0009] a third working cylinder arranged outside the second working cylinder, a cavity between the third working cylinder and the second working cylinder constituting a third working cavity, the second working cylinder being provided with a second oil passage hole for connecting the third working cavity and the second working cavity;

[0010] a fourth working cylinder arranged outside the third working cylinder, a cavity between the fourth working cylinder and the third working cylinder constituting a fourth working cavity;

[0011] a guide oil seal assembly arranged at a first end of the fourth working cylinder;

[0012] a bottom valve arranged at a second end of the fourth working cylinder, the bottom valve being provided with a first flow channel of the bottom valve;

[0013] A transition ring is arranged between the second working cylinder and the fourth working cylinder, a chamber between the transition ring and the second working cylinder forms a fifth working chamber, the transition ring is connected with the end of the third working cylinder through a connector, the compression chamber is communicated with the fifth working chamber through the first flow channel of the bottom valve, the fifth working chamber is communicated with the fourth working chamber through a compression electromagnetic valve, and the fourth working chamber is communicated with the third working chamber through a recovery electromagnetic valve.

[0014] An accumulator is communicated with the fourth working chamber.

[0015] In an embodiment of the present application, a third flow channel of the bottom valve is arranged in the bottom valve and communicated with the fourth working chamber, the accumulator is arranged outside the fourth working cylinder, and the third flow channel of the bottom valve is communicated with the accumulator through a pipeline.

[0016] In an embodiment of the present application, a second flow channel of the bottom valve is arranged in the bottom valve and communicated with the second working chamber, a first oil passage valve and a second oil passage valve are arranged on the bottom valve, the first oil passage valve is communicated with the second flow channel of the bottom valve, the second oil passage valve is communicated with the first flow channel of the bottom valve, and the first oil passage valve and the second oil passage valve are connected with an electro-hydraulic pump through a reversing valve.

[0017] In an embodiment of the present application, the first end of the transition ring is interference-fitted with the connector, and the second end of the transition ring is interference-fitted with the bottom valve.

[0018] In an embodiment of the present application, the compression electromagnetic valve comprises a compression check valve side small hole, a compression check valve center hole and a compression oil outlet, the compression check valve center hole is communicated with the fifth working chamber, the compression oil outlet and the compression check valve side small hole are communicated with the fourth working chamber, the one-way valve direction between the compression check valve side small hole and the compression check valve center hole is from the compression check valve side small hole to the compression check valve center hole, and the compression check valve center hole and the compression oil outlet are communicated with the inside of the compression electromagnetic valve.

[0019] In an embodiment of the present application, the recovery electromagnetic valve comprises a recovery check valve side small hole, a recovery check valve center hole and a recovery oil outlet, the recovery check valve center hole is communicated with the third working chamber, the recovery oil outlet and the recovery check valve side small hole are communicated with the fourth working chamber, the one-way valve direction between the recovery check valve side small hole and the recovery check valve center hole is from the recovery check valve side small hole to the recovery check valve center hole, and the recovery check valve center hole and the recovery oil outlet are communicated with the inside of the recovery electromagnetic valve.

[0020] In a specific embodiment of the present application, the restoring solenoid valve and the compression solenoid valve are connected to the outer side of the fourth working cylinder.

[0021] In a specific embodiment of the present application, the restoring solenoid valve and the compression solenoid valve are arranged in a staggered manner in the axial direction of the shock absorber.

[0022] In a specific embodiment of the present application, the projection angle of the axial centers of the restoring solenoid valve and the compression solenoid valve in the axial direction of the shock absorber is 0-180°.

[0023] In a specific embodiment of the present application, the piston is provided with a compression pressure relief valve and a restoring pressure relief valve, and the compression pressure relief valve and the restoring pressure relief valve are two one-way valves in opposite directions.

[0024] The present application proposes a shock absorber. In the above scheme, the built-in valve path and the multi-layer coaxial sleeve replace a large number of external flanges, hoses and joints, reduce potential leakage paths, improve system sealing reliability, reduce maintenance frequency and operation and maintenance cost. The multi-cavity shares the pressure, reduces the pressure difference and wear of the single sealing element, the oil seal assembly of the guide is radially positioned and wiped to protect the rod end and reduce the damage of the rod surface, thereby prolonging the service life of the sealing and mechanical parts and improving the durability of the whole machine. BRIEF DESCRIPTION OF DRAWINGS

[0025] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the following will briefly introduce the drawings needed to be used in the embodiment description. Obviously, the drawings in the following description are only some embodiments of the present application, and other drawings can also be obtained by those skilled in the art without creative labor.

[0026] Figure 1 It is a structure schematic diagram of the shock absorber in an embodiment of the present application;

[0027] Figure 2 It is an oil flow diagram of the restoring process of the shock absorber in an embodiment of the present application;

[0028] Figure 3 It is a principle diagram of the shock absorber in an embodiment of the present application;

[0029] Figure 4 It is a schematic diagram of the bottom valve and the oil passage valve seat assembly of the shock absorber in an embodiment of the present application;

[0030] Figure 5 It is a structure schematic diagram of the oil passage valve of the shock absorber in an embodiment of the present application;

[0031] Figure 6 It is a structure schematic diagram of the bottom valve of the shock absorber in an embodiment of the present application;

[0032] Figure 7 This is a three-dimensional structural diagram of the vibration damper according to one embodiment of the present invention;

[0033] Figure 8 This is a schematic diagram of the end face of the vibration damper in one embodiment of the present invention;

[0034] Figure 9 This is a cross-sectional view of a vibration damper according to one embodiment of the present invention.

[0035] Explanation of reference numerals in the attached drawings: 11. First working cylinder; 12. Second working cylinder; 13. Third working cylinder; 14. Fourth working cylinder; 15. Transition ring; 16. Connector; 17. First oil passage; 18. Second oil passage; 20. Guide oil seal assembly; 30. Bottom valve; 31. Second flow channel of bottom valve; 32. First flow channel of bottom valve; 33. Directional valve; 34. Electro-hydraulic pump; 35. First oil passage valve; 36. Second oil passage valve; 37. Third flow channel of bottom valve; 40. Accumulator; 50. Piston rod assembly Components; 51. Piston rod; 52. Piston; 53. Compression relief valve; 54. Reset relief valve; 61. Reset chamber; 62. Compression chamber; 63. Second working chamber; 64. Third working chamber; 65. Fourth working chamber; 66. Fifth working chamber; 70. Compression solenoid valve; 71. Side hole of compression check valve; 72. Center hole of compression check valve; 73. Compression oil outlet; 80. Reset solenoid valve; 81. Side hole of reset check valve; 82. Center hole of reset check valve; 83. Reset oil outlet. Detailed Implementation

[0036] The following specific examples illustrate the implementation of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. The present invention can also be implemented or applied through other different specific embodiments, and various details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of the present invention. It should be noted that, unless otherwise specified, the following embodiments and features described therein can be combined with each other.

[0037] It should be noted that the illustrations provided in the following embodiments are only schematic representations of the basic concept of the present invention. Therefore, the illustrations only show the components related to the present invention and are not drawn according to the actual number, shape and size of the components in the actual implementation. In the actual implementation, the form, quantity and proportion of each component can be arbitrarily changed, and the layout of the components may also be more complex.

[0038] With the development of active suspension and high-performance chassis control technologies, fully active shock absorbers, due to their variable damping force and active energy management capabilities, have become key actuators for improving vehicle handling and comfort. Currently, most mainstream fully active shock absorbers adopt a single-tube or twin-tube structure, and their structure and working method have certain commonalities.

[0039] A typical fully active vibration damper consists of the following core components:

[0040] The working cylinder (with built-in piston valve) is the main chamber used to generate damping force and realize telescopic movement;

[0041] The oil reservoir (surrounding the working cylinder) is used to hold and return oil.

[0042] An integrated solenoid valve assembly (usually located at the top or bottom of the piston rod) adjusts the damping by changing the cross-sectional area of ​​the oil flow through an electric drive.

[0043] The accumulator releases and absorbs oil during the extension and retraction of the piston rod to compensate for the volume change of the piston rod.

[0044] Its working principle is as follows: the solenoid valve achieves instantaneous damping adjustment by changing the flow cross-sectional area of ​​the oil circuit; during the piston rod extension (compression) or retraction (restoration) process, additional oil compensation is required due to the change in piston rod volume. The accumulator, as a fluid volume compensation and energy storage device, undertakes the transfer of oil between the compression and restoration strokes to maintain system pressure and oil balance. To accommodate the control of both compression and restoration strokes, existing designs typically use a shared valve body or coaxially stacked valve assemblies for the control valve bodies of the two oil circuits.

[0045] However, the combination of axially integrated solenoid valve assemblies and external accumulators results in the solenoid valves stacking along the piston rod axis, significantly increasing the overall axial height of the shock absorber. Furthermore, the external accumulator and its connecting pipes occupy lateral space, increasing the lateral width of the shock absorber. This space occupancy makes it difficult to adapt to low-slung suspension structures or space-constrained vehicle platforms, limiting the application of fully active shock absorbers in compact, ultra-low chassis, or styling-constrained vehicles. At the same time, axial stacking and external components can also lead to issues such as mass concentration, increased installation complexity, increased risk of pipe leaks, and higher maintenance costs, affecting system integration and reliability.

[0046] like Figures 1-9 As shown, the present invention proposes a vibration damper, including a first working cylinder 11, a piston rod assembly 50, a second working cylinder 12, a third working cylinder 13, a fourth working cylinder 14 (oil reservoir), a guide oil seal assembly 20, a bottom valve 30, a transition ring 15, and an accumulator 40.

[0047] The piston rod assembly 50 is disposed inside the first working cylinder 11. The piston rod assembly 50 includes a piston 52 and a piston rod 51. The piston 52 divides the internal chamber of the first working cylinder 11 into a compression chamber 62 and a recovery chamber 61.

[0048] The second working cylinder 12 is sleeved on the outside of the first working cylinder 11. The chamber between the second working cylinder 12 and the first working cylinder 11 forms the second working chamber 63. The first working cylinder 11 is provided with a first oil passage hole 17 for connecting the restoration chamber 61 and the second working chamber 63.

[0049] The third working cylinder 13 is sleeved on the outside of the second working cylinder 12. The chamber between the third working cylinder 13 and the second working cylinder 12 forms the third working chamber 64. The second working cylinder 12 is provided with a second oil passage hole 18 for connecting the third working chamber 64 and the second working chamber 63.

[0050] The fourth working cylinder 14 is sleeved on the outside of the third working cylinder 13, and the chamber between the fourth working cylinder 14 and the third working cylinder 13 constitutes the fourth working chamber 65.

[0051] Multi-layer coaxial sleeves and internal valve circuits replace external connections, reducing external flanges, piping, and sealing joints, compressing potential leakage paths, and lowering the risk of oil leakage. Multiple cavities distribute pressure, reducing the pressure differential and wear on individual seals, and improving system durability.

[0052] The guide oil seal assembly 20 is located at the first end (e.g., the upper end) of the fourth working cylinder 14. The guide oil seal assembly 20 primarily performs guiding, sealing, dustproofing, and lubrication functions. It precisely aligns with the piston rod 51, restricts radial displacement and sway, and transfers lateral loads to the guide members to reduce the impact and wear of the rod end on the inner cavity components. The oil seal seals the fourth working chamber 65, preventing oil leakage and blocking external dust, moisture, and air from entering, protecting the built-in air bag and inner cavity valve circuit from contamination and gas ingress. The wiping lip removes impurities from the rod surface and maintains the lubricating film, reducing friction and jamming, and improving low-speed response sensitivity. Overall, it extends the lifespan of the seals and piston rod 51, reduces maintenance and leakage risks, improves damping control accuracy, and helps improve NVH and vehicle handling performance.

[0053] The bottom valve 30 is located at the second end (e.g., the lower end) of the fourth working cylinder 14, and the bottom valve 30 is provided with a bottom valve first flow channel 32.

[0054] A transition ring 15 is disposed between the second working cylinder 12 and the fourth working cylinder 14. The chamber between the transition ring 15 and the second working cylinder 12 constitutes the fifth working chamber 66. The transition ring 15 is connected to the end of the third working cylinder 13 via a connector 16. The compression chamber 62 is connected to the fifth working chamber 66 via the first flow channel 32 of the bottom valve. The fifth working chamber 66 is connected to the fourth working chamber 65 via a compression solenoid valve 70. The fourth working chamber 65 is connected to the third working chamber 64 via a recovery solenoid valve 80. The system includes two solenoid valve assemblies, serving as the compression solenoid valve 70 for the compression path and the recovery solenoid valve 80 for the recovery path. This physically separates the compression and recovery flow paths within the internal cavity, allowing for independent adjustment of the compression and recovery damping forces. The independent solenoid valve layout eliminates the mutual influence and coupling between compression and recovery, enabling individual calibration of damping characteristics for different operating conditions and improving the coordination between vehicle handling and ride comfort. The short flow channel within the internal cavity, combined with the orderly flow diversion of the transition ring 15, improves the regulation response speed and control accuracy, facilitating rapid closed-loop control and more refined low-speed / high-speed damping vectoring. Simultaneously, the built-in valve path and transition ring 15 structure reduce external piping and connectors, lowering leakage points and installation complexity, thus enhancing reliability and durability. Independent regulation also facilitates the implementation of degraded control strategies (such as single-path bypass or flow limiting) under fault or failure conditions, improving system safety and maintainability.

[0055] The accumulator 40 is connected to the fourth working chamber 65.

[0056] like Figure 6 As shown, in a specific embodiment of the present invention, the bottom valve 30 is provided with a bottom valve third flow channel 37 communicating with the fourth working chamber 65, and the accumulator 40 is disposed outside the fourth working cylinder 65. The bottom valve third flow channel 37 is connected to the accumulator 40 through a pipeline. The external accumulator 40 releases the spatial constraints of the shock absorber, making it easier to install in low or restricted suspension layouts. The shock absorber volume is reduced, making maintenance and replacement easier. Heat dissipation conditions are improved, which is beneficial for temperature management. Part of the mass can be fixed to the vehicle body to reduce the unsprung mass, which is beneficial for handling and comfort. Standardized external accumulators 40 can be used to reduce procurement costs and achieve flexible selection. External pipelines and additional volume increase system compliance and fluid inertia, which may lead to transient response delays or oscillations. Pipelines and joints increase potential leakage points and bring additional pressure drops. It is necessary to reserve installation space for the accumulator 40 in the vehicle body layout and consider the effects of NVH and temperature.

[0057] like Figure 1As shown, in a specific embodiment of the present invention, the compression solenoid valve 70 includes a compression check valve side hole 71, a compression check valve center hole 72, and a compression outlet 73. The compression check valve center hole 72 communicates with the fifth working chamber 66, and the compression outlet 73 and the compression check valve side hole 71 communicate with the fourth working chamber 65. The one-way valve direction between the compression check valve side hole 71 and the compression check valve center hole 72 is from the compression check valve side hole 71 to the compression check valve center hole 72. The compression check valve center hole 72 and the compression outlet 73 communicate internally with the compression solenoid valve 70. This one-way valve arrangement allows for a low-impedance bypass path in one direction, while in the opposite flow direction, the fluid must pass through the adjustable throttling channel of the solenoid valve. By combining the electrically controlled opening of the solenoid valve, the flow rate under compression conditions can be precisely adjusted to achieve the required damping characteristics, while the check valve can provide rapid bypass or prevent reverse flow when needed, reduce transient pressure rise, improve valve response speed and cavitation resistance, and provide a degradation path when the solenoid valve is closed or fails, thereby improving reliability and safety.

[0058] like Figure 1 As shown, in a specific embodiment of the present invention, the recovery solenoid valve 80 includes a recovery check valve side hole 81, a recovery check valve center hole 82, and a recovery outlet 83. The recovery check valve center hole 82 communicates with the third working chamber 64, and the recovery outlet 83 and the recovery check valve side hole 81 communicate with the fourth working chamber 65. The one-way valve direction between the recovery check valve side hole 81 and the recovery check valve center hole 82 is from the recovery check valve side hole 81 to the recovery check valve center hole 82. The recovery check valve center hole 82 and the recovery outlet 83 communicate internally with the recovery solenoid valve 80. This structure allows the recovery flow path to obtain a low-resistance channel (check valve bypass) in its permissible direction, while in the direction requiring controlled regulation, the fluid must pass through the variable throttling orifice of the recovery solenoid valve 80, thereby achieving independent and precise adjustment of the recovery damping force. This arrangement avoids mutual interference between the compression / recovery channels, improving the decoupling and control accuracy of the two damping paths. Simultaneously, the rapid bypass of the check valve improves low-speed sensitivity and transient response, reduces pressure fluctuations and noise, and provides a safe degraded path in case of valve failure, enhancing system reliability.

[0059] In the above scheme, under CDC mode, when the shock absorber is compressed (electrohydraulic pump 34 is not working), the piston rod 51 assembly moves towards the bottom valve 30, and the volume of the compression chamber 62 decreases. During this process, the oil in the compression chamber 62 passes through the center hole of the bottom valve, through the first flow channel 32 of the bottom valve, and enters the fifth working chamber 66. The oil from the fifth working chamber 66 passes through the center hole 72 of the compression check valve, and then enters the compression solenoid valve 70 (at this time, the throttling is adjustable). After throttling, it enters the fourth working chamber 65 from the compression outlet 73. At the same time, the piston rod 51 assembly moves towards the bottom valve 30, and the volume of the recovery chamber 61 increases. During this process, the oil in the fourth working chamber 65 pushes open the small hole 81 on the side of the recovery check valve and enters the center hole of the recovery solenoid valve 80, then enters the third working chamber 64, passes through the second oil passage hole 18 to enter the second working chamber 63, and then passes through the first oil passage hole 17 to enter the recovery chamber 61.

[0060] That is: compression chamber 62 → bottom valve center hole → bottom valve first flow channel 32 → fifth working chamber 66 → compression check valve center hole 72 (enters compression solenoid valve 70) → through the throttling channel of compression solenoid valve 70 (throttling flow adjustable) → compression oil outlet 73 → fourth working chamber 65 → push open the small hole 81 on the side of the restoration check valve → restoration check valve center hole 82 → third working chamber 64 → through the second oil passage hole 18 (oil passage hole on the second working cylinder 12) → second working chamber 63 → through the first oil passage hole 17 (oil passage hole on the first working cylinder 11) → restoration chamber 61, completing the oil replenishment return flow.

[0061] In the above scheme, under the CDC model, such as Figure 2 As shown, when the shock absorber is stretched (with the electro-hydraulic pump 34 not operating), the piston rod 51 assembly moves away from the bottom valve 30, reducing the volume of the recovery chamber 61. During this process, the oil in the recovery chamber 61 enters the second working chamber 63 through the first oil passage 17, then through the second oil passage 18 into the third working chamber 64, and then through the center hole 82 of the recovery check valve into the recovery solenoid valve 80 (throttling is adjustable at this time). After throttling, it enters the fourth working chamber 65 from the recovery outlet 83. Simultaneously, the piston rod 51 assembly moves away from the bottom valve 30, increasing the volume of the compression chamber 62. During this process, the oil in the fourth working chamber 65 pushes open the side hole 71 of the compression check valve and enters the center hole with the compression check valve, then flows into the fifth working chamber 66, and finally enters the compression chamber 62 through the first flow channel 32 of the bottom valve. The compression damping force can be controlled and adjusted by the compression solenoid valve 70 assembly.

[0062] That is: the oil flows through the recovery chamber 61 → through the first oil passage 17 → the second working chamber 63 → through the second oil passage 18 → the third working chamber 64 → into the center hole 82 of the recovery check valve (the check valve allows flow in this direction) → into the internal throttling channel of the recovery solenoid valve 80 (at this time, the solenoid valve is throttled according to the set value) → discharged from the recovery outlet 83 into the fourth working chamber 65 (oil storage chamber). The oil in the fourth working chamber 65 acts on the accumulator 40 to compensate for the extended volume of the piston rod 51.

[0063] like Figure 1 As shown, in a specific embodiment of the present invention, the bottom valve 30 is provided with a second flow channel 31, which is connected to the second working chamber 63. The bottom valve 30 is provided with a first oil valve 35 and a second oil valve 36. The first oil valve 35 is connected to the first flow channel 32, and the second oil valve 36 is connected to the second flow channel 31. The first oil valve 35 and the second oil valve 36 are connected to the electro-hydraulic pump 34 via a reversing valve 33. It has rapid lifting and rapid lowering functions. The first oil valve 35 and the second oil valve 36 remain open before the shock absorber is filled with oil. After the shock absorber is filled with oil, the oil valves can be manually adjusted to the closed state to achieve pre-pressurization before transportation. After the shock absorber is installed on the vehicle, the oil valves are manually adjusted to the open state again, so that the internal oil circuit of the shock absorber is connected to the external oil pipe, forming a complete circuit.

[0064] like Figure 3 As shown, when the electro-hydraulic pump 34 is engaged, the system no longer passively drives the flow of oil in the chamber solely through the stroke of the piston 52. Instead, the pump sends high-pressure oil into one side chamber via the reversing valve 33, creating a controlled chamber pressure difference. This actively generates a driving force that causes the piston rod 51 to extend or retract rapidly. The oil propelled by the driving force flows back to the pump's suction port through the inner cavity channel on the other side, forming a complete hydraulic circuit. The reversing valve 33 determines the pump flow direction and cooperates with the two oil passage valves / flow channels in the bottom valve 30 to achieve the two working modes of extension / retraction.

[0065] In active mode, when the shock absorber is stretched (the electro-hydraulic pump 34 component participates in the circuit operation), the electro-hydraulic pump 34 operates, pumping out high-pressure oil that passes through the reversing valve 33, then through the oil pipe to the first flow channel 32 of the bottom valve, and finally enters the compression chamber 62. At this time, the compression chamber 62 is filled with high-pressure oil, while the pressure in the recovery chamber 61 is lower. The pressure difference will generate an upward thrust on the piston 52, causing the piston rod 51 to move upward and lift rapidly. At the same time, the oil in the recovery chamber 61 enters the second working chamber 63 through the first oil passage 17, then enters the second flow channel 31 of the bottom valve, and finally enters the hydraulic pump suction port through the oil pipe and the reversing valve 33, thus forming a complete circuit.

[0066] That is: electro-hydraulic pump 34 high pressure outlet → reversing valve 33 (set to supply oil to the first flow channel) → oil pipe → bottom valve first flow channel 32 → compression chamber 62 (filled with high pressure oil by the pump).

[0067] The oil discharged from the recovery chamber 61 → enters the second working chamber 63 through the first oil passage 17 → through the second flow channel 31 of the bottom valve → oil pipe → reversing valve 33 → returns to the oil suction port of the electro-hydraulic pump 34 (forming a circuit).

[0068] In active mode, when the shock absorber is compressed (the electro-hydraulic pump 34 component participates in the circuit operation), the electro-hydraulic pump 34 operates, and the pumped high-pressure oil passes through the reversing valve 33, then through the oil pipe into the second flow channel 31 of the bottom valve, then into the second working chamber 63, and finally into the recovery chamber 61 through the first oil passage 17. At this time, the recovery chamber 61 is filled with high-pressure oil, while the pressure in the compression chamber 62 is lower. The pressure difference will generate a downward thrust on the piston 52, causing the piston rod 51 to descend rapidly. At the same time, the oil in the compression chamber 62 directly enters the hydraulic pump suction port through the first flow channel 32 of the bottom valve, through the oil pipe and the reversing valve 33, thus forming a complete circuit.

[0069] That is, the high-pressure outlet of the electro-hydraulic pump 34 → the reversing valve 33 (set to supply oil to the second flow channel) → the oil pipe → the second flow channel 31 of the bottom valve → the second working chamber 63 → through the second oil passage 18 → the third working chamber 64 → through the center hole 82 of the reset check valve ( / the passage of the reset solenoid valve 80) → into the reset chamber 61.

[0070] The oil discharged from the compression chamber 62 → passes through the first flow channel 32 of the bottom valve → oil pipe → reversing valve 33 → returns to the oil suction port of the electro-hydraulic pump 34 (completing the circuit).

[0071] In active mode, high-pressure oil is delivered to the compression chamber 62 or the recovery chamber 61 via the electro-hydraulic pump 34 and the reversing valve 33, creating a controlled pressure difference and driving the piston 52 to rapidly extend / retract. Simultaneously, oil on the other side flows back to the pump suction port through the inner cavity oil passage and the bottom valve 30, forming a closed loop. This operating mode enables the shock absorber to have rapid lifting / lowering, precise attitude control, and active damping capabilities.

[0072] In one specific embodiment of the invention, the first end of the transition ring 15 is interference-fitted with the connector 16, and the second end of the transition ring 15 is interference-fitted with the bottom valve 30. Here, the interference fit mechanically clamps the transition ring 15 onto the connector 16 and the bottom valve 30, pre-tightening and positioning the transition ring 15 radially / axially. The interference fit is typically controlled by tolerance and assembled using a heating or cold assembly process. The purpose here is to form a rigid, concentric mechanical connection between the transition ring 15 and adjacent parts, eliminating gaps and ensuring radial concentricity and axial positioning.

[0073] like Figure 7 ,8 As shown, in a specific embodiment of the present invention, the recovery solenoid valve 80 and the compression solenoid valve 70 are connected to the outside of the fourth working cylinder 14. These two valves are installed on the outside of the fourth working cylinder 14, meaning the valve bodies are located outside the cylinder body rather than within the internal cavity, and communicate with the oil chamber of the fourth working cylinder 14 through an external interface. The coils of the solenoid valves, electrical connectors, and the external structure of the recovery solenoid valve 80 are all easily arranged and maintained from the outside.

[0074] like Figure 1 , 2 As shown in Figure 7, in a specific embodiment of the present invention, the recovery solenoid valve 80 and the compression solenoid valve 70 are arranged in a staggered manner along the axial direction of the vibration damper. Axial stagger means that the two valves do not overlap in the axial direction of the vibration damper, but are arranged with a certain offset distance along the axis, so that they are not superimposed in the same axial position. This reduces the axial dimension stacking, facilitates the distribution of valves into available space, and improves the overall structural compactness. It avoids mutual interference between valve bodies or concentrated loads at the same point, which is beneficial for thermal management and vibration isolation. It allows for optimization of the flow path arrangement of each valve, shortening the diameter of a certain flow path or simplifying the pipe connection path. It facilitates division of labor in processing and assembly, reducing the technological difficulty of a single area.

[0075] like Figure 8 As shown, in a specific embodiment of the present invention, the projection angle between the axes of the recovery solenoid valve 80 and the compression solenoid valve 70 on the axial direction of the shock absorber is 0-180°. The recovery solenoid valve 80 assembly and the compression solenoid valve 70 assembly are respectively arranged on the side of the shock absorber, and the axial projection angle α between the two solenoid valves is adjustable, making it easier to adapt to different arrangement spaces. Under different vehicle or equipment arrangement conditions, the valve position can be adjusted to avoid interference parts and facilitate pipeline routing and cable layout. Optimizing installation and maintenance channels, selecting the side that is easier to operate for valve installation reduces assembly difficulty. It can disperse heat sources and power connections, avoiding localized heat accumulation or cable congestion. Different arrangements such as 0° (same side) and 180° (opposite side) can be used to meet space, stress, and maintenance preferences.

[0076] like Figure 1 , 2As shown, in a specific embodiment of the present invention, the piston 52 is provided with a compression relief valve 53 and a recovery relief valve 54, which are two one-way valves in opposite directions. When the compression stroke speed is very fast or the pressure is too high, some of the high-pressure oil in the compression chamber 62 can push open the compression relief valve 53 in the piston rod assembly 50 and enter the recovery chamber 61. The compression relief valve 53 serves as overload protection. The compression damping force can be controlled and adjusted by the compression solenoid valve 70 assembly. When the recovery stroke speed is very fast or the pressure is too high, some of the high-pressure oil in the recovery chamber 61 can push open the recovery relief valve 54 in the piston rod assembly 50 and enter the compression chamber 62. The recovery relief valve 54 serves as overload protection.

[0077] In summary, this invention achieves a compact structure, low axial height, significantly reduced external piping and flange joints, and reduced leakage paths through the integrated design of multi-layer coaxial sleeves and internal valve circuits, interference fit of the transition ring 15, and the orderly arrangement of the foot valve 30, the recovery / compression solenoid valve 70, and the check valve. The multi-chamber pressure sharing and short internal flow channels reduce the pressure differential and wear borne by a single seal, improve durability, and enhance the response speed and control accuracy of damping adjustment. The recovery / compression solenoid valve 70, in conjunction with the check valve, physically separates the compression and recovery flow paths, allowing for independent and precise adjustment. This enables rapid lifting / lowering and precise attitude control in both CDC passive mode and electro-hydraulic pump 34 active mode, while also providing reliable overload protection through the pressure relief valve. The adjustable installation angle on the side and the external layout improve installation adaptability and maintainability. The oil valve design of the bottom valve 30 supports processes such as oil injection pre-pressurization, transportation isolation and on-site connection. Overall, it takes into account high-performance control, reliability, maintainability and engineering adaptability.

[0078] The above embodiments are merely illustrative of the principles and effects of the present invention and are not intended to limit the invention. Any person skilled in the art can modify or alter the above embodiments without departing from the spirit and scope of the present invention. Therefore, all equivalent modifications or alterations made by those skilled in the art without departing from the spirit and technical concept disclosed in the present invention should still be covered by the claims of the present invention.

[0079] Throughout this description, numerous specific details, such as examples of components and / or methods, are provided to provide a complete understanding of embodiments of the invention. However, those skilled in the art will recognize that embodiments of the invention may be practiced without one or more of these specific details or by other devices, systems, components, methods, parts, materials, components, etc. In other instances, well-known structures, materials, or operations have not been specifically shown or described in detail to avoid obscuring aspects of embodiments of the invention.

Claims

1. A damper characterized by, The utility model relates to a kind of hydraulic system, including: First working cylinder; Piston rod assembly is arranged in the first working cylinder, and the piston rod assembly includes piston and piston rod, and the piston divides the internal chamber of the first working cylinder into compression cavity and recovery cavity; Second working cylinder is sleeved outside the first working cylinder, and the chamber between the second working cylinder and the first working cylinder constitutes second working cavity, and first oil hole for communicating the recovery cavity and the second working cavity is opened on the first working cylinder; Third working cylinder is sleeved outside the second working cylinder, and the chamber between the third working cylinder and the second working cylinder constitutes third working cavity, and second oil hole for communicating the third working cavity and the second working cavity is opened on the second working cylinder; Fourth working cylinder is sleeved outside the third working cylinder, and the chamber between the fourth working cylinder and the third working cylinder constitutes fourth working cavity; Guide oil seal assembly is arranged at the first end of the fourth working cylinder; Bottom valve is arranged at the second end of the fourth working cylinder, and bottom valve first flow passage is arranged in the bottom valve; Transition ring is arranged between the second working cylinder and the fourth working cylinder, and the chamber between the transition ring and the second working cylinder constitutes fifth working cavity, and the end of the third working cylinder is connected with the transition ring by connector, the compression cavity is communicated with the fifth working cavity by the bottom valve first flow passage, the fifth working cavity is communicated with the fourth working cavity by compression solenoid valve, and fourth working cavity is communicated with third working cavity by recovery solenoid valve; Energy accumulator is communicated with the fourth working cavity.

2. The damper of claim 1, wherein Bottom valve third flow passage is arranged in the bottom valve and communicated with the fourth working cavity, and the energy accumulator is arranged outside the fourth working cylinder, and the bottom valve third flow passage is communicated with the energy accumulator by pipeline.

3. The damper of claim 1, wherein Bottom valve second flow passage is arranged in the bottom valve and communicated with the second working cavity, first oil passage valve and second oil passage valve are arranged on the bottom valve, the first oil passage valve is communicated with the bottom valve second flow passage, the second oil passage valve is communicated with the bottom valve first flow passage, and the first oil passage valve and the second oil passage valve are connected with electro-hydraulic pump by reversing valve.

4. The damper of claim 1, wherein The first end of the transition ring is interference fit with the connector, and the second end of the transition ring is interference fit with the bottom valve.

5. The damper of claim 1, wherein The compression solenoid valve includes compression check valve side small hole, compression check valve center hole and compression oil outlet, the compression check valve center hole is communicated with the fifth working cavity, the compression oil outlet and the compression check valve side small hole are communicated with the fourth working cavity, the one-way valve direction between the compression check valve side small hole and the compression check valve center hole is from the compression check valve side small hole to the compression check valve center hole, and the compression check valve center hole and the compression oil outlet are communicated with the inside of the compression solenoid valve.

6. The damper of claim 1, wherein The recovery electromagnetic valve comprises a recovery check valve side small hole, a recovery check valve center hole and a recovery oil outlet, the recovery check valve center hole is communicated with the third working chamber, the recovery oil outlet and the recovery check valve side small hole are communicated with the fourth working chamber, the direction of the check valve between the recovery check valve side small hole and the recovery check valve center hole is from the recovery check valve side small hole to the recovery check valve center hole, and the recovery check valve center hole and the recovery oil outlet are communicated with the inside of the recovery electromagnetic valve.

7. The damper of claim 1, wherein The recovery electromagnetic valve and the compression electromagnetic valve are connected to the outside of the fourth working cylinder.

8. The damper of claim 1, wherein The recovery electromagnetic valve and the compression electromagnetic valve are arranged in a staggered manner in the axial direction of the shock absorber.

9. The damper of claim 1, wherein The projection angle between the shaft centers of the recovery electromagnetic valve and the compression electromagnetic valve in the axial direction of the shock absorber is 0-180°.

10. The damper of claim 1, wherein The piston is provided with a compression pressure relief valve and a recovery pressure relief valve, and the compression pressure relief valve and the recovery pressure relief valve are two check valves with opposite directions.

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