Hydraulic damping valve, shock absorber, hydraulic suspension system and vehicle

Abstract

The invention discloses a hydraulic damping valve, a shock absorber, a hydraulic suspension system and a vehicle, relates to the technical field of vehicles, and aims to solve the problem that the hydraulic damping valve cannot timely, accurately and correspondingly change the damping degree when the flow of damping liquid changes suddenly. The hydraulic damping valve comprises a first assembly, a second assembly and an overflow adjusting device, the first assembly can reciprocate in the first direction relative to the second assembly, the second assembly comprises a connecting hole and a damping channel, and the two end faces, in the first direction, of the first assembly are matched with the second assembly to form a first space and a second space; the damping channel communicates with the first space and the second space. Thus, pressure difference is formed between the first space and the second space, then the first assembly moves relative to the second assembly, and overflow self-adjustment is achieved. Movement of the first assembly is not affected by fluctuation caused by friction of the damping liquid flowing inner wall in the damping channel, so that pressure fluctuation of the damping liquid in the first space and the second space is more stable.

Description

Technical Field

[0001] The present application relates to the field of vehicle technology, and in particular to a hydraulic damping valve, a shock absorber, a hydraulic suspension system and a vehicle. Background Art

[0002] To rapidly dampen vibrations between the vehicle frame and body, improving ride smoothness and comfort, automobile suspension systems are typically equipped with shock absorbers. Furthermore, to balance comfort and handling, suspension systems employ hydraulic pressure to adjust the shock absorber's stiffness and damping. For example, at high speeds, a higher stiffness or damping setting can be used to improve driver control and prevent vehicle roll. At lower speeds, a lower stiffness or damping setting can be used to better cushion road bumps and provide greater comfort.

[0003] Existing shock absorbers have complex structures. They can self-regulate by overflowing during the recovery and compression strokes to handle sudden changes in damping fluid flow velocity. However, fluctuations in the damping fluid flow rate can affect the movement of the magnetic core. The damping fluid can rub against the core's sidewalls or inner bore, shifting its position and affecting the damping effect. Summary of the Invention

[0004] The purpose of the present application is to provide a hydraulic damping valve, a shock absorber, a hydraulic suspension system and a vehicle, aiming to solve the problem that when the flow of the damping fluid suddenly changes, the hydraulic damping valve cannot promptly and accurately change the damping degree.

[0005] In a first aspect, a hydraulic damping valve is provided, comprising: a first component, a second component, and an overflow adjustment device; the first component is reciprocatable relative to the second component in a first direction; the second component comprises a connecting hole and a damping channel; the damping fluid is adapted to pass through the connecting hole to perform hydraulic damping; two end surfaces of the first component along the first direction cooperate with the second component to form a first space and a second space; the damping channel connects the first space and the second space; the first component comprises a main channel; and the overflow adjustment device is at least partially disposed in the main channel;

[0006] When the pressure of the damping fluid in the first space is greater than a threshold value, the damping fluid in the first space opens the overflow regulating device and flows out from the main channel, so that the pressure in the second space is greater than the pressure in the first space and pushes the first component to move relative to the second component along the first direction, thereby changing the aperture size of the connecting hole.

[0007] In an embodiment of the present application, the hydraulic damping valve comprises a first component, a second component, and an overflow adjustment device. The first component is reciprocatable relative to the second component in a first direction. The second component includes a connecting hole and a damping channel. Damping fluid is adapted to flow through the connecting hole to perform hydraulic damping. Two end surfaces of the first component along the first direction cooperate with the second component to form a first space and a second space. The damping channel connects the first and second spaces. The first component includes a main channel, and the overflow adjustment device is at least partially disposed in the main channel. When the pressure of the damping fluid in the first space exceeds a threshold, the damping fluid in the first space activates the overflow adjustment device and flows out of the main channel, causing the pressure in the second space to increase relative to the pressure in the first space and driving the first component to move relative to the second component in the first direction, thereby changing the diameter of the connecting hole. Thus, the second component is provided with a damping channel that connects the first and second spaces. The damping fluid in the first space passes through the overflow adjustment device, creating a pressure differential between the first and second spaces, thereby causing the first component to move relative to the second component, achieving self-regulating overflow. At this time, the movement of the first component is not affected by the fluctuation caused by the friction of the inner wall of the damping fluid in the damping channel, so that the pressure fluctuation of the damping fluid in the first space and the second space is more stable.

[0008] Optionally, the first component also includes a magnetic core component, and the second component also includes a core cover and a magnetic isolation ring, the magnetic isolation ring and the core cover are connected, the damping channel is arranged in the magnetic isolation ring and the core cover, the magnetic isolation ring and the core cover are arranged outside the magnetic core component and cooperate with the magnetic core component to form the first space and the second space.

[0009] Optionally, the second component also includes a fixed iron core, the core cover is fixed on the fixed iron core through the magnetic isolation ring, the fixed iron core includes a first connecting port, the first connecting port connects the second space and the damping channel, and the core cover also includes a second connecting port, the second connecting port connects the first space and the damping channel.

[0010] Optionally, the second component further includes a first accommodating chamber, the first accommodating chamber is connected to the second space, and the first space is connected to the first accommodating chamber through the overflow regulating device.

[0011] Optionally, the second component further includes a first communicating port and a second communicating port, both of which are suitable for passing the damping fluid into the first accommodating chamber, and the connecting hole connects the second communicating port and the first accommodating chamber.

[0012] Optionally, the overflow regulating device includes a one-way valve mechanism. When the damping fluid flows from the first connecting port through the connecting hole to the second connecting port, the damping fluid in the first space can pass through the one-way valve mechanism, and the first component moves relative to the second component in a direction away from the connecting hole to increase the aperture of the connecting hole.

[0013] Optionally, the second component further includes a guide rod, which passes through the first component along the first direction.

[0014] Optionally, the magnetic core assembly includes a magnetic core, which is sleeved on the guide rod and can move relative to the guide rod.

[0015] Optionally, the first component further includes a sliding bearing and a first elastic member, the magnetic core component further includes a groove, the sliding bearing is arranged in the groove and is sleeved on the guide rod, and the first elastic member is at least partially arranged in the groove and respectively abuts against the sliding bearing and the second component.

[0016] Optionally, the guide rod includes a third communication port and a stepped hole, the third communication port is suitable for connecting the first space and the stepped hole, and the one-way valve mechanism is provided in the stepped hole.

[0017] Optionally, the second component further includes a second accommodating chamber, the second accommodating chamber is connected to the first accommodating chamber through the connecting hole, and the damping fluid can flow to the second accommodating chamber through the second communicating port.

[0018] Optionally, the hydraulic damping valve further includes a throttling element, and the throttling element is arranged between the first accommodating chamber and the second accommodating chamber.

[0019] Optionally, the throttling element includes a first throttling member and a second throttling member, the connecting hole is formed between the second throttling member and the first throttling member, the second throttling member is connected to the second component, the first throttling member is connected to the first component and moves with the first component relative to the second component, and the first throttling member can at least partially block the connecting hole.

[0020] Optionally, the overflow regulating device 30 further includes a pin 32 and a second elastic member 33, wherein the second elastic member 33 and the pin 32 are both arranged on the inner side of the first throttle member 41, and the second elastic member 33 and the pin 32 both press against the first throttle member 41 from an end away from the one-way valve mechanism 31, and the lower end of the pin 32 is exposed on one side of the second accommodating chamber 25.

[0021] Optionally, the overflow regulating device 30 further includes a third elastic member 34 , which is passed through the ejector pin 32 and respectively abuts against the second component 20 and the ejector pin 32 .

[0022] In a second aspect, a shock absorber is further provided, the shock absorber comprising the hydraulic damping valve described in any one of the above embodiments.

[0023] In a third aspect, a hydraulic suspension system is further provided, the hydraulic suspension system comprising the hydraulic damping valve described in any one of the above embodiments; and / or the shock absorber described in the above embodiments.

[0024] In a fourth aspect, a vehicle is also provided, comprising the hydraulic damping valve described in any one of the above embodiments; and / or the shock absorber described in the above embodiments; and / or the hydraulic suspension system described in the above embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the following briefly introduces the drawings required for use in the description of the embodiments. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0026] Figure 1 A structural diagram of a vehicle provided according to some embodiments;

[0027] Figure 2 A structural diagram of a hydraulic suspension system provided according to some embodiments;

[0028] Figure 3 A structural diagram of a hydraulic damping valve provided according to some embodiments;

[0029] Figure 4 FIG1 is another structural diagram of a hydraulic damping valve according to some embodiments;

[0030] Figure 5 Another structural diagram of a hydraulic damping valve according to some embodiments;

[0031] Figure 6 A structural diagram of a magnetic core assembly provided according to some embodiments;

[0032] Figure 7 is a structural diagram of a second component provided according to some embodiments;

[0033] Figure 8 FIG1 is another structural diagram of a hydraulic damping valve according to some embodiments;

[0034] Figure 9 A structural diagram of a vibration absorber provided according to some embodiments.

[0035] Reference numerals:

[0036] 100, hydraulic damping valve; 10, first component; 11, main channel; 12, magnetic core component; 122, magnetic core; 123, groove; 13, sliding bearing; 14, first elastic member; 20, second component; 21, connecting hole; 22, first space; 23, second space; 24, first accommodating chamber; 241, first communication port; 25, second accommodating chamber; 251, second communication port; 26, guide rod; 261, third communication port; 262, stepped hole; 27 , damping channel; 28, core cover; 281, second connection port; 29, magnetic isolation ring; 210, fixed core; 211, first connection port; 30, overflow regulating device; 31, one-way valve mechanism; 32, ejector pin; 33, second elastic member; 34, third elastic member; 40, throttling element; 41, first throttling member; 42, second throttling member; 200, shock absorber; 201, rod chamber; 202, rodless chamber; 300, hydraulic suspension system; 400, vehicle. DETAILED DESCRIPTION

[0037] In the embodiments of the present application, the terms "first," "second," "third," "fourth," "fifth," and "sixth" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, a feature specified as "first," "second," "third," "fourth," "fifth," and "sixth" may explicitly or implicitly include one or more of the features.

[0038] In the embodiments of the present application, the terms "comprises," "comprising," or any other variations thereof are intended to encompass non-exclusive inclusion, such that a process, method, article, or apparatus comprising a series of elements includes not only those elements but also other elements not explicitly listed, or elements inherent to such process, method, article, or apparatus. In the absence of further limitations, an element defined by the phrase "comprising a ..." does not preclude the presence of other identical elements in the process, method, article, or apparatus comprising the element.

[0039] “A and / or B” includes the following three combinations: A only, B only, and a combination of A and B.

[0040] In the embodiments of the present application, "parallel", "perpendicular", and "equal" include the situations described and situations similar to the situations described, and the range of the similar situations is within an acceptable deviation range, wherein the acceptable deviation range is as determined by a person of ordinary skill in the art taking into account the measurement being discussed and the errors associated with the measurement of a specific quantity (i.e., the limitations of the measurement system). For example, "parallel" includes absolute parallelism and approximate parallelism, wherein the acceptable deviation range of approximate parallelism can be, for example, a deviation within 5°; "perpendicular" includes absolute perpendicularity and approximate perpendicularity, wherein the acceptable deviation range of approximate perpendicularity can also be, for example, a deviation within 5°. "Equal" includes absolute equality and approximate equality, wherein the acceptable deviation range of approximate equality can be, for example, that the difference between the two equals is less than or equal to 5% of either one.

[0041] See also Figures 1 to 9 The present application provides a vehicle 400, which includes a hydraulic damping valve 100 according to an embodiment of the present application; and / or a shock absorber 200 according to an embodiment of the present application; and / or a hydraulic suspension system 300 according to an embodiment of the present application. The vehicle 400 can be a fuel-powered vehicle, a pure electric vehicle, or a hybrid vehicle. The vehicle 400 also includes a body and an axle. The hydraulic suspension system 300 is connected between the body and the axle to transmit forces and torques between the body and the axle. The vibration fed back from the road surface to the axle can be attenuated by the hydraulic suspension system 300 before being transmitted to the body, allowing the vehicle 400 to travel smoothly and improving the driver's driving experience.

[0042] The hydraulic suspension system 300 allows the driver to adjust the chassis stiffness or damping based on their driving preferences or road conditions. For example, when vehicle 400 is traveling at high speed, the driver can set a higher stiffness or damping to improve controllability and prevent vehicle 400 from rolling. When vehicle 400 is traveling at low speed, the driver can set a lower stiffness or damping to better cushion road bumps and provide a more comfortable ride.

[0043] However, after the driver sets the stiffness and damping of the hydraulic suspension system 300 , when the vehicle 400 encounters a sudden change in the road surface while driving, the hydraulic suspension system 300 often cannot respond quickly, resulting in a poor user experience.

[0044] The present application provides a hydraulic suspension system 300 , which includes the hydraulic damping valve 100 according to an embodiment of the present application; and / or the shock absorber 200 according to an embodiment of the present application.

[0045] The present application provides a shock absorber 200 , which includes a hydraulic damping valve 100 according to an embodiment of the present application.

[0046] The present invention provides a hydraulic damping valve 100, comprising: a first component 10, a second component 20, and an overflow regulating device 30. The first component 10 is reciprocatable relative to the second component 20 in a first direction. The second component 20 includes a connecting hole 21 and a damping channel 27. Damping fluid is adapted to pass through the connecting hole 21 for hydraulic damping. Two end surfaces of the first component 10 along the first direction cooperate with the second component 20 to form a first space 22 and a second space 23. The damping channel 27 connects the first space 22 and the second space 23. The first component 10 includes a main channel 11, and the overflow regulating device 30 is at least partially disposed in the main channel 11. When the pressure of the damping fluid in the first space 22 exceeds a threshold, the damping fluid in the first space 22 activates the overflow regulating device 30 and flows out of the main channel 11, causing the pressure in the second space 23 to exceed the pressure in the first space 22 and driving the first component 10 to move relative to the second component 20 in the first direction, thereby changing the aperture size of the connecting hole 21.

[0047] In the hydraulic damping valve 100 according to an embodiment of the present application, the hydraulic damping valve 100 includes a first assembly 10, a second assembly 20, and an overflow adjustment device 30. The first assembly 10 is reciprocatable relative to the second assembly 20 in a first direction. The second assembly 20 includes a connecting hole 21 and a damping channel 27. Damping fluid is adapted to flow through the connecting hole 21 to perform hydraulic damping. The two end surfaces of the first assembly 10 along the first direction cooperate with the second assembly 20 to form a first space 22 and a second space 23. The damping channel 27 connects the first space 22 and the second space 23. The first assembly 10 includes a main channel 11, and the overflow adjustment device 30 is at least partially disposed in the main channel 11. When the pressure of the damping fluid in the first space 22 exceeds a threshold, the damping fluid in the first space 22 opens the one-way valve mechanism 31 and flows out of the main channel 11, causing the pressure in the second space 23 to exceed the pressure in the first space 22 and driving the first assembly 10 to move relative to the second assembly 20 in the first direction, thereby changing the aperture size of the connecting hole 21. In this way, the second component 20 is provided with a damping channel 27 that connects the first space 22 and the second space 23. The damping fluid in the first space 22 passes through the overflow regulating device 30, creating a pressure differential between the first space 22 and the second space 23. This in turn causes the first component 10 to move relative to the second component 20, achieving overflow self-regulation. At this time, the movement of the first component 10 is not affected by the fluctuations caused by the friction of the damping fluid flowing through the inner wall of the damping channel 27, making the pressure fluctuations of the damping fluid in the first space 22 and the second space 23 more stable.

[0048] Optionally, the first component 10 also includes a magnetic core component 12, and the second component 20 also includes a core cover 28 and a magnetic isolation ring 29. The magnetic isolation ring 29 and the core cover 28 are connected, and the damping channel 27 is arranged in the magnetic isolation ring 29 and the core cover 28. The magnetic isolation ring 29 and the core cover 28 are arranged outside the magnetic core component 12 and cooperate with the magnetic core component 12 to form a first space 22 and a second space 23.

[0049] Optionally, the second component 20 also includes a fixed iron core 210, and the core cover 28 is fixed to the fixed iron core 210 through a magnetic isolation ring 29. The fixed iron core 210 includes a first connecting port 211, and the first connecting port 211 connects the second space 23 and the damping channel 27. The core cover 28 also includes a second connecting port 281, and the second connecting port 281 connects the first space 22 and the damping channel.

[0050] In this way, the damping liquid in the first space 22 passes through the overflow regulating device 30, so that a pressure difference is formed between the first space 22 and the second space 23, thereby changing the relative position between the first component 10 and the second component 20, and realizing overflow self-regulation. At the same time, the damping channel 27 is arranged in the magnetic isolation ring 29 and the core cover 28, so that the damping liquid can flow freely between the first space 22 and the second space 23. It avoids the problem that the damping channel 27 is arranged on the magnetic core component 12, and the damping liquid flow rate fluctuates as the magnetic core component 12 moves. Compared with the existing technology, the pressure can not only realize the circulation of the upper and lower cavities of the magnetic core component 12, but also make the pressure fluctuation there more stable. The movement of the magnetic core component 12 is not affected by the fluctuation caused by the friction between the liquid in the damping channel 27 and the inner wall of the circulation.

[0051] In such an embodiment, the user can adjust the stiffness of the hydraulic suspension system 300 by setting the gear position of the hydraulic damping valve 100, ensuring that the vehicle 400 can cope with the selected normal road surface. When the road surface is bumpy or has other sudden changes, the hydraulic damping valve 100 of the embodiment of the present application can relieve pressure in the first space 22 through the overflow regulating device 30. A pressure difference is formed between the first space 22 and the second space 23, which drives the first component 10 to move relative to the second component 20, thereby changing the aperture of the connecting hole 21, thereby responding to sudden changes in the road surface and ensuring the user experience. When the damping fluid flow is stable, the hydraulic pressure at both ends of the one-way valve mechanism 31 along the first direction is consistent, and no pressure relief will occur.

[0052] For example, in this embodiment, the hydraulic damping valve 100's gear adjustment and damping control allows the user to set the gear (e.g., "Comfort," "Sport," "Off-Road," etc.) of the hydraulic damping valve 100 via an external control unit (e.g., an onboard central control system or a physical knob). Gear adjustment is achieved by varying the solenoid valve input current or a preset pressure threshold in the hydraulic circuit. Specifically, stiffness can be controlled in stages: each gear corresponds to a different initial opening of the connecting hole 21. For example, in "Comfort" mode, the first component 10 moves away from the connecting hole 21 relative to the second component 20, resulting in a wider opening of the connecting hole 21, allowing rapid flow of damping fluid and exhibiting low-damping suspension characteristics. In contrast, in "Sport" mode, the first component 10 moves closer to the connecting hole 21 relative to the second component 20, reducing the opening of the connecting hole 21 and significantly increasing suspension damping to suppress body roll. In other words, the user can adjust the stiffness of the hydraulic suspension system 300 according to their preferences. Users can freely switch gears based on the driving scenario. The system dynamically adjusts to offset sudden road surface changes while maintaining basic performance. For example, Off-Road mode defaults to high stiffness, but automatically reduces damping force when the wheel is airborne or touches the ground to avoid chassis rigidity impact; Comfort mode maintains low damping, but instantly increases damping force when encountering bumps to reduce vehicle body sway.

[0053] When the vehicle 400 encounters a sudden bump (such as a pothole or speed bump), the overflow regulating device 30 of the hydraulic damping valve 100 starts a rapid pressure relief process. Specifically, when the vehicle 400 encounters a sudden bump, the flow of the damping fluid increases to promote the increase in the hydraulic pressure of the damping fluid in the second space 23 and the first space 22. At this time, the valve core in the one-way valve mechanism 31 opens under the impact of the hydraulic pressure of the damping fluid in the first space 22, and the high-pressure damping fluid in the first space 22 flows into the second accommodating chamber 25 through the side hole of the guide rod 26. At this time, the pressure on one side of the second space 22 is greater than the pressure on one side of the first space 22. The pressure difference between the first space 22 and the second space 23 drives the first component 10 to move axially relative to the second component 20, and the displacement is determined by the pressure difference and the stiffness of the return spring. The relative movement of the second component 20 changes the effective flow area of the connecting hole 21 (main throttling channel). For example, when the second assembly 20 moves downward, the connection hole 21 is partially blocked, reducing the flow area and increasing the damping force. Conversely, when the second assembly 20 moves upward, the flow area expands and the damping force decreases. In this way, within milliseconds of a bumpy impact, the system rapidly increases the damping force through differential pressure-driven aperture adjustment to absorb the impact energy and prevent the hydraulic suspension system 300 from bottoming out.

[0054] In the embodiment of the present application, the shock absorber 200 can achieve overflow self-regulation through the flow of the damping fluid. When the road is bumpy and the flow of the damping fluid through the connecting hole 21 suddenly increases, the hydraulic pressure of the damping fluid increases, and part of the damping fluid can pass through the overflow regulating device 30 to generate a pressure difference. The pressure difference pushes the first component 10 to move relative to the second component 20 to change the aperture of the connecting hole 21, thereby achieving overflow self-regulation of the hydraulic damping valve 100.

[0055] In some embodiments, the damping fluid can flow through the gap between the first component 10 and the second component 20, that is, the first space 22 and the second space 23 can be connected through the gap, and the size of the gap can ensure that the hydraulic pressure of the damping fluid increases. Part of the damping fluid in the first space 22 passes through the overflow regulating device 30 to generate a pressure difference.

[0056] Optionally, the second component 20 further includes a first accommodating chamber 24, which communicates with the second space 23. The first space 22 communicates with the first accommodating chamber 24 via an overflow regulating device 30. In this manner, the damping fluid can flow through the first accommodating chamber 24 to the second space 23 and the first space 22, ensuring normal damping position adjustment of the first component 10 and the second component 20. Simultaneously, the damping fluid in the first space 22 can enter the first accommodating chamber 24 through the overflow regulating device 30 for buffering, increasing the flow path of the damping fluid and creating a pressure difference between the first space 22 and the second space 23, thereby adjusting the positions of the first component 10 and the second component 20 and achieving self-adjustment of the overflow of the hydraulic damping valve 100.

[0057] Specifically, when the damping fluid flows from the first space 22 through the overflow regulating device 30 and enters the first accommodating chamber 24, a certain pressure differential is generated between the first space 22 and the second space 23 due to the extended flow path and the buffering effect. This pressure differential is key to achieving position adjustment and overflow self-adjustment in the hydraulic damping valve 100. By adjusting the opening or flow rate of the overflow regulating device 30, the magnitude of the pressure differential can be precisely controlled, thereby achieving dynamic adjustment of the positions of the first and second assemblies 10, 20. This adjustment method not only improves the response speed of the hydraulic damping valve 100 but also enhances its ability to adapt to different operating conditions.

[0058] Optionally, the second assembly 20 further includes a first communication port 241 and a second communication port 251, both of which are adapted to pass damping fluid into the first accommodating chamber 24. The connecting hole 21 connects the second communication port 251 with the first accommodating chamber 24. In this manner, the first communication port 241 and the second communication port 251 can be respectively connected to other components of the hydraulic suspension system 300. These other components can then communicate with the first communication port 241 and the second communication port 251 via pipelines, ensuring that the damping fluid can flow between different components, thereby achieving the basic functions of the hydraulic suspension system 300.

[0059] Optionally, the overflow adjustment device 30 includes a one-way valve mechanism 31. When the damping fluid flows from the first communication port 241 through the connecting hole 21 to the second communication port 251, the damping fluid in the first space 22 can pass through the one-way valve mechanism 31, causing the first component 10 to move away from the connecting hole 21 relative to the second component 20, thereby increasing the diameter of the connecting hole 21. In this way, when the flow rate of the damping fluid increases during circulation, the damping fluid in the first space 22 can pass through the one-way valve mechanism 31 to create a pressure difference between the first space 22 and the second space 23. At this point, the hydraulic pressure in the second space 23 is greater than that in the first space 22, pushing the first component 10 away from the connecting hole 21, increasing the diameter of the connecting hole 21 to accommodate the current damping fluid flow rate. The first component 10 can be reset under the combined action of the elastic member, the magnetic member, and the balanced pressure, thereby achieving self-regulating overflow in the hydraulic damping valve 100.

[0060] In the embodiments of the present application, the specific form of the one-way valve mechanism 31 is not limited to meet different requirements. For example, the one-way valve mechanism 31 can be a one-way steel ball seal, a one-way cone valve, a one-way valve disc, etc. Its main functional principle is to achieve a one-way damping fluid flow from the upper cavity of the magnetic core 122 to the lower cavity of the second throttle member 42 during the return stroke.

[0061] Optionally, the second component 20 further includes a guide rod 26, which passes through the first component 10 along the first direction. In this way, the first component 10 can be sleeved on the guide rod 26 and slide on the guide rod 26 along the first direction, thereby ensuring the stability of the first component 10 and the second component 20.

[0062] Optionally, the magnetic core assembly 12 includes a magnetic core 122 , which is sleeved on the guide rod 26 and can move relative to the guide rod 26 .

[0063] In this way, the magnetic core assembly 12 can be controlled by electromagnetic force, and the magnetic core assembly 12 can be electrically connected to the vehicle computer system. The driver can control the gear state of the magnetic core assembly 12 by operating the relevant buttons on the vehicle computer system to adjust the stiffness or damping of the hydraulic suspension system 300.

[0064] Optionally, the first component 10 further includes a sliding bearing 13 and a first elastic member 14, and the magnetic core component 12 further includes a groove 123. The sliding bearing 13 is disposed in the groove 123 and sleeved on the guide rod 26. The first elastic member 14 is at least partially disposed in the groove 123 and abuts against the sliding bearing 13 and the second component 20, respectively. In this way, the first elastic member 14 can cooperate with the sliding bearing 13 to abut the first component 10 toward the connecting hole 21. The elastic force of the first elastic member 14 cooperates with the magnetic force of the magnetic core component 12 to stabilize the position of the first component 10 relative to the second component 20.

[0065] Optionally, the guide rod 26 includes a third communication port 261 and a stepped hole 262. The third communication port 261 is adapted to connect the first space 22 and the stepped hole 262, and the one-way valve mechanism 31 is disposed in the stepped hole 262. Thus, the one-way valve is disposed in the stepped hole 262, and the damping fluid in the first space 22 can flow into the stepped hole 262 through the third communication port 261. When the damping fluid flow rate is high, the damping fluid in the stepped hole 262 can relieve pressure in the first space 22 through the one-way valve.

[0066] In the embodiment of the present application, the guide rod 26 is designed with a third connecting port 261 and a one-way valve mechanism 31. By varying the area of the stepped hole 262 on the magnetic core assembly 12 and the area of the connecting hole 21, the flow resistance in the lower chamber of the magnetic core 122 through the stepped hole 262 on the magnetic core 122 is greater than the flow resistance in the upper chamber of the magnetic core 122 through the side hole of the guide rod 26 and the stepped hole 262 of the one-way valve mechanism 31. This causes the axial hydraulic pressure on the pressure-bearing surface of the lower end of the magnetic core 122 to be greater than the axial hydraulic pressure on the pressure-bearing surface of the upper end of the magnetic core 122, resulting in an upward resultant hydraulic force acting on the magnetic core 122 in the axial direction. This allows the hydraulic pressure acting on the magnetic core assembly 12 to vary with the flow rate during recovery, allowing the magnetic core assembly 12 to function as a relief valve body in the principle of a pilot relief valve during recovery, ensuring that the output pressure differential remains substantially stable with flow rate and achieving adjustable damping in the recovery flow path.

[0067] For example, when the vehicle 400 encounters a sudden bump (such as a pothole or speed bump), the overflow regulating device 30 of the hydraulic damping valve 100 starts a rapid pressure relief process. Specifically, when the vehicle 400 encounters a sudden bump, the flow of the damping fluid increases to promote the increase in the hydraulic pressure of the damping fluid in the second space 23 and the first space 22. At this time, the valve core in the one-way valve mechanism 31 opens under the impact of the hydraulic pressure of the damping fluid in the first space 22, and the high-pressure damping fluid in the first space 22 flows into the second accommodating chamber 25 through the side hole of the guide rod 26. At this time, the pressure on one side of the second space 22 is greater than the pressure on one side of the first space 22. The pressure difference between the first space 22 and the second space 23 drives the first component 10 to move axially relative to the second component 20, and the displacement is determined by the pressure difference and the stiffness of the return spring. The relative movement of the second component 20 changes the effective flow area of the connecting hole 21 (main throttling channel). For example, when the second assembly 20 moves downward, the connection hole 21 is partially blocked, reducing the flow area and increasing the damping force. Conversely, when the second assembly 20 moves upward, the flow area expands and the damping force decreases. This way, within milliseconds of a bumpy impact, the system rapidly increases the damping force through differential pressure-driven aperture adjustment to absorb the impact energy and prevent the suspension from bottoming out. After the impact, the return spring pushes the valve core back to its original position, and the connection hole 21 returns to its original opening, ensuring rapid suspension rebound and maintaining smooth ride quality.

[0068] Optionally, the overflow regulating device 30 further includes a pin 32 and a second elastic member 33. The second elastic member 33 and the pin 32 are both arranged on the inner side of the first throttle member 41. The second elastic member 33 and the pin 32 both press against the first throttle member 41 from the end away from the one-way valve mechanism 31. The lower end of the pin 32 is exposed on one side of the second accommodating chamber 25.

[0069] Optionally, the overflow regulating device 30 further includes a third elastic member 34, which is disposed outside the ejector pin 32 and respectively abuts the second component 20 and the ejector pin 32. In this manner, the ejector pin 32 and the second elastic member 33 can constitute a self-regulating mechanism for reverse overflow of the damping fluid. Specifically, when the damping fluid flows from the second connecting port 251 through the connecting hole 21 to the first connecting port 241, the ejector pin 32 can throttle the damping fluid. If a sudden change in the road surface causes a sudden increase in the flow of the damping fluid from the second connecting port 251 through the connecting hole 21 to the first connecting port 241, the damping fluid can dislodge the ejector pin 32, increasing the exposed diameter of the connecting hole 21 and allowing the damping fluid to circulate rapidly. After the damping fluid circulates, the ejector pin 32 can be reset by the action of the second elastic member 33.

[0070] In the embodiment of the present application, the specific forms of the first elastic member 14, the second elastic member 33 and the third elastic member 34 are not limited to meet different requirements. For example, the first elastic member 14 and the second elastic member 33 can be springs.

[0071] Optionally, the second component 20 further includes a second accommodating chamber 25, which is connected to the first accommodating chamber 24 via the connecting hole 21. The damping fluid can flow into the second accommodating chamber 25 via the second connecting port 251. In this way, the first accommodating chamber 24 and the second accommodating chamber 25 can be connected via the connecting hole 21, and the first accommodating chamber 24 is connected to an external pipeline via the first connecting port 241, and the second accommodating chamber 25 is connected to an external cavity via the second connecting port 251. Thus, the hydraulic damping valve 100 is connected to the shock absorber 200, achieving the basic function of damping vibration reduction.

[0072] Optionally, the hydraulic damping valve 100 further includes a throttling element 40, which is disposed between the first accommodating chamber 24 and the second accommodating chamber 25. In this way, the throttling element 40 can overflow the damping fluid in the first accommodating chamber 24 and the second accommodating chamber 25 to ensure a stable flow of the damping fluid.

[0073] Optionally, the throttling element 40 includes a first throttling member 41 and a second throttling member 42. The connecting hole 21 is formed between the second throttling member 42 and the first throttling member 41. The second throttling member 42 is connected to the second component 20, and the first throttling member 41 is connected to the first component 10 and moves with the first component 10 relative to the second component 20. The first throttling member 41 can at least partially block the connecting hole 21. In this way, the first throttling member 41 can move with the first component 10 to precisely control the aperture of the connecting hole 21. At the same time, the first throttling member 41 can be mounted on the second elastic member 33 and the ejector pin 32 to ensure the stable position of the second elastic member 33 and the ejector pin 32.

[0074] In the embodiments of the present application, the specific types of the first throttle member 41 and the second throttle member 42 are not limited to meet different requirements. For example, the first throttle member 41 can be a throttle valve body, and the second throttle member 42 can be a throttle valve seat. Furthermore, in the embodiments of the present application, the specific location of the connecting hole 21 is also not limited. For example, the connecting hole 21 can be formed between the throttle valve body and the throttle valve seat. In another example, the connecting hole 21 can be formed on the throttle valve seat, and the movement of the throttle valve body can at least partially obscure the connecting hole 21.

[0075] Optionally, the second elastic member 33 abuts the first throttle member 41 and the second throttle member 42, respectively. In this way, the second elastic member 33 and the ejector pin 32 cooperate to adjust the diameter of the connecting hole 21. Simultaneously, the ejector pin 32 throttles the damping fluid as it flows from the second connecting port 251 through the connecting hole 21 to the first connecting port 241. If a sudden change in the road surface causes a sudden increase in the flow of damping fluid from the second connecting port 251 through the connecting hole 21 to the first connecting port 241, the damping fluid can dislodge the ejector pin 32, increasing the exposed diameter of the connecting hole 21 and allowing the damping fluid to circulate rapidly. After the damping fluid circulates, the ejector pin 32 can be reset by the action of the second elastic member 33.

[0076] In some embodiments, the overflow regulating device 30 further includes a pin disk, which may include a plurality of pins 32 and a disk body. The lower ends of the plurality of pins 32 are aligned with the second accommodating chamber 25, and the plurality of pins 32 are connected to the disk body. In such an embodiment, the second elastic member 33 respectively abuts against the first throttle member 41 and the disk body. The plurality of pins 32 on the disk body can be inserted into the second throttle member 42, so that when the damping fluid flow rate is large, the position of the first throttle member 41 can be changed by the pin disk. Specifically, a plurality of pins 32 are designed on the pin disk, and the pins 32 can move up and down within the first throttle member 41. During the compression stroke, as the flow rate increases, the upward liquid pressure on the pins 32 increases, and the force is transmitted to the first throttle member 41 through the second elastic member 33, and finally to the magnetic core assembly 12, so that the magnetic core assembly 12 also has a speed-dependent overflow function in the compression channel, realizing adjustable damping in the compression flow channel. The guide rod 26 is directly connected to the first throttle member 41. During the recovery stroke, the damping fluid entering from the bottom of the magnetic core assembly 12 can pass through the damping channel 27 and the one-way valve mechanism 31, enter the first throttle member 41 and flow out, thereby realizing a cycle of damping fluid flow from the top of the magnetic core 122 to the second throttle member 42, and realizing the discharge of gas that may exist on the upper part of the solenoid valve along with the flow of damping fluid, thereby avoiding fluctuations during damping adjustment.

[0077] In summary, the shock absorber 200 of the embodiment of the present application realizes restoration and adjustable compression damping more simply than the existing pilot overflow structure, reduces the pilot valve plug and other parts at the bottom of the magnetic core 122, has fewer axial dimensions, lower requirements for the axial coaxiality of the components as a whole, lower processing precision, and better cost. Specifically, the first component 10 can be a piston valve system, and the second component 20 can be a solenoid valve part. The ejector pin 32 is installed in the ejector pin hole, and the ejector pin 32 can move up and down in the first throttle member 41. A second elastic member 33 is provided on the ejector pin 32, and the upper end of the second elastic member 33 is in contact with the first throttle member 41. The first throttle member 41 cooperates with the second throttle member 42 in the circumferential direction, and the first throttle member 41 can move up and down along the second throttle member 42 to achieve adjustment of the flow area of the connecting hole 21. The magnetic core 122 is provided with a sliding bearing 13, which can move axially up and down along the guide rod 26. The sliding bearing 13 is provided with a first elastic member 14. Under the action of the first elastic member 14, the lower end of the magnetic core 122 is kept in contact with the throttling element 40, transmitting force to each other. The second component 20 is provided with a damping channel 27 axially along the magnetic core 122. The second component 20 also includes a first connecting port 211 and a second connecting port 281 perpendicular to the axial direction of the magnetic core 122. The damping channel 27 can be in the form of a straight-through hole or a stepped damping hole. The guide rod 26 is provided on the first throttling element 41, with its lower end in contact with the first throttling element 41 and its upper end fixed to the core cover 28. A third connecting port 261 is provided at the upper end of the guide rod 26, and a one-way valve mechanism 31 is provided axially within the guide rod 26 to allow the damping fluid in the upper cavity of the magnetic core 122 to flow into the first throttling element 41 during the return stroke.

[0078] During the return stroke, specifically, damping fluid flows from the rod chamber 201 of the shock absorber 200 through the first communication port 241. One path flows through the connecting hole 21 between the first throttle member 41 and the second throttle member 42, and then flows out through the piston valve system. Another path flows through the damping passage 27, the third communication port 261 on the guide rod 26, the one-way valve mechanism 31, and the flow hole of the second throttle member 42, before flowing into the rodless chamber 202 of the shock absorber 200 through the second communication port 251.

[0079] During the return stroke, when the solenoid valve input current increases, the downward electromagnetic force on the magnetic core assembly 12 increases. The resulting force on the magnetic core assembly 12 is downward, causing the magnetic core 122 to push the first throttle member 41 downward along the second throttle member 42, resulting in a smaller cross-sectional area of the connecting hole 21 in the second throttle member 42 and a larger damping adjustment. At this time, as the throttle element 40 moves downward, the spring is compressed, transferring force to the ejector pin 32. The ejector pin 32 has no downward travel, and the force acts on the second throttle member 42, having no effect on the adjustment.

[0080] During the recovery stroke, when the input current of the solenoid valve becomes smaller, the downward electromagnetic force received by the core assembly 12 decreases, the resultant force received by the core assembly 12 is upward, the core assembly 12 moves upward, the core 122 moves upward, and the first throttle member 41 moves upward with the core 122 under the action of the second elastic member 33, causing the cross-sectional area of the connecting hole 21 to become larger and the damping adjustment to become smaller.

[0081] When the one-way valve mechanism 31 releases pressure, the pressure in the first space 22 becomes lower than the pressure in the second space 23, and the resultant axial hydraulic force on the magnetic core 122 is directed upward. Specifically, the axial hydraulic pressure on the pressure-bearing surface at the lower end of the magnetic core 122 is greater than the axial hydraulic pressure on the pressure-bearing surface at the upper end of the magnetic core 122. This results in the resultant axial hydraulic force on the magnetic core 122 being directed upward. Damping fluid flowing into the upper cavity of the magnetic core 122 can be promptly discharged along the one-way valve mechanism 31 channel of the guide rod 26, and the pressure in the upper cavity of the magnetic core 122 becomes a low-pressure zone. The resultant hydraulic force on the upper and lower pressure-bearing surfaces of the magnetic core 122 is directed upward.

[0082] During the return stroke, when the input flow rate entering through the side hole of the solenoid valve housing increases, the combined hydraulic force on the magnetic core 122 increases, driving the magnetic core 122 upward. Under the action of the second elastic member 33, the first throttle member 41 moves upward along with the magnetic core 122, causing the cross-sectional area of the connecting hole 21 to increase, thereby keeping the output differential pressure basically stable with changes in flow rate. When the input flow rate entering through the side hole of the solenoid valve housing decreases, the combined hydraulic force on the magnetic core 122 decreases, driving the magnetic core 122 downward. The magnetic core 122 pushes the first throttle member 41 downward along the second throttle member 42, causing the cross-sectional area of the connecting hole 21 to decrease, thereby keeping the output differential pressure basically stable with changes in flow rate.

[0083] During the compression stroke, damping fluid flows from the rodless chamber 202 of the shock absorber 200, passes through the transverse connecting hole 21 of the relief valve body, and flows out through the transverse hole in the solenoid valve housing. At this point, upward flow from the first throttle member 41 is blocked by the ejector pin 32 and the one-way valve mechanism 31 on the guide rod 26, allowing the damping fluid to flow only through the transverse connecting hole 21. The damping fluid then flows from the first communication port 241 into the rod chamber 201 of the shock absorber 200.

[0084] During the compression stroke, when the input current of the solenoid valve increases, the downward electromagnetic force received by the magnetic core assembly 12 increases, the resultant force received by the magnetic core assembly 12 is downward, the magnetic core assembly 12 moves downward, and the magnetic core 122 pushes the first throttle member 41 to move downward along the second throttle member 42, causing the cross-sectional area of the connecting hole 21 to become smaller and the damping adjustment to become larger.

[0085] During the compression stroke, when the solenoid valve input current decreases, the downward electromagnetic force on the magnetic core assembly 12 decreases, and the resultant force on the magnetic core assembly 12 is upward, causing the magnetic core assembly 12 to move upward. The magnetic core 122 moves upward, and the first throttle member 41, under the action of the second elastic member 33, moves upward along with the magnetic core 122, causing the cross-sectional area of the connecting hole 21 to increase and the damping adjustment to decrease.

[0086] During the compression stroke, when the input flow rate increases, the hydraulic pressure applied to the ejector pin 32 increases, which is transmitted to the magnetic core 122 through the second elastic member 33 and the first throttle member 41. The magnetic core 122 is subjected to a combined upward force. The magnetic core 122 moves upward, and the first throttle member 41 moves upward along with the magnetic core 122 under the action of the second elastic member 33, causing the cross-sectional area of the connecting hole 21 to increase. This keeps the output differential pressure generally stable with changes in flow rate. When the input flow rate decreases, the hydraulic pressure applied to the ejector pin 32 decreases, which is transmitted to the magnetic core 122 through the second elastic member 33 and the first throttle member 41. The magnetic core 122 is subjected to a combined upward force downward, driving the magnetic core 122 downward. The magnetic core 122 pushes the first throttle member 41 downward along the second throttle member 42, causing the cross-sectional area of the connecting hole 21 to decrease. This keeps the output differential pressure generally stable with changes in flow rate.

[0087] In the embodiment of the present application, the upper end of the guide rod 26 is fixed to the core cover 28, and the lower end is positioned with the first throttle member 41, and the lower end of the first throttle member 41 is positioned on the second throttle member 42. During operation, the guide rod 26 and the second throttle member 42 are both fixed and do not move relative to each other. The flow between the two can be connected through the one-way valve mechanism 31 in the guide rod 26. During the recovery stroke, the damping fluid in the upper cavity of the magnetic core 122 can be discharged to the lower part of the first throttle member 41 and then discharged out of the valve. The gas remaining in the upper part of the magnetic core 122 will also be discharged along the flow of the damping fluid, realizing the exhaust function of the upper part of the solenoid valve, avoiding abnormalities such as output damping jitter and instability caused by residual gas in the solenoid valve or unclean exhaust during operation.

[0088] Through the above principle and structural design, a damping regulating valve with a new principle can be realized, and damping adjustment can be achieved in both recovery and compression. The damping adjustment bandwidth of recovery and compression can be adjusted through the flow area of the connecting hole 21 to achieve damping adjustment with a large bandwidth.

[0089] In this embodiment, a throttling channel (i.e., connecting hole 21) is designed. As the first throttling member 41 moves axially, the amount of coverage on the throttling channel changes, and the flow area also changes accordingly. The principle is to control the change in flow area through the relative movement between the two components. Therefore, it can also be expanded to design a throttling channel that changes with height on the side wall of the throttling element 40, and a constant flow channel on the side wall of the second throttling member 42. This also achieves damping adjustment.

[0090] In the embodiment of the present application, the hydraulic damping valve 100 is composed of a solenoid valve part and a piston valve assembly, and the solenoid valve housing and the piston valve assembly are connected without relative movement. The function of the solenoid valve housing is to fix and encapsulate the solenoid valve body. The components composed of the core cover 28, the magnetic isolation ring 29, the fixed iron core 210 and the spiral tube with coil assembly jointly provide a magnetic field under different currents, and the magnetic core 122 provides different electromagnetic forces under the action of the magnetic field. The magnetic core 122 and the first throttle member 41 maintain contact under the action of the first elastic member 14 and the second elastic member 33 (both in a compressed state at all times) and transmit force to each other. Under the action of different forces on the effective area, the pressure difference between the upper and lower chambers of the magnetic core 122, the combined force of this part of the liquid pressure and the electromagnetic force and spring force mentioned above, determines the relative position of the second throttle member 42 and the first throttle member 41.

[0091] Unlike the existing technology, the liquid flow channels in the upper and lower cavities of the magnetic core 122 are arranged on a component consisting of the core cover 28, the magnetic isolation ring 29, and the fixed iron core 210 (existing product technology is generally arranged on the magnetic core 122). The magnetic core 122 and the first throttle member 41 move axially up and down along the guide rod 26 under the combined action of electromagnetic force, elastic member and hydraulic pressure. The movement is achieved by the sliding bearing 13 made of low-friction material. This part constitutes the current-adjustable motion mechanism of the solenoid valve. The second throttle member 42 provides axial support for the guide rod 26. The copper sleeve is made of a soft metal material with low hardness. Its purpose is to absorb axial assembly tolerances and synchronously seal the different pressure areas inside and outside the guide rod. The one-way bushing, one-way valve spring and steel ball constitute the one-way valve mechanism 31 inside the guide rod 26. The one-way valve mechanism 31 plays a key role in restoring the flow direction of the solenoid valve. The throttle valve seat is also provided with a mechanism of a ejector pin 32 and an ejector spring. During the compression process, the pressure difference between the upper and lower parts of the ejector pin 32 causes different forces (larger at the bottom and smaller at the top) to push the ejector pin 32 upward, further promoting the throttle valve stroke overflow effect. The sealing ring is provided to prevent the risk of short circuit caused by liquid entering the interior of the coil. The valve body support seat is located on the piston support seat to provide support for the fixed iron core 210. The piston valve mounting seat has two functions. One is to fix the main body of the entire solenoid valve through a threaded locking connection with the piston rod housing. The other function is to provide a mounting structure for the piston valve assembly. The piston valve and the solenoid valve are a series structure, and are matched together to provide the solenoid valve assembly with PQ flow characteristics suitable for the entire vehicle.

[0092] The damping channel 27 of the upper and lower cavities of the balanced magnetic core 122 in the embodiment of the present application is set on the component composed of the core cover 28, the magnetic isolation ring 29, and the fixed iron core 210. Compared with the existing technical pressure, it can not only realize the circulation of the upper and lower cavities of the magnetic core 122, but also make the pressure fluctuation there more stable. The movement of the magnetic core 122 is not affected by the fluctuation caused by the friction between the liquid in the channel and the inner wall of the circulation. Through the above principle and structural design, a damping regulating valve with a completely new principle can be realized. Both restoration and compression can achieve damping adjustment, and the damping adjustment bandwidth of restoration and compression can be adjusted by the side wall flow area on the throttle valve body to achieve damping adjustment with a large bandwidth.

[0093] In the embodiment of the present application, a one-way structure is designed in the guide rod 26, and the specific implementation form can be said to be various, which can be a one-way steel ball sealing form, a one-way cone valve, a one-way valve plate, etc. Its main functional principle is to achieve a one-way oil flow from the upper cavity of the magnetic core to the lower cavity of the throttle valve body when the recovery stroke is realized. The specific implementation form is not limited here.

[0094] In the embodiment of the present application, the throttle element 40 is designed with a throttle channel. As the throttle sleeve moves axially, the amount of coverage on the throttle channel changes, and the flow area also changes accordingly. The principle is to control the change in flow area through the relative movement between the two components. Therefore, it can also be expanded to design a throttle channel that changes with height on the side wall of the throttle sleeve, and a constant flow channel on the side wall of the throttle body. This also achieves damping adjustment.

[0095] In the embodiment of the present application, the damping channel 27 connecting the upper and lower cavities of the magnetic core 122 and balancing the pressure is set on the component composed of the core cover 28, the magnetic isolation ring 29, and the fixed iron core 210 to achieve the connection between the upper and lower cavities. Not only that, the damping channel 27 can also be set on other components that can connect the upper and lower cavities, such as the side wall of the guide rod 26, which is not limited here.

[0096] In the description of the embodiments of the present application, specific features, structures, materials or characteristics may be combined in an appropriate manner in any one or more embodiments or examples.

[0097] The above are only specific embodiments of the present application, but the scope of protection of this application is not limited thereto. Any changes or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in this application should be included in the scope of protection of this application. Therefore, the scope of protection of this application should be based on the scope of protection of the claims.

Claims

1. A hydraulic damping valve (100), characterized in that: include: A first component (10), a second component (20) and an overflow regulating device (30), wherein the first component (10) can reciprocate relative to the second component (20) along a first direction, the second component (20) comprises a connecting hole (21) and a damping channel (27), the damping fluid is suitable for passing through the connecting hole (21) to perform hydraulic damping, two end surfaces of the first component (10) along the first direction cooperate with the second component (20) to form a first space (22) and a second space (23), the damping channel (27) communicates the first space (22) and the second space (23), the first component (10) comprises a main channel (11), and the overflow regulating device (30) is at least partially provided in the main channel (11); When the pressure of the damping fluid in the first space (22) is greater than a threshold value, the damping fluid in the first space (22) opens the overflow regulating device (30) and flows out from the main channel (11), so that the pressure of the second space (23) is greater than the pressure of the first space (22) and pushes the first component (10) to move relative to the second component (20) along the first direction, thereby changing the aperture size of the connecting hole (21).

2. The hydraulic damping valve (100) according to claim 1, characterized in that The first component (10) further includes a magnetic core component (12), and the second component (20) further includes a core cover (28) and a magnetic isolation ring (29), wherein the magnetic isolation ring (29) and the core cover (28) are connected, and the damping channel (27) is arranged in the magnetic isolation ring (29) and the core cover (28), and the magnetic isolation ring (29) and the core cover (28) are sleeved outside the magnetic core component (12) and cooperate with the magnetic core component (12) to form the first space (22) and the second space (23).

3. The hydraulic damping valve (100) according to claim 2, characterized in that: The second component (20) further includes a fixed iron core (210), the iron core cover (28) is fixed to the fixed iron core (210) through the magnetic isolation ring (29), the fixed iron core (210) includes a first connection port (211), the first connection port (211) is connected to the second space (23) and the damping channel (27), and the iron core cover (28) further includes a second connection port (281), the second connection port (281) is connected to the first space (22) and the damping channel.

4. The hydraulic damping valve (100) according to claim 3, characterized in that The second component (20) further includes a first accommodating chamber (24), the first accommodating chamber (24) being connected to the second space (23), and the first space (22) being connected to the first accommodating chamber (24) via the overflow regulating device (30).

5. The hydraulic damping valve (100) according to claim 4, characterized in that The second component (20) further comprises a first communicating port (241) and a second communicating port (251), wherein the first communicating port (241) and the second communicating port (251) are both suitable for passing the damping fluid into the first accommodating chamber (24), and the connecting hole (21) connects the second communicating port (251) and the first accommodating chamber (24).

6. The hydraulic damping valve (100) according to claim 5, characterized in that The overflow regulating device (30) includes a one-way valve mechanism (31). When the damping fluid flows from the first communication port (241) through the connection hole (21) to the second communication port (251), the damping fluid in the first space (22) can pass through the one-way valve mechanism (31), and the first component (10) moves relative to the second component (20) in a direction away from the connection hole (21) to increase the aperture of the connection hole (21).

7. The hydraulic damping valve (100) according to claim 6, characterized in that The second component (20) further includes a guide rod (26), wherein the guide rod (26) penetrates the first component (10) along the first direction.

8. The hydraulic damping valve (100) according to claim 7, characterized in that The magnetic core assembly (12) comprises a magnetic core (122), wherein the magnetic core (122) is sleeved on the guide rod (26) and is movable relative to the guide rod (26).

9. The hydraulic damping valve (100) according to claim 8, characterized in that The first component (10) further includes a sliding bearing (13) and a first elastic member (14); the magnetic core component (12) further includes a groove (123); the sliding bearing (13) is arranged in the groove (123) and sleeved on the guide rod (26); the first elastic member (14) is at least partially arranged in the groove (123) and respectively abuts against the sliding bearing (13) and the second component (20).

10. The hydraulic damping valve (100) according to claim 9, characterized in that The guide rod (26) includes a third communication port (261) and a stepped hole (262). The third communication port (261) is suitable for connecting the first space (22) and the stepped hole (262). The one-way valve mechanism (31) is provided in the stepped hole (262).

11. The hydraulic damping valve (100) according to claim 6, characterized in that The second component (20) further includes a second accommodating chamber (25), the second accommodating chamber (25) being connected to the first accommodating chamber (24) through the connecting hole (21), and the damping fluid can flow to the second accommodating chamber (25) through the second communicating port (251).

12. The hydraulic damping valve (100) according to claim 11, characterized in that The hydraulic damping valve (100) further comprises a throttling element (40), wherein the throttling element (40) is arranged between the first accommodating chamber (24) and the second accommodating chamber (25).

13. The hydraulic damping valve (100) according to claim 12, characterized in that The throttling element (40) includes a first throttling piece (41) and a second throttling piece (42), the connecting hole (21) is formed between the second throttling piece (42) and the first throttling piece (41), the second throttling piece (42) is connected to the second component (20), the first throttling piece (41) is connected to the first component (10) and moves with the first component (10) relative to the second component (20), and the first throttling piece (41) is capable of at least partially blocking the connecting hole (21).

14. The hydraulic damping valve (100) according to claim 3, characterized in that The overflow regulating device (30) further comprises a pin (32) and a second elastic member (33), wherein the second elastic member (33) and the pin (32) are both arranged on the inner side of the first throttling member (41), and the second elastic member (33) and the pin (32) both abut against the first throttling member (41) from an end away from the one-way valve mechanism (31), and the lower end of the pin (32) is exposed on one side of the second accommodating chamber (25).

15. The hydraulic damping valve (100) according to claim 14, characterized in that The overflow regulating device (30) further includes a third elastic member (34), which is arranged outside the ejector pin (32) and respectively abuts against the second component (20) and the ejector pin (32).

16. A vibration absorber (200), characterized in that: The hydraulic damping valve (100) comprises the hydraulic damping valve (100) according to any one of claims 1 to 15.

17. A hydraulic suspension system (300), characterized in that: It comprises the hydraulic damping valve (100) according to any one of claims 1 to 15; and / or the shock absorber (200) according to claim 16.

18. A vehicle (400), characterized in that The invention comprises the hydraulic damping valve (100) according to any one of claims 1 to 15; and / or the shock absorber (200) according to claim 16; and / or the hydraulic suspension system (300) according to claim 17.

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