Active hydraulic suspension system and vehicle

Abstract

This utility model discloses an active hydraulic suspension system and vehicle, comprising: a shock absorber body, including a cylinder and a rod piston slidably disposed within the cylinder, the rod piston dividing the cylinder interior into a rod chamber and a rodless chamber; an internal oil passage, one end of which is connected to the rodless chamber via a first one-way damping valve assembly, and the other end of which is connected to the rod chamber via a second one-way damping valve assembly, allowing oil in the rodless and rod chambers to flow between them along the internal oil passage; the first and second one-way damping valve assemblies providing damping force to the oil flowing out of the rodless and rod chambers; and an external oil passage, the first end of which is connected to the outlet end of the first one-way damping valve assembly, and the second end of which is connected to the outlet end of the second one-way damping valve assembly, and equipped with a pump assembly for providing power to the oil flowing out of the rodless and / or rod chambers. This utility model can reduce the passive influence of the external oil passage's piping quality on damping control, ensuring the accuracy of damping adjustment.

Description

Technical Field

[0001] This utility model relates to the field of vehicle suspension technology, specifically to an active hydraulic suspension system and a vehicle. Background Technology

[0002] The suspension system of a car can suppress spring vibration and reduce road impact, making it an essential structure for improving ride comfort. Currently, passive mechanical suspension is commonly used in automobiles, which typically only includes springs and damping shock absorbers, and cannot simultaneously achieve both comfort and handling stability.

[0003] To address this, the relevant technology employs an active hydraulic suspension system. This system controls the damping magnitude through the opening of solenoid valves and utilizes external oil circuits and hydraulic pumps to actively adjust the shock absorber stiffness, thus improving ride comfort and stability to some extent. However, this technology typically connects the external oil circuit directly to the internal oil circuit used for damping control. During damping control, the material of the external oil circuit lines can easily affect the damping control process. If the external oil circuit lines are too soft, damping control lag may occur, affecting the accuracy of damping adjustment; if the external oil circuit lines are too hard, it will affect the absorption capacity of hydraulic pulses, reducing NVH (Noise, Vibration, Harshness) performance. Utility Model Content

[0004] In view of the above problems, this utility model provides an active hydraulic suspension system and vehicle that can reduce the passive influence of the quality of the external oil circuit on damping control and ensure the accuracy of damping adjustment.

[0005] According to one aspect of the present invention, an active hydraulic suspension system is provided, comprising: a shock absorber body including a cylinder and a rod piston slidably disposed inside the cylinder, the rod piston dividing the cylinder interior into a rod chamber and a rodless chamber; an internal oil passage, one end of which is connected to the rodless chamber via a first one-way damping valve assembly, the first one-way damping valve assembly being used to provide damping force to the oil flowing out of the rodless chamber; the other end of which is connected to the rod chamber via a second one-way damping valve assembly, the second one-way damping valve assembly being used to provide damping force to the oil flowing out of the rod chamber; wherein the oil in the rodless chamber and the rod chamber can flow to each other along the internal oil passage; and an external oil passage, the first end of which is connected to the outlet end of the first one-way damping valve assembly, the second end of which is connected to the outlet end of the second one-way damping valve assembly, and a pump assembly configured to provide power to the oil flowing out of the rodless chamber and / or the rod chamber.

[0006] In an exemplary embodiment of this utility model, the internal oil circuit includes a first solenoid valve and a first check valve connected in sequence along the first oil flow direction, and a second solenoid valve and a second check valve connected in sequence along the second oil flow direction, wherein the second oil flow direction is opposite to the first oil flow direction; wherein the first solenoid valve and the second check valve are connected in parallel to form a first one-way damping valve assembly, and the second solenoid valve and the first check valve are connected in parallel to form a second one-way damping valve assembly.

[0007] In an exemplary embodiment of this utility model, the active hydraulic suspension system has a passive compression mode and a passive recovery mode: in the passive compression mode, the pump assembly is turned off, the rod piston moves to the rodless chamber, and the oil flowing out of the rodless chamber flows into the rod chamber in sequence through the first solenoid valve and the first check valve along the first oil flow direction; in the passive recovery mode, the pump assembly is turned off, the rod piston moves to the rod chamber, and the oil flowing out of the rod chamber flows into the rodless chamber in sequence through the second solenoid valve and the second check valve along the second oil flow direction.

[0008] In an exemplary embodiment of the present invention, when the pump assembly is configured to provide power to the oil flowing out of the rodless chamber, the active hydraulic suspension system also has an active compression mode: in the active compression mode, the pump assembly is started, and at least a portion of the oil flowing out of the rodless chamber flows into the rod chamber in sequence along the first oil flow direction through the first solenoid valve, the pump assembly and the first check valve, causing the rod piston to move towards the rodless chamber.

[0009] In an exemplary embodiment of this utility model, the parallel branch where the first check valve is located is further provided with a third check valve, and the second end of the external oil circuit is connected between the first check valve and the third check valve; wherein, the third check valve is located at the inlet end of the first check valve, and the conduction direction is the same as that of the first check valve.

[0010] In an exemplary embodiment of the present invention, when the pump assembly is configured to provide power to the oil flowing out of the rod chamber, the active hydraulic suspension system also has an active lifting mode: in the active lifting mode, the pump assembly is started, and at least a portion of the oil flowing out of the rod chamber flows into the rodless chamber in sequence through the second solenoid valve, the pump assembly and the second check valve along the second oil flow direction, causing the rod piston to move toward the rod chamber.

[0011] In an exemplary embodiment of the present invention, the parallel branch where the second check valve is located is further provided with a fourth check valve, and the first end of the external oil circuit is connected between the second check valve and the fourth check valve; wherein, the fourth check valve is located at the inlet end of the second check valve, and the conduction direction is the same as that of the second check valve.

[0012] In an exemplary embodiment of the present invention, the internal oil circuit is further equipped with an accumulator, which is located between the first one-way damping valve assembly and the second one-way damping valve assembly.

[0013] In an exemplary embodiment of the present invention, the pump assembly is a bidirectional oil pump and is configured to provide power to the oil flowing out of the rodless chamber when rotating forward and to provide power to the oil flowing out of the rod chamber when rotating in reverse.

[0014] According to a second aspect of the present invention, a vehicle is provided, including the above-described active hydraulic suspension system.

[0015] This invention connects the inlet / outlet ports of the external oil circuit (i.e., the first and second ends) in parallel to the outlet end of the one-way damping valve assembly of the internal oil circuit. This allows the oil flowing out of the rod chamber or rodless chamber to be damped by the one-way damping valve assembly before entering the external oil circuit. This reduces the passive influence of the quality of the external oil circuit pipeline on the damping control, achieves independent control of the damping adjustment, and ensures the accuracy of the damping adjustment.

[0016] The above description is merely an overview of the technical solutions of the present utility model embodiments. In order to better understand the technical means of the present utility model embodiments and to implement them in accordance with the contents of the specification, and to make the above and other objects, features and advantages of the present utility model embodiments more obvious and understandable, specific embodiments of the present utility model are described below. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0018] Figure 1 A connection diagram of the active hydraulic suspension system of this embodiment is shown; Figure 2 This diagram illustrates the state of the active hydraulic suspension system in passive compression mode according to this embodiment. Figure 3 This diagram illustrates the state of the active hydraulic suspension system in passive recovery mode according to this embodiment. Figure 4 This diagram illustrates the state of the active hydraulic suspension system in active compression mode according to this embodiment. Figure 5 This diagram illustrates the active hydraulic suspension system in active lifting mode according to this embodiment.

[0019] Explanation of icon numbers: 1-Shock absorber body, 11-Hydraulic cylinder, 111-Rod chamber, 112-Rodless chamber, 12-Rod piston, 2-Internal oil circuit, 21-First one-way damping valve assembly, 211-First solenoid valve, 212-Second one-way valve, 213-Fourth one-way valve, 22-Second one-way damping valve assembly, 221-Second solenoid valve, 222-First one-way valve, 223-Third one-way valve, 23-Accumulator 3-External oil passage, 31-First end, 32-Second end, 33-Pump assembly.

[0020] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0021] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the examples set forth herein; rather, these embodiments are provided to make the present invention more comprehensive and complete, and to fully convey the concept of the exemplary embodiments to those skilled in the art.

[0022] Furthermore, the described features, structures, or characteristics can be combined in any suitable manner in one or more embodiments. In the following description, numerous specific details are provided to give a full understanding of embodiments of the present invention. However, those skilled in the art will recognize that the technical solutions of the present invention can be practiced without one or more of the specific details, or other methods, components, vehicles, steps, etc., may be employed. In other instances, well-known methods, vehicles, implementations, or operations are not shown or described in detail to avoid obscuring various aspects of the present invention.

[0023] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that the technical features involved in the various embodiments of the present invention described below can be combined with each other as long as they do not conflict with each other. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0024] Furthermore, the orientations or positional relationships indicated by terms such as "front," "rear," "left," "right," "up," and "down" in the embodiments of this utility model are based on the orientations or positional relationships shown in the accompanying drawings; the terms "inner" and "outer" mentioned in the embodiments of this application are defined based on the outline of the corresponding component. It is understood that the above-mentioned terms indicating orientations or positional relationships are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the vehicle or component referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0025] like Figure 1As shown, this embodiment provides an active hydraulic suspension system, including a shock absorber body 1, an internal oil circuit 2, and an external oil circuit 3. The shock absorber body 1 includes a cylinder 11 with an internal chamber and a rod piston 12 slidably disposed within the chamber of the cylinder 11. The rod piston 12 divides the internal chamber of the cylinder 11 into a rod chamber 111 and a rodless chamber 112. The rod end of the rod piston 12 can extend out of the cylinder 11 from the end of the rod chamber 111 and connect to the suspension arm of the vehicle body or vehicle to perform external work. One end of the internal oil circuit 2 is connected to the rodless chamber 112 through a first one-way damping valve assembly 21. The first one-way damping valve assembly 21 is used to control the rodless chamber 112. The oil flowing out of the internal oil passage 2 provides damping force; the other end of the internal oil passage 2 is connected to the rod chamber 111 through the second one-way damping valve assembly 22, which is used to provide damping force to the oil flowing out of the rod chamber 111; wherein, the oil in the rodless chamber 112 and the rod chamber 111 can flow to each other along the internal oil passage 2; the first end 31 of the external oil passage 3 is connected to the outlet end of the first one-way damping valve assembly 21, the second end 32 of the external oil passage 3 is connected to the outlet end of the second one-way damping valve assembly 22, and is equipped with a pump assembly 33 for providing power to the oil flowing out of the rodless chamber 112 and / or the rod chamber 111, the pump assembly 33 being preferably a hydraulic pump.

[0026] Thus, as the rod piston 12 moves, the oil can flow out of the rodless chamber 112 along the first oil flow direction and flow into the rod chamber 111 through the internal oil passage 2, or flow out of the rod chamber 111 along the second oil flow direction and flow into the rodless chamber 112 through the internal oil passage 2. Simultaneously, under the action of the pump assembly 33, the oil can flow out of the rodless chamber 112 along the first oil flow direction and flow into the rod chamber 111 through the internal oil passage 2 and the external oil passage 3, or flow out of the rod chamber 111 along the second oil flow direction. The oil flows out through the internal oil passage 2 and the external oil passage 3 into the rodless chamber 112. Since the inlet / outlet ports of the external oil passage 3, namely the first end 31 and the second end 32, are connected to the outlet end of the one-way damping valve assembly of the internal oil passage 2, the oil flowing out of the rodless chamber 112 or the rod chamber 111 has been damped by the one-way damping valve assembly before entering the external oil passage 3. This reduces the passive influence of the pipeline quality of the external oil passage 3 on the damping control, realizes independent control of damping adjustment, and ensures the accuracy of damping adjustment.

[0027] In some embodiments, such as Figure 1As shown, the internal oil circuit 2 includes a first solenoid valve 211 and a first check valve 222 connected in sequence along the first oil flow direction, and a second solenoid valve 221 and a second check valve 212 connected in sequence along the second oil flow direction, the second oil flow direction being opposite to the first oil flow direction; wherein, the first solenoid valve 211 and the second check valve 212 are connected in parallel to form a first one-way damping valve assembly 21, and the second solenoid valve 221 and the first check valve 222 are connected in parallel to form a second one-way damping valve assembly 22. In this way, when the oil flows in the first oil flow direction, it can only pass through the parallel branch where the first solenoid valve 211 is located at the first one-way damping valve assembly 21. The first solenoid valve 211 can dampen the oil. When the oil flows through the second one-way damping valve assembly 22, it passes through the parallel branch where the first one-way valve 222 is located, and the second solenoid valve 221 does not have a damping effect. When the oil flows in the second oil flow direction, it can only pass through the parallel branch where the second solenoid valve 221 is located at the second one-way damping valve assembly 22. The second solenoid valve 221 can dampen the oil. When the oil flows through the first one-way damping valve assembly 21, it passes through the parallel branch where the second one-way valve 212 is located, and the first solenoid valve 211 does not have a damping effect. Through the above settings, one-way damping control of the internal oil circuit 2 is realized, and the independent control of damping adjustment can be ensured by controlling the opening degree of the first solenoid valve 211 / second solenoid valve 221, thereby improving the accuracy of damping adjustment.

[0028] The active hydraulic suspension system provided in the above embodiments can select a suitable working mode according to the needs of different working conditions, thereby improving the comfort and handling stability of the vehicle.

[0029] For example, an active hydraulic suspension system has a passive compression mode and a passive recovery mode, wherein, Figure 2 This is a schematic diagram of the active hydraulic suspension system in passive compression mode. Figure 3 This is a schematic diagram of the active hydraulic suspension system in passive recovery mode; the arrows in the diagram indicate the direction of movement of the rod piston 12 and the direction of oil flow.

[0030] Specifically, such as Figure 2 As shown, in the passive compression mode, the pump assembly 33 is closed, and the rod end of the rod piston 12 is subjected to a compressive force and moves towards the rodless chamber 112. At this time, the oil in the rodless chamber 112 is forced out by the rod piston 12. The oil flowing out of the rodless chamber 112 flows into the rod chamber 111 in sequence through the first solenoid valve 211 and the first check valve 222 along the first oil flow direction. The damping effect of the first solenoid valve 211 can reduce the tendency of the rod piston 12 to move towards the rodless chamber 112, thereby reducing the vibration between the vehicle body and the suspension arm.

[0031] like Figure 3As shown, in passive recovery mode, pump assembly 33 is closed, and the rod end of rod piston 12 is subjected to tensile force and moves toward rod chamber 111. At this time, the oil in rod chamber 111 is forced out by rod piston 12. The oil flowing out of rod chamber 111 flows into rodless chamber 112 along the second oil flow direction through second solenoid valve 221 and second check valve 212. The damping effect of second solenoid valve 221 can reduce the tendency of rod piston 12 to move toward rod chamber 111, thereby reducing the vibration between the vehicle body and suspension control arm.

[0032] In some embodiments, when the pump assembly 33 is configured to power the oil flowing out of the rodless chamber 112, the active hydraulic suspension system also has an active compression mode. Figure 4 This is a schematic diagram of the active hydraulic suspension system in active compression mode. The arrows in the diagram indicate the direction of movement of the rod piston 12 and the direction of oil flow. The pump assembly 33 shown in the diagram can be a one-way oil pump that pumps from the first end 31 to the second end 32.

[0033] like Figure 4 As shown, in active compression mode, pump assembly 33 starts and rotates clockwise as shown in the figure, which can draw out the oil in rodless chamber 112 and pump it into rod chamber 111. At this time, at least part of the oil flowing out of rodless chamber 112 flows into rod chamber 111 in sequence through first solenoid valve 211, pump assembly 33 and first check valve 222 along the first oil flow direction, causing rod piston 12 to move towards rodless chamber 112, realizing active adjustment of vehicle body posture. At the same time, when the oil flows along the first oil flow direction, the damping effect of first solenoid valve 211 can reduce the tendency of rod piston 12 to move towards rodless chamber 112, thereby reducing the vibration between vehicle body and suspension arms.

[0034] In some embodiments, such as Figure 1 and Figure 4 As shown, the parallel branch where the first check valve 222 is located is also equipped with a third check valve 223. The second end 32 of the external oil circuit 3 is connected between the first check valve 222 and the third check valve 223. The third check valve 223 is located at the inlet end of the first check valve 222, and its conduction direction is the same as that of the first check valve 222. The oil moving along the first oil flow direction can flow into the rod chamber 111 through the first solenoid valve 211, the third check valve 223, and the first check valve 222. By setting the third check valve 223, the direction of the oil flowing out of the second end 32 in the second one-way damping valve assembly 22 can be restricted in the active compression mode, so as to avoid interference between the oil flowing out of the second end 32 and the direction of the oil in the internal oil circuit 2.

[0035] In some embodiments, when the pump assembly 33 is configured to power the oil flowing out of the rod chamber 111, the active hydraulic suspension system also has an active lift mode. Figure 5 This is a schematic diagram of the active hydraulic suspension system in active lifting mode. The arrows in the diagram indicate the direction of movement of the rod piston 12 and the direction of oil flow. The pump assembly 33 shown in the diagram can be a one-way oil pump that pumps from the second end 32 to the first end 31.

[0036] like Figure 5 As shown, in active lifting mode, the pump assembly 33 starts and rotates counterclockwise as shown in the figure, which can draw out the oil in the rod chamber 111 and pump it into the rodless chamber 112. At least part of the oil flowing out of the rod chamber 111 flows into the rodless chamber 112 in sequence through the second oil flow direction, passing through the second solenoid valve 221, the pump assembly 33 and the second check valve 212, causing the rod piston 12 to move towards the rod chamber 111, thereby realizing active adjustment of the vehicle body posture. At the same time, when the oil flows along the second oil flow direction, the damping effect of the second solenoid valve 221 can reduce the tendency of the rod piston 12 to move towards the rod chamber 111, thereby reducing the vibration between the vehicle body and the suspension arms.

[0037] In some embodiments, such as Figure 1 and Figure 5 As shown, the parallel branch where the second check valve 212 is located is also equipped with a fourth check valve 213. The first end 31 of the external oil circuit 3 is connected between the second check valve 212 and the fourth check valve 213. The fourth check valve 213 is located at the inlet end of the second check valve 212, and its conduction direction is the same as that of the second check valve 212. The oil moving along the second oil flow direction can flow into the rod chamber 111 through the second solenoid valve 221, the fourth check valve 213, and the second check valve 212. By setting the fourth check valve 213, the direction of the oil flowing out of the second end 32 in the first one-way damping valve assembly 21 can be restricted in the active lifting mode, so as to avoid interference between the oil flowing out of the first end 31 and the direction of the oil in the internal oil circuit 2.

[0038] In some embodiments, such as Figure 1 As shown, pump assembly 33 is preferably a bidirectional oil pump and is configured to power the oil flowing out of rodless chamber 112 when rotating clockwise (i.e., clockwise as shown in the figure) and to power the oil flowing out of rod chamber 111 when rotating counterclockwise (i.e., counterclockwise as shown in the figure). In this way, the pumping direction of pump assembly 33 can be selected as needed to power the oil flowing out of rod chamber 111 or rodless chamber 112.

[0039] In some embodiments, such as Figure 1As shown, the internal oil circuit 2 is also equipped with an accumulator 23. The accumulator 23 is located between the first one-way damping valve assembly 21 and the second one-way damping valve assembly 22. It can store excess oil during the oil circulation process, and play the role of maintaining system pressure and replenishing oil.

[0040] Specifically, due to the presence of the rod end of the rod piston 12, the cross-sectional area of ​​the oil in the rod chamber 111 is smaller than that in the rodless chamber 112. Therefore, in both passive compression mode and active compression mode, when the rod piston 12 moves towards the rodless chamber 112, the hydraulic oil squeezed out of the rodless chamber 112 cannot be completely contained in the rod chamber 111. At this time, if... Figure 2 and Figure 4 As shown, excess oil enters the accumulator 23 for storage and energy storage; in passive recovery mode and active lifting mode, the rod piston 12 moves towards the rod chamber 111, and the hydraulic oil squeezed out of the rod chamber 111 is insufficient to completely fill the rodless chamber 112. At this time, as Figure 3 and Figure 5 As shown, the accumulator 23 releases the stored energy and replenishes the oil stored inside to the rodless chamber 112, thereby maintaining the system pressure and replenishing the oil.

[0041] Furthermore, in another embodiment, a vehicle is also provided, including the active hydraulic suspension system described in the above embodiments. It is understood that for other structures and working principles of the active hydraulic suspension system, please refer to the above description of the embodiments of the active hydraulic suspension system; for other structures of the vehicle, please refer to the prior art. Since the active hydraulic suspension system has the aforementioned technical effects, a vehicle having this active hydraulic suspension system should also have corresponding technical effects, which will not be elaborated further here.

[0042] It is understood that, in this utility model, unless otherwise explicitly specified and limited, the terms "assembly," "connection," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0043] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. "A plurality of" means two or more, unless otherwise explicitly specified. The terms "some embodiments," "exemplarily," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this utility model.

[0044] The illustrative expressions of the terms used above do not necessarily refer to the same embodiments or examples. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, those skilled in the art can combine and integrate the different embodiments or examples described herein, as well as the features of those different embodiments or examples, without contradiction.

[0045] Although embodiments of the present invention have been shown and described above, it should be understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make modifications, substitutions and variations to the above embodiments within the scope of the present invention. Therefore, any changes or modifications made in accordance with the claims and description of the present invention should fall within the scope of the patent coverage of the present invention.

Claims

1. An active hydraulic suspension system, characterized by include: The damper body includes a hydraulic cylinder and a rod piston slidably disposed inside the hydraulic cylinder, the rod piston dividing the inside of the hydraulic cylinder into a rod chamber and a rodless chamber; An internal oil passage is provided, one end of which is connected to the rodless chamber via a first one-way damping valve assembly, which provides damping force to the oil flowing out of the rodless chamber; the other end of the internal oil passage is connected to the rod chamber via a second one-way damping valve assembly, which provides damping force to the oil flowing out of the rod chamber; wherein the oil in the rodless chamber and the rod chamber can flow between each other along the internal oil passage; and An external oil passage, the first end of which is connected to the outlet end of the first one-way damping valve assembly, and the second end of which is connected to the outlet end of the second one-way damping valve assembly, and is equipped with a pump assembly for providing power to the oil flowing out of the rodless chamber and / or the rod chamber.

2. An active hydraulic suspension system according to claim 1, wherein, The internal oil circuit includes a first solenoid valve and a first check valve connected sequentially along a first oil flow direction, and a second solenoid valve and a second check valve connected sequentially along a second oil flow direction, wherein the second oil flow direction is opposite to the first oil flow direction; wherein... The first solenoid valve and the second check valve are connected in parallel to form the first one-way damping valve assembly, and the second solenoid valve and the first check valve are connected in parallel to form the second one-way damping valve assembly.

3. An active hydraulic suspension system according to claim 2, wherein, The active hydraulic suspension system has a passive compression mode and a passive recovery mode: In the passive pressure mode, the pump assembly is turned off, the rod piston moves toward the rodless chamber, and the oil flowing out of the rodless chamber flows into the rod chamber in sequence through the first solenoid valve and the first check valve along the first oil flow direction. In the passive recovery mode, the pump assembly is turned off, the rod piston moves toward the rod chamber, and the oil flowing out of the rod chamber flows into the rodless chamber in sequence through the second solenoid valve and the second check valve along the second oil flow direction.

4. An active hydraulic suspension system according to claim 3, wherein When the pump assembly is configured to power the oil flowing out of the rodless chamber, the active hydraulic suspension system also has an active compression mode: In the active compression mode, the pump assembly is activated, and at least a portion of the oil flowing out of the rodless chamber flows into the rod chamber along the first oil flow direction, passing sequentially through the first solenoid valve, the pump assembly, and the first check valve, causing the rod piston to move toward the rodless chamber.

5. An active hydraulic suspension system according to claim 4, wherein The parallel branch containing the first check valve is also equipped with a third check valve, and the second end of the external oil circuit is connected between the first check valve and the third check valve; wherein... The third check valve is located at the inlet end of the first check valve, and its conduction direction is the same as that of the first check valve.

6. An active hydraulic suspension system according to any one of claims 3 to 5, wherein, When the pump assembly is configured to power the oil flowing out of the rod chamber, the active hydraulic suspension system also has an active lifting mode: In the active lifting mode, the pump assembly is activated, and at least a portion of the oil flowing out of the rod chamber flows into the rodless chamber in sequence through the second solenoid valve, the pump assembly, and the second check valve along the second oil flow direction, causing the rod piston to move toward the rod chamber.

7. An active hydraulic suspension system according to claim 6, characterized in that, The parallel branch containing the second check valve is also equipped with a fourth check valve, and the first end of the external oil circuit is connected between the second check valve and the fourth check valve; wherein, The fourth check valve is located at the inlet end of the second check valve, and its conduction direction is the same as that of the second check valve.

8. An active hydraulic suspension system according to claim 1, wherein, The internal oil circuit is also equipped with an accumulator, which is located between the first one-way damping valve assembly and the second one-way damping valve assembly.

9. An active hydraulic suspension system according to claim 1, wherein, The pump assembly is a bidirectional oil pump and is configured to power the oil flowing out of the rodless chamber when rotating forward and to power the oil flowing out of the rod chamber when rotating in reverse.

10. A vehicle characterized by comprising: Including the active hydraulic suspension system as described in any one of claims 1-9.

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