Shock absorber and active suspension system

Abstract

The invention relates to a shock absorber which comprises a hydraulic cylinder, a first one-way damping valve, a second one-way damping valve, a first energy accumulator, a second energy accumulator and a first control valve. Wherein the hydraulic cylinder comprises a cylinder body and a piston, the piston is arranged in the cylinder body in a sliding mode, and an inner cavity of the cylinder body is divided into a rod cavity and a rodless cavity; the rod cavity, the first one-way damping valve, the first energy accumulator, the first control valve, the second energy accumulator, the second one-way damping valve and the rodless cavity are sequentially connected to form a fluid loop. The first one-way damping valve and the second one-way damping valve communicate with the rod cavity and the rodless cavity correspondingly, the first one-way damping valve is suitable for forming damping on oil in the direction that the oil flows out of the rod cavity, and the second one-way damping valve is suitable for forming damping on the oil in the direction that the oil flows out of the rodless cavity; the first control valve is suitable for controlling a flow path between the first energy accumulator and the second energy accumulator to be connected or disconnected. According to the shock absorber and the active suspension system provided by the invention, the controllability and comfort of the suspension system can be improved.

Description

Technical Field

[0001] The invention relates to a shock absorber and an active suspension system. Background Art

[0002] In the suspension system of the prior art, the damping element mainly uses a passive shock absorber, and the anti-roll element generally uses a lateral stabilizer bar. However, the solution of the passive shock absorber and the lateral stabilizer bar cannot achieve good handling and comfort at the same time. Summary of the Invention

[0003] An object of the present invention is to provide a shock absorber and an active suspension system including the shock absorber that can improve the handling and comfort of a vehicle.

[0004] A first aspect of the present invention provides a shock absorber comprising a hydraulic cylinder, a first one-way damping valve, a second one-way damping valve, a first accumulator, a second accumulator and a first control valve; wherein,

[0005] The hydraulic cylinder includes a cylinder body and a piston, wherein the piston is slidably disposed in the cylinder body to separate the inner cavity of the cylinder body into a rod cavity and a rodless cavity;

[0006] The rod chamber, the first one-way damping valve, the first accumulator, the first control valve, the second accumulator, the second one-way damping valve, and the rodless chamber are sequentially connected to form a fluid circuit;

[0007] A first one-way damping valve and a second one-way damping valve are respectively connected to the rod chamber and the rodless chamber, the first one-way damping valve is adapted to damp the oil in a direction in which the oil flows out of the rod chamber, and the second one-way damping valve is adapted to damp the oil in a direction in which the oil flows out of the rodless chamber;

[0008] The first control valve is adapted to control the flow path between the first accumulator and the second accumulator to be open or closed.

[0009] The vibration absorber provided by the present invention further includes:

[0010] A bidirectional pump is provided on the fluid circuit, and is suitable for pumping the oil from one of the rod cavity and the rodless cavity into the other cavity.

[0011] The second aspect of the present invention provides a shock absorber, which includes a hydraulic cylinder, a first one-way damping valve, a second one-way damping valve, a first accumulator, a second accumulator, a second control valve, a third control valve, and a bidirectional pump; wherein,

[0012] The hydraulic cylinder includes a cylinder body and a piston, wherein the piston is slidably disposed in the cylinder body to separate the inner cavity of the cylinder body into a rod cavity and a rodless cavity;

[0013] The rod chamber, the first one-way damping valve, the first accumulator, the second branch, the second accumulator, the second one-way damping valve, and the rodless chamber are sequentially connected to form a fluid circuit;

[0014] The shock absorber has a first branch and a second branch connected in parallel, and the first branch and the second branch are both connected between the first accumulator and the second accumulator. The third control valve is provided on the first branch and is suitable for controlling the first branch to be conductive or cut off.

[0015] The bidirectional pump and the second control valve are arranged on the second branch, and the second control valve is suitable for controlling the second branch to be conductive or cut off;

[0016] The first one-way damping valve and the second one-way damping valve are connected to the rod chamber and the rodless chamber respectively. The first one-way damping valve is suitable for damping the oil in the direction of oil flowing out of the rod chamber, and the second one-way damping valve is suitable for damping the oil in the direction of oil flowing out of the rodless chamber.

[0017] A third aspect of the present application provides a shock absorber comprising a hydraulic cylinder, a first one-way damping valve, a second one-way damping valve, a first accumulator, a second accumulator, a fourth control valve, a fifth control valve, a sixth control valve and a bidirectional pump; wherein,

[0018] The hydraulic cylinder includes a cylinder body and a piston, wherein the piston is slidably disposed in the cylinder body to separate the inner cavity of the cylinder body into a rod cavity and a rodless cavity;

[0019] The rod chamber, the first one-way damping valve, the first accumulator, the fourth control valve, the two-way pump, the fifth control valve, the second accumulator, the second one-way damping valve, and the rodless chamber are sequentially connected to form a fluid circuit;

[0020] The first one-way damping valve is adapted to damp the oil in a direction in which the oil flows out of the rod chamber, and the second one-way damping valve is adapted to damp the oil in a direction in which the oil flows out of the rodless chamber;

[0021] The fourth control valve is adapted to control the flow path between the bidirectional pump and the first accumulator to be open or closed, and the fifth control valve is adapted to control the flow path between the bidirectional pump and the second accumulator to be open or closed;

[0022] The sixth control valve is connected in parallel with the bidirectional pump, and both the sixth control valve and the bidirectional pump are connected between the fourth control valve and the fifth control valve.

[0023] According to the shock absorber provided by the present invention, the fourth control valve and the fifth control valve are both one-way locking valves, wherein:

[0024] When the fourth control valve is in the locked position and the oil flows from the first accumulator to the bidirectional pump, the fourth control valve is cut off;

[0025] When the fifth control valve is in the closed position and oil flows from the second accumulator to the bidirectional pump, the fifth control valve is cut off.

[0026] A fourth aspect of the present invention provides a shock absorber comprising a hydraulic cylinder, a first one-way damping valve, a second one-way damping valve, a first accumulator, a second accumulator, a seventh control valve, an eighth control valve and a bidirectional pump; wherein,

[0027] The hydraulic cylinder includes a cylinder body and a piston, wherein the piston is slidably disposed in the cylinder body to separate the inner cavity of the cylinder body into a rod cavity and a rodless cavity;

[0028] The rod chamber, the first one-way damping valve, the first accumulator, the two-way pump, the seventh control valve, the second accumulator, the second one-way damping valve, and the rodless chamber are sequentially connected to form a fluid circuit;

[0029] The first one-way damping valve is adapted to damp the oil in a direction in which the oil flows out of the rod chamber, and the second one-way damping valve is adapted to damp the oil in a direction in which the oil flows out of the rodless chamber;

[0030] The seventh control valve is adapted to control the flow path between the bidirectional pump and the second accumulator to be open or closed;

[0031] The eighth control valve is connected in parallel with the bidirectional pump, and both the eighth control valve and the bidirectional pump are connected between the seventh control valve and the first accumulator.

[0032] According to the shock absorber provided by the present invention, the seventh control valve and the eighth control valve are both two-way locking valves.

[0033] The vibration absorber provided by the present invention further includes:

[0034] A one-way pressure relief valve is provided on the piston, and the one-way pressure relief valve is adapted to be conducted when the pressure in the rodless chamber is greater than the pressure in the rod chamber and exceeds a set threshold.

[0035] According to the shock absorber provided by the present invention, the one-way pressure relief valve is provided on the piston.

[0036] The vibration absorber provided by the present invention further includes:

[0037] A microporous device and a pressure-stabilizing accumulator, wherein the pressure-stabilizing accumulator is connected to the fluid circuit through the microporous device.

[0038] According to the shock absorber provided by the present invention, the damping of the first one-way damping valve and the second one-way damping valve is adjustable.

[0039] A fourth aspect of the present invention provides an active suspension system, comprising the shock absorber as described in any one of the above items.

[0040] The shock absorber and active suspension system provided by the present invention include passive compression / tension operating conditions and active anti-roll / pitch operating conditions. In the passive compression / tension operating condition, the first control valve is in the on position, thereby connecting the flow path between the first accumulator and the second accumulator. In the active anti-roll / pitch operating condition, the first control valve is in the off position, thereby blocking the flow path between the first accumulator and the second accumulator.

[0041] Specifically, when the hydraulic cylinder is in a passive compression state, the piston rod and piston of the hydraulic cylinder move toward the rodless chamber, and the oil in the rodless chamber is squeezed out and passes through the second one-way damping valve to generate a compression damping force. Since the cross-sectional area of ​​the rodless chamber is larger than that of the rod chamber, a portion of the oil discharged from the rodless chamber enters the rod chamber through the first control valve, and the remaining oil enters the first accumulator and the second accumulator. When the hydraulic cylinder switches to a passive tension state, the piston rod and piston move toward the rod chamber, and the oil in the rod chamber is squeezed out and passes through the first one-way damping valve to generate a tension damping force. The cross-sectional area of ​​the rodless chamber is larger than that of the rod chamber, so the oil discharged from the rod chamber enters the rodless chamber through the first control valve. At the same time, the oil in the first accumulator and the second accumulator respectively passes through the first one-way damping valve and the second one-way damping valve (no damping force is generated) and enters the rodless chamber.

[0042] During roll / pitch operation, the first control valve is closed. The hydraulic cylinder on the compression side of the suspension is forced out of the rodless chamber, flowing through the second one-way damping valve into the second accumulator, increasing the pressure in the rodless chamber. The oil in the first accumulator then flows through the first one-way damping valve (which does not generate damping force) and into the rod chamber, reducing the pressure in the rod chamber. Consequently, the pressure in the rodless chamber is significantly greater than that in the rod chamber, generating a force that resists the piston's movement toward the rodless chamber and reduces the amount of compression in the hydraulic cylinder. When the shock absorber is in roll / pitch operation and the hydraulic cylinder is subjected to tension, the oil in the rod chamber is forced out of the rod chamber, flowing through the first one-way damping valve into the first accumulator, increasing the pressure in the rod chamber. The oil in the second accumulator then flows through the second one-way damping valve (which does not generate damping force) and into the rodless chamber. This reduces the pressure in the rod chamber, resulting in a significantly greater pressure in the rod chamber, generating a force that resists the piston's movement toward the rod chamber and reducing the amount of tension in the hydraulic cylinder. By arranging the hydraulic cylinders of the present invention on both sides of the vehicle body, the two hydraulic cylinders exert opposite forces on the vehicle body, thereby generating a moment to resist roll / pitch. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] Figure 1 is a schematic structural diagram of a shock absorber according to a first embodiment of the present invention;

[0044] Figure 2a is a schematic structural diagram showing a shock absorber in a passive compression state according to a first embodiment of the present invention;

[0045] Figure 2b is a schematic structural diagram showing a vibration absorber according to a first embodiment of the present invention in a passive tension working condition;

[0046] Figure 3a is a schematic structural diagram showing a shock absorber according to a first embodiment of the present invention in a roll / pitch working condition with a hydraulic cylinder under compression;

[0047] Figure 3b is a schematic structural diagram showing a shock absorber according to a first embodiment of the present invention in a roll / pitch working condition, with the hydraulic cylinder being stretched;

[0048] Figure 4 is a schematic structural diagram of a shock absorber according to a second embodiment of the present invention;

[0049] Figure 5a is a schematic structural diagram showing a shock absorber in a passive compression state according to a second embodiment of the present invention;

[0050] Figure 5b is a schematic structural diagram showing a vibration absorber according to a second embodiment of the present invention in a passive tension condition;

[0051] Figure 6a is a schematic structural diagram showing a shock absorber under active compression according to a second embodiment of the present invention;

[0052] Figure 6b is a schematic structural diagram showing a vibration absorber according to a second embodiment of the present invention in an active stretching condition;

[0053] Figure 7a is a schematic structural diagram showing a shock absorber according to a second embodiment of the present invention in a roll / pitch working condition, with the hydraulic cylinder being compressed;

[0054] Figure 7b is a schematic structural diagram showing a shock absorber according to a second embodiment of the present invention in a roll / pitch working condition, with the hydraulic cylinder being stretched;

[0055] Figure 8 is a schematic structural diagram of a shock absorber according to a third embodiment of the present invention;

[0056] Figure 9a is a schematic structural diagram showing a shock absorber in a passive compression state according to a third embodiment of the present invention;

[0057] Figure 9b is a schematic structural diagram showing a vibration absorber according to a third embodiment of the present invention in a passive tension working condition;

[0058] Figure 10a is a schematic structural diagram showing a shock absorber under active compression according to a third embodiment of the present invention;

[0059] Figure 10b is a schematic structural diagram showing a vibration absorber according to a third embodiment of the present invention in an active stretching condition;

[0060] Figure 11a is a schematic structural diagram showing a shock absorber according to a third embodiment of the present invention in a roll / pitch working condition with a hydraulic cylinder under compression;

[0061] Figure 11b is a schematic structural diagram showing a shock absorber according to a third embodiment of the present invention in a roll / pitch working condition, with the hydraulic cylinder being stretched;

[0062] Figure 12 is a schematic structural diagram of a shock absorber according to a fourth embodiment of the present invention;

[0063] Figure 13a is a schematic structural diagram showing a shock absorber in a passive compression state according to a fourth embodiment of the present invention;

[0064] Figure 13b is a schematic structural diagram showing a vibration absorber according to a fourth embodiment of the present invention in a passive tension working condition;

[0065] Figure 14a is a schematic structural diagram showing a shock absorber under active compression according to a fourth embodiment of the present invention;

[0066] Figure 14b is a schematic structural diagram showing a shock absorber according to a fourth embodiment of the present invention in an active stretching condition;

[0067] Figure 15a is a schematic structural diagram showing a shock absorber according to a fourth embodiment of the present invention in a roll / pitch working condition with a hydraulic cylinder under compression;

[0068] Figure 15b 3 is a schematic structural diagram showing a shock absorber according to a fourth embodiment of the present invention in a roll / pitch working state, with the hydraulic cylinder being stretched. DETAILED DESCRIPTION

[0069] The following detailed description and accompanying drawings are used to illustrate the principles of the present invention. The present invention is not limited to the preferred embodiments described. The scope of protection of the present invention is defined by the claims.

[0070] It should be noted that the orientations or positional relationships indicated in this specification are based on the orientations or positional relationships described in the accompanying drawings and are only for the convenience and simplification of description, and do not indicate or imply that the device referred to must have a specific orientation or be constructed in a specific orientation. Therefore, it should not be understood as a limitation on the present invention.

[0071] Please refer to Figure 1 In some embodiments of the present invention, the shock absorber includes a hydraulic cylinder, a first one-way damping valve 4 , a second one-way damping valve 6 , a first accumulator 5 , a second accumulator 7 and a first control valve 13 .

[0072] A hydraulic cylinder comprises a cylinder body 1, a piston 2, and a piston rod 3. The piston 2 is slidably disposed within the cylinder body 1, dividing the interior of the cylinder body 1 into a rod chamber and a rodless chamber. The piston rod 3 is connected to the piston 2 and extends out of the cylinder body 1 from the end of the rod chamber. In this embodiment, the cylinder body 1 of the hydraulic cylinder is connected to the vehicle body, and the piston rod 3 is connected to the vehicle's suspension arm. Alternatively, the cylinder body 1 of the hydraulic cylinder is connected to the vehicle's suspension arm, and the piston rod 3 is connected to the vehicle body.

[0073] When oil flows through the first and second one-way damping valves 4 and 6 in a set direction, they can generate a damping force on the oil. When oil flows through the first and second one-way damping valves 4 and 6 in a direction opposite to the set direction, they do not generate a damping force on the oil.

[0074] The rod chamber of the hydraulic cylinder, the first one-way damping valve 4, the first accumulator 5, the first control valve 13, the second accumulator 7, the second one-way damping valve 6, and the rodless chamber are sequentially connected to form a fluid circuit.

[0075] The first one-way damping valve 4 and the second one-way damping valve 6 are connected to the rod chamber and the rodless chamber of the hydraulic cylinder, respectively. The first one-way damping valve 4 is adapted to damp the oil in the direction of oil flowing out of the rod chamber, and to not damp the oil in the direction of oil flowing out of the rodless chamber. The second one-way damping valve 6 is adapted to damp the oil in the direction of oil flowing out of the rodless chamber, and to not damp the oil in the direction of oil flowing out of the rodless chamber.

[0076] The first control valve 13 is adapted to control the flow path between the first accumulator 5 and the second accumulator 7 to be open or closed.

[0077] The shock absorber provided in this embodiment operates in both passive compression / tension and active anti-roll / pitch conditions. In the passive compression / tension condition, the first control valve 13 is in the on position, allowing the flow path between the first accumulator 5 and the second accumulator 7 to flow. In the active anti-roll / pitch condition, the first control valve 13 is in the off position, blocking the flow path between the first accumulator 5 and the second accumulator 7.

[0078] Specifically, if Figure 2a As shown, the arrow in the figure indicates the direction of movement of the piston rod 3 and the direction of oil flow. When the hydraulic cylinder is in passive compression, the piston rod 3 and piston 2 of the hydraulic cylinder move toward the rodless chamber, forcing the oil in the rodless chamber out and passing through the second one-way damping valve 6 to generate a compression damping force. Because the cross-sectional area of ​​the rodless chamber is larger than that of the rod chamber, a portion of the oil discharged from the rodless chamber enters the rod chamber through the first control valve 13, and the remaining oil enters the first accumulator 5 and the second accumulator 7.

[0079] like Figure 2b As shown, when the hydraulic cylinder switches to the passive tension mode, the piston rod 3 and piston 2 move toward the rod chamber. The oil in the rod chamber is forced out and passes through the first one-way damping valve 4, generating a tensile damping force. The cross-sectional area of ​​the rodless chamber is larger than that of the rod chamber. Therefore, all the oil discharged from the rod chamber enters the rodless chamber through the first control valve 13. Simultaneously, the oil in the first accumulator 5 and the second accumulator 7, respectively, passes through the first one-way damping valve 4 and the second one-way damping valve 6 (which do not generate a damping force), and enters the rodless chamber.

[0080] When the suspension is in roll / pitch condition, the suspension compresses the side, e.g. Figure 3a As shown, the oil in the rodless chamber is forced out, flowing through the second one-way damping valve 6 into the second accumulator 7, increasing the pressure in the rodless chamber. The oil in the first accumulator 5 passes through the first one-way damping valve 4 (which does not generate damping force) and enters the rod chamber, reducing the pressure in the rod chamber. Consequently, the pressure in the rodless chamber is much greater than that in the rod chamber, generating a force that resists the movement of the piston 2 toward the rodless chamber, reducing the compression of the hydraulic cylinder.

[0081] When the suspension is in roll / pitch condition, the suspension stretches on the side such as Figure 3b As shown, the oil in the rod chamber is forced out, flowing through the first one-way damping valve 4 into the first accumulator 5, increasing the pressure in the rod chamber. The oil in the second accumulator 7 passes through the second one-way damping valve 6 (which does not generate damping force) and enters the rodless chamber, reducing the pressure in the rodless chamber. Consequently, the pressure in the rod chamber is much greater than that in the rodless chamber, generating a force that resists the movement of the piston 2 toward the rod chamber, reducing the extension of the hydraulic cylinder.

[0082] In this embodiment, hydraulic cylinders may be arranged on both sides of the vehicle body, so that the two hydraulic cylinders exert opposite forces on the vehicle body, thereby generating a moment to resist roll / pitch.

[0083] In a further embodiment, the shock absorber further comprises a one-way pressure relief valve 9. The two end interfaces of the one-way pressure relief valve 9 are respectively connected to the rod chamber and the rodless chamber, and the one-way pressure relief valve 9 is adapted to be opened when the pressure in the rodless chamber is greater than that in the rod chamber and exceeds a set threshold.

[0084] In a further embodiment, the shock absorber further includes a microporous device 11 and a pressure-stabilizing accumulator 10. The pressure-stabilizing accumulator 10 is connected to the fluid circuit via the microporous device 11, which is provided with one or more micropores. When oil flows between the fluid circuit and the pressure-stabilizing accumulator 10, it passes through the micropores of the microporous device 11, which provide a significant damping effect, resulting in a very small flow rate through the microporous device 11. The connection location of the microporous device 11 to the fluid circuit can be determined depending on the situation. For example, the microporous device 11 can be connected to the flow path between the first control valve 13 and the first accumulator 5, or to the flow path between the first control valve 13 and the second accumulator 7.

[0085] With this arrangement, when the oil in the fluid circuit changes volume due to temperature fluctuations, the pressure-stabilizing accumulator 10 and the microporous device 11 can act as a counterbalance, preventing significant fluctuations in the fluid pressure in the fluid circuit. The oil volume changes caused by temperature fluctuations can enter and exit the pressure-stabilizing accumulator 10 through the microporous device 11. It should be noted that due to the small aperture of the microporous device 11, it can exert a significant damping force on the oil. Therefore, when the shock absorber is operating, it can be considered that no oil enters the pressure-stabilizing accumulator 10 through the microporous device 11.

[0086] In a further embodiment, the damping of the first one-way damping valve 4 and the second one-way damping valve 6 is adjustable. Specifically, the first one-way damping valve 4 and the second one-way damping valve 6 can be electrically controlled adjustable damping valves, and the damping force of the two can be adjusted by current control.

[0087] In a further embodiment, the shock absorber further comprises a bidirectional pump 8. The bidirectional pump 8 is provided on the fluid circuit and is adapted to pump the oil from one of the rod cavity and the rodless cavity into the other cavity.

[0088] With this configuration, the shock absorber not only maintains the functions of the above-mentioned embodiments but also realizes active compression / tension operating conditions. When in active compression mode, bidirectional pump 8 activates and pumps oil from the rodless chamber into the rod chamber, causing piston 2 and piston rod 3 to move toward the rodless chamber. When in active tension mode, bidirectional pump 8 pumps oil from the rod chamber into the rodless chamber, causing piston 2 and piston rod 3 to move toward the rod chamber.

[0089] In some embodiments, a bidirectional pump 8 can be provided in the flow path between the first accumulator 5 and the second accumulator 7. When in an active compression state, the bidirectional pump 8 is activated and pumps oil from the rodless chamber and the second accumulator 7 into the rod chamber and the first accumulator 5, causing the piston 2 and the piston rod 3 to move toward the rodless chamber. When in an active tension state, the bidirectional pump 8 pumps oil from the rod chamber and the first accumulator 5 into the rodless chamber and the second accumulator 7, causing the piston 2 and the piston rod 3 to move toward the rod chamber.

[0090] In order to realize the active compression / extension working condition of the shock absorber, the fluid circuit can be specifically configured as follows: Figure 4 As shown, the shock absorber has a first branch and a second branch, which are connected in parallel and connected to the first accumulator 5 and the second accumulator 7 at their ends, respectively. A third control valve 14 is provided on the first branch and is adapted to control the flow of the first branch. Specifically, the third control valve 14 is switchable between an on position and a off position. When the third control valve 14 is in the on position, the first branch is open; when in the off position, the first branch is closed.

[0091] The bidirectional pump 8 and the second control valve 12 are disposed on the second branch. The second control valve 12 is adapted to control the conduction or blocking of the second branch. The second control valve 12 is switchable between an on position and a blocked position. When the second control valve 12 is in the on position, the second branch is conducted; when the second control valve 12 is in the blocked position, the second branch is blocked.

[0092] In this embodiment, the microporous device 11 can be connected to the second branch.

[0093] With such configuration, the shock absorber provided in this embodiment has three working conditions. The control principles of the three working conditions of the shock absorber are described in detail below.

[0094] Working condition 1: Passive compression / tension working condition. Under this working condition, the third control valve 14 and the second control valve 12 are both open.

[0095] like Figure 5a As shown, the shock absorber operates in passive compression mode. The piston rod 3 and piston 2 move toward the rodless chamber, forcing the oil in the rodless chamber out through the second one-way damping valve 6, generating a compression damping force. The cross-sectional area of ​​the rodless chamber is larger than that of the rod chamber. Therefore, a portion of the oil discharged from the rodless chamber enters the rod chamber through the first control valve 13, while the remainder enters the second accumulator 7 and the first accumulator 5. If the compression speed is too high and the pressure in the rodless chamber exceeds the set pressure of the one-way pressure relief valve 9, the one-way pressure relief valve 9 opens to prevent system damage.

[0096] like Figure 5bAs shown, the shock absorber is operating in passive tension mode, with the piston rod 3 and piston 2 moving toward the rod chamber. The oil in the rod chamber is forced out and passes through the first one-way damping valve 4, generating a tensile damping force. The cross-sectional area of ​​the rodless chamber is larger than that of the rod chamber. Therefore, all the oil discharged from the rod chamber enters the rodless chamber through the first control valve 13. Simultaneously, the oil in the first and second accumulators 5, 7, passes through the second one-way damping valve 6 and enters the rodless chamber.

[0097] Working condition 2: active compression / tension working condition. Under this working condition, the second control valve 12 is opened, the third control valve 14 is closed, and the bidirectional pump 8 is started.

[0098] like Figure 6a As shown, when the shock absorber is in active compression working condition, the bidirectional pump 8 draws oil from the rodless chamber and the second accumulator 7 and pumps it into the rod chamber and the first accumulator 5, causing the piston rod 3 and the piston 2 to move toward the rodless chamber.

[0099] like Figure 6b As shown, when the shock absorber is in active stretching condition, the bidirectional pump 8 draws oil from the rod chamber and the first accumulator 5, and pumps it into the rodless chamber and the second accumulator 7, causing the piston rod 3 and the piston 2 to move toward the rod chamber.

[0100] Working condition 3: active anti-roll / pitch working condition. Under this working condition, the third control valve 14 and the second control valve 12 are both closed, and the bidirectional pump 8 does not work.

[0101] like Figure 7a As shown, in the roll / pitch operation of the shock absorber, the oil in the rodless chamber of the compressed hydraulic cylinder is forced out through the second one-way damping valve 6 and into the second accumulator 7, increasing the pressure in the rodless chamber. The oil in the first accumulator 5 then passes through the first one-way damping valve 4 (which does not generate damping force) and enters the rod chamber, reducing the pressure in the rod chamber. Consequently, the pressure in the rodless chamber is much greater than that in the rod chamber, generating a force that resists the movement of the piston 2 into the rodless chamber and reduces the compression of the hydraulic cylinder.

[0102] like Figure 7b As shown, in the roll / pitch operating mode, when the hydraulic cylinder is stretched, the oil in the rod chamber is forced out through the first one-way damping valve 4 and flows into the first accumulator 5, increasing the pressure in the rod chamber. The oil in the second accumulator 7 then flows through the second one-way damping valve 6 (which does not generate damping force) and enters the rodless chamber. The pressure in the rodless chamber decreases, resulting in a much greater pressure in the rod chamber than in the rodless chamber. This creates a force resisting the movement of the piston 2 toward the rod chamber, reducing the stretch of the hydraulic cylinder.

[0103] The two hydraulic cylinders exert opposing forces on the vehicle body, generating a moment that resists roll / pitch.

[0104] In another embodiment, the fluid circuit of the shock absorber can also be set in other forms, and the above three working conditions can also be achieved. Figure 8 As shown, the rod chamber of the hydraulic cylinder, the first one-way damping valve 4, the first accumulator 5, the fourth control valve 15, the two-way pump 8, the fifth control valve 16, the second accumulator 7, the second one-way damping valve 6, and the rodless chamber are sequentially connected to form a fluid circuit. The first interface of the fourth control valve 15 is connected to the first accumulator 5. Specifically, the first interface of the fourth control valve 15 can be connected to the flow path between the first accumulator 5 and the first one-way damping valve 4. The fifth control valve 16 is connected to the second accumulator 7. Specifically, the first interface of the fifth control valve 16 can be connected to the flow path between the second accumulator 7 and the second one-way damping valve 6.

[0105] The bidirectional pump 8 is connected in parallel with the sixth control valve 17, and both are connected between the fourth control valve 15 and the fifth control valve 16. Specifically, the first port of the bidirectional pump 8 and the first interface of the sixth control valve 17 are both connected to the second interface of the fourth control valve 15, and the second port of the bidirectional pump 8 and the second interface of the sixth control valve 17 are both connected to the second interface of the fifth control valve 16, so that the bidirectional pump 8 and the sixth control valve 17 are connected in parallel.

[0106] The fourth control valve 15 and the fifth control valve 16 are adapted to be switched between an on position and a off position.

[0107] In this embodiment, the fourth control valve 15 and the fifth control valve 16 are both configured as one-way locking valves. When the fourth control valve 15 is in the locking position and oil flows from the first accumulator 5 to the bidirectional pump 8, the fourth control valve 15 is closed. When the fifth control valve 16 is in the locking position and oil flows from the second accumulator 7 to the bidirectional pump 8, the fifth control valve 16 is closed.

[0108] With such configuration, the shock absorber provided in this embodiment also has three working conditions. The control principles of the three working conditions of the shock absorber are described in detail below.

[0109] Working condition 1: passive compression / tension working condition. Under this working condition, the fourth control valve 15, the fifth control valve 16 and the sixth control valve 17 are all open.

[0110] Figure 9a In the passive compression mode, the piston rod 3 and piston 2 move toward the rodless chamber, forcing the oil in the rodless chamber out through the second one-way damping valve 6, generating a compression damping force. The cross-sectional area of ​​the rodless chamber is larger than that of the rod chamber. Therefore, a portion of the oil discharged from the rodless chamber enters the rod chamber through the sixth control valve 17, while the remainder enters the second accumulator 7 and the first accumulator 5. If the compression speed is too high and the pressure in the rodless chamber exceeds the set pressure of the one-way pressure relief valve 9, the one-way pressure relief valve 9 opens to relieve pressure and prevent system damage.

[0111] Figure 9b In the passive tension mode, the piston rod 3 and piston 2 move toward the rod chamber, forcing the oil in the rod chamber out through the first one-way damping valve 4, generating a tensile damping force. The cross-sectional area of ​​the rodless chamber is larger than that of the rod chamber. Therefore, all the oil discharged from the rod chamber enters the rodless chamber through the sixth control valve 17. Simultaneously, the oil in the second accumulator 7 enters the rodless chamber through the second one-way damping valve 6.

[0112] Working condition 2: active compression / tension working condition. Under this working condition, the fourth control valve 15 and the fifth control valve 16 are opened, and the sixth control valve 17 is closed.

[0113] Figure 10a For active compression working condition, the bidirectional pump 8 draws oil from the rodless chamber and the second accumulator 7, and pumps it into the rod chamber and the first accumulator 5, so that the piston rod 3 and the piston 2 move toward the rodless chamber.

[0114] Figure 10b For active stretching conditions, the bidirectional pump 8 draws oil from the rod chamber and the first accumulator 5 and pumps it into the rodless chamber and the second accumulator 7, causing the piston rod 3 and the piston 2 to move toward the rod chamber.

[0115] Working condition 3: active anti-roll / pitch working condition. Under this working condition, the fifth control valve 16 is closed, the sixth control valve 17 is opened, and the bidirectional pump 8 does not work.

[0116] Figure 11a In the roll / pitch operating mode, the oil in the rodless chamber of the compressed hydraulic cylinder is forced out through the second one-way damping valve 6 and flows into the second accumulator 7, increasing the pressure in the rodless chamber. The oil in the first accumulator 5 passes through the first one-way damping valve 4 (which does not generate damping force) and enters the rod chamber, reducing the pressure in the rod chamber. As a result, the pressure in the rodless chamber is much greater than that in the rod chamber, generating a force that resists the movement of the piston 2 toward the rodless chamber, reducing the compression of the hydraulic cylinder.

[0117] Figure 11b In the roll / pitch operating condition, the hydraulic cylinder is stretched, and the oil in the rod chamber is forced out through the first one-way damping valve 4 and flows into the first accumulator 5, increasing the pressure in the rod chamber. The oil in the second accumulator 7 passes through the second one-way damping valve 6 (which does not generate damping force) and enters the rodless chamber. The pressure in the rodless chamber decreases. As a result, the pressure in the rod chamber is much greater than that in the rodless chamber, generating a force that resists the movement of the piston 2 toward the rod chamber, reducing the stretch of the hydraulic cylinder.

[0118] The two hydraulic cylinders exert opposing forces on the vehicle body, creating a moment that resists roll / pitch.

[0119] In another embodiment of the present application, Figure 12As shown, the shock absorber includes a hydraulic cylinder, a first one-way damping valve 4, a second one-way damping valve 6, a first accumulator 5, a second accumulator 7, a seventh control valve 18, an eighth control valve 19 and a two-way pump 8; wherein, the hydraulic cylinder includes a cylinder body 1 and a piston 2, and the piston 2 is slidably arranged in the cylinder body 1, dividing the inner cavity of the cylinder body 1 into a rod cavity and a rodless cavity.

[0120] The rod chamber of the hydraulic cylinder, the first one-way damping valve 4, the first accumulator 5, the two-way pump 8, the seventh control valve 18, the second accumulator 7, the second one-way damping valve 6, and the rodless chamber are connected in sequence to form a fluid circuit.

[0121] The first one-way damping valve 4 is suitable for damping the oil in the direction of oil flowing out of the rod chamber, and the second one-way damping valve 6 is suitable for damping the oil in the direction of oil flowing out of the rodless chamber.

[0122] The seventh control valve 18 is adapted to control the flow path between the bidirectional pump 8 and the second accumulator 7 to be open or closed. The eighth control valve 19 is connected in parallel with the bidirectional pump 8, and both the eighth control valve 19 and the bidirectional pump 8 are connected between the seventh control valve 18 and the first accumulator 5.

[0123] In this embodiment, the seventh control valve 18 and the eighth control valve 19 are both bidirectional locking valves. When the bidirectional locking valves are switched from the conducting position to the locking position, the bidirectional locking valves are bidirectionally cut off, that is, both oil circuits connected to the bidirectional locking valves are cut off.

[0124] With such configuration, the shock absorber provided in this embodiment also has three working conditions. The control principles of the three working conditions of the shock absorber are described in detail below.

[0125] Working condition 1: passive compression / tension working condition. Under this working condition, the seventh control valve 18 and the eighth control valve 19 are both open.

[0126] Figure 13a In the passive compression mode, the piston rod 3 and piston 2 move upward, forcing the oil in the rodless chamber out through the second one-way damping valve 6, generating a compression damping force. The cross-sectional area of ​​the rodless chamber is larger than that of the rod chamber. Therefore, some of the oil discharged from the rodless chamber enters the rod chamber through the eighth control valve 19, while the remainder enters the second accumulator 7 and the first accumulator 5. If the compression speed is too high and the pressure in the rodless chamber exceeds the set pressure of the one-way pressure relief valve 9, the one-way pressure relief valve 9 opens to prevent system damage.

[0127] Figure 13b In the passive tension mode, the piston rod 3 and piston 2 move downward, forcing the oil in the rod chamber out through the first one-way damping valve 4, generating a tensile damping force. The cross-sectional area of ​​the rodless chamber is larger than that of the rod chamber. Therefore, all the oil discharged from the rod chamber enters the rod chamber through the eighth control valve 19. Simultaneously, the oil in the second accumulator 7 and the first accumulator 5 enters the rodless chamber through the second one-way damping valve 6.

[0128] Working condition 2: active compression / tension working condition. Under this working condition, the eighth control valve 19 is opened and the seventh control valve 18 is closed.

[0129] Figure 14a For active compression working condition, the bidirectional pump 8 draws oil from the rodless chamber and the second accumulator 7 and pumps it into the rod chamber and the first accumulator 5, causing the piston rod 3 and the piston 2 to move upward.

[0130] Figure 14b For active stretching conditions, the bidirectional pump 8 draws oil from the rod chamber and the first accumulator 5 and pumps it into the rodless chamber and the second accumulator 7, causing the piston rod 3 and the piston 2 to move downward.

[0131] Working condition 3: active anti-roll / pitch working condition. Under this working condition, the seventh control valve 18 is closed, the eighth control valve 19 is opened, and the bidirectional pump 8 does not work.

[0132] Figure 15a In the roll / pitch working condition, the hydraulic cylinder is compressed, and the oil in the rodless chamber is pressed out and flows into the second accumulator 7 through the second one-way damping valve 6, and the pressure in the rodless chamber increases; the oil in the first accumulator 5 passes through the first one-way damping valve 4 (no damping force is generated) and enters the rod chamber, and the pressure in the rod chamber decreases. Therefore, the pressure in the rodless chamber is much greater than that in the rod chamber, which generates a force to resist the upward movement of the piston 2, reducing the compression of the hydraulic cylinder.

[0133] Figure 15b In the roll / pitch operating condition, the hydraulic cylinder is stretched. The oil in the rod chamber is forced out through the first one-way damping valve 4 and flows into the first accumulator 5, increasing the pressure in the rod chamber. The oil in the second accumulator 7 then flows through the second one-way damping valve 6 (which does not generate damping force) and into the rodless chamber. The pressure in the rodless chamber decreases, and as a result, the pressure in the rod chamber is much greater than that in the rodless chamber, generating a force that resists the downward movement of the piston 2, reducing the stretch of the hydraulic cylinder.

[0134] An embodiment of the present invention further provides an active suspension system, comprising the shock absorbers of the above embodiments. In some embodiments, one shock absorber may be provided on each of the left and right sides of the active suspension system.

[0135] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the various embodiments of the present invention.

[0136] Reference Signs List

[0137] 1. Cylinder body; 2. Piston; 3. Piston rod; 4. First one-way damping valve; 5. First accumulator; 6. Second one-way damping valve; 7. Second accumulator; 8. Bidirectional pump; 9. One-way pressure relief valve; 10. Pressure-stabilizing accumulator; 11. Micropore device; 12. Second control valve; 13. First control valve; 14. Third control valve; 15. Fourth control valve; 16. Fifth control valve; 17. Sixth control valve; 18. Seventh control valve; 19. Eighth control valve.

Claims

1. A shock absorber, comprising a hydraulic cylinder, a first one-way damping valve (4), a second one-way damping valve (6), a first accumulator (5), a second accumulator (7) and a first control valve (13); wherein: The hydraulic cylinder comprises a cylinder body (1) and a piston (2), wherein the piston (2) is slidably arranged in the cylinder body (1) to separate the inner cavity of the cylinder body (1) into a rod cavity and a rodless cavity; The rod chamber, the first one-way damping valve (4), the first accumulator (5), the first control valve (13), the second accumulator (7), the second one-way damping valve (6), and the rodless chamber are sequentially connected to form a fluid circuit; The first one-way damping valve (4) and the second one-way damping valve (6) are respectively connected to the rod chamber and the rodless chamber, the first one-way damping valve (4) is suitable for damping the oil in the direction of the oil flowing out of the rod chamber, and the second one-way damping valve (6) is suitable for damping the oil in the direction of the oil flowing out of the rodless chamber; The first control valve (13) is suitable for controlling the flow path between the first accumulator (5) and the second accumulator (7) to be open or closed.

2. The vibration absorber according to claim 1, further comprising: A bidirectional pump (8) is arranged on the fluid circuit, and the bidirectional pump (8) is suitable for pumping the oil from one of the rod chamber and the rodless chamber into the other chamber.

3. A shock absorber, comprising a hydraulic cylinder, a first one-way damping valve (4), a second one-way damping valve (6), a first accumulator (5), a second accumulator (7), a second control valve (12), a third control valve (14), and a bidirectional pump (8); wherein: The hydraulic cylinder comprises a cylinder body (1) and a piston (2), wherein the piston (2) is slidably disposed in the cylinder body (1) to separate the inner cavity of the cylinder body (1) into a rod cavity and a rodless cavity; The rod chamber, the first one-way damping valve (4), the first accumulator (5), the second branch, the second accumulator (7), the second one-way damping valve (6), and the rodless chamber are sequentially connected to form a fluid circuit; The shock absorber comprises a first branch and a second branch connected in parallel, wherein the first branch and the second branch are both connected between the first accumulator (5) and the second accumulator (7), and the third control valve (14) is arranged on the first branch and is suitable for controlling the first branch to be turned on or off; The bidirectional pump (8) and the second control valve (12) are arranged on the second branch, and the second control valve (12) is suitable for controlling the second branch to be turned on or off; The first one-way damping valve (4) and the second one-way damping valve (6) are respectively connected to the rod chamber and the rodless chamber. The first one-way damping valve (4) is suitable for damping the oil in the direction of the oil flowing out of the rod chamber, and the second one-way damping valve (6) is suitable for damping the oil in the direction of the oil flowing out of the rodless chamber.

4. A shock absorber, comprising a hydraulic cylinder, a first one-way damping valve (4), a second one-way damping valve (6), a first accumulator (5), a second accumulator (7), a fourth control valve (15), a fifth control valve (16), a sixth control valve (17) and a bidirectional pump (8); wherein: The hydraulic cylinder comprises a cylinder body (1) and a piston (2), wherein the piston (2) is slidably disposed in the cylinder body (1) to separate the inner cavity of the cylinder body (1) into a rod cavity and a rodless cavity; The rod chamber, the first one-way damping valve (4), the first accumulator (5), the fourth control valve (15), the two-way pump (8), the fifth control valve (16), the second accumulator (7), the second one-way damping valve (6), and the rodless chamber are sequentially connected to form a fluid circuit; The first one-way damping valve (4) is suitable for damping the oil in the direction in which the oil flows out of the rod chamber, and the second one-way damping valve (6) is suitable for damping the oil in the direction in which the oil flows out of the rodless chamber; The fourth control valve (15) is suitable for controlling the flow path between the bidirectional pump (8) and the first accumulator (5) to be connected or cut off; the fifth control valve (16) is suitable for controlling the flow path between the bidirectional pump (8) and the second accumulator (7) to be connected or cut off; The sixth control valve (17) is connected in parallel with the bidirectional pump (8), and both the sixth control valve (17) and the bidirectional pump (8) are connected between the fourth control valve (15) and the fifth control valve (16).

5. The shock absorber according to claim 4, wherein the fourth control valve (15) and the fifth control valve (16) are both one-way locking valves, wherein: When the fourth control valve (15) is in the locked position and oil flows from the first accumulator (5) to the bidirectional pump (8), the fourth control valve (15) is cut off; When the fifth control valve (16) is in the locking position and oil flows from the second accumulator (7) to the bidirectional pump (8), the fifth control valve (16) is cut off.

6. A shock absorber, comprising a hydraulic cylinder, a first one-way damping valve (4), a second one-way damping valve (6), a first accumulator (5), a second accumulator (7), a seventh control valve (18), an eighth control valve (19) and a bidirectional pump (8); wherein: The hydraulic cylinder comprises a cylinder body (1) and a piston (2), wherein the piston (2) is slidably disposed in the cylinder body (1) to separate the inner cavity of the cylinder body (1) into a rod cavity and a rodless cavity; The rod chamber, the first one-way damping valve (4), the first accumulator (5), the two-way pump (8), the seventh control valve (18), the second accumulator (7), the second one-way damping valve (6), and the rodless chamber are sequentially connected to form a fluid circuit; The first one-way damping valve (4) is suitable for damping the oil in the direction in which the oil flows out of the rod chamber, and the second one-way damping valve (6) is suitable for damping the oil in the direction in which the oil flows out of the rodless chamber; The seventh control valve (18) is suitable for controlling the flow path between the bidirectional pump (8) and the second accumulator (7) to be open or closed; The eighth control valve (19) is connected in parallel with the bidirectional pump (8), and both the eighth control valve (19) and the bidirectional pump (8) are connected between the seventh control valve (18) and the first accumulator (5).

7. The shock absorber according to claim 6, wherein the seventh control valve (18) and the eighth control valve (19) are both two-way locking valves.

8. The vibration absorber according to any one of claims 1 to 7, further comprising: A one-way pressure relief valve (9) is arranged on the piston (2), and the one-way pressure relief valve (9) is suitable for being conducted when the pressure in the rodless chamber is greater than that in the rod chamber and exceeds a set threshold.

9. The vibration absorber according to any one of claims 1 to 7, further comprising: A microporous device (11) and a pressure-stabilizing accumulator (10), wherein the pressure-stabilizing accumulator (10) is connected to the fluid circuit via the microporous device (11).

10. An active suspension system, comprising the shock absorber according to any one of claims 1 to 9.

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