Blade type hydraulic-electric shock absorber

Abstract

The invention belongs to the technical field of vehicle suspension vibration reduction, and particularly relates to a blade type hydraulic-electric vibration damper. The device comprises a shell assembly (1), a motor pump assembly (2), a blade assembly (3), a partition plate assembly (4), an end cover assembly (5), a connecting arm assembly (6), a left small oil gas buffer absorber (7), a right small oil gas buffer absorber (8), a left large oil gas buffer absorber (9), a right large oil gas buffer absorber (10), a first oil pressure sensor (11) and a second oil pressure sensor (12). According to the technical scheme, the low-damping oil-gas buffer shock absorber is arranged and absorbs and dissipates high-frequency vibration of the suspension, so that the adverse effect of rotational inertia of the electro-hydraulic conversion structure on the performance of the suspension is reduced, and the performance of the blade type electro-hydraulic shock absorber with the electro-hydraulic conversion structure is improved.

Description

Technical Field

[0001] The present invention belongs to the technical field of vehicle suspension vibration reduction, and specifically relates to a blade-type hydraulic electric shock absorber, which realizes low-pass filtering of random vibration input by a wheel through a buffer structure, and dissipates most of the high-frequency vibration by the buffer structure, thereby reducing the effect of the shock absorbing valve during high-frequency vibration, which is beneficial to reducing the power consumption of the shock absorber and reducing the vibration transmitted to the vehicle body. Background Art

[0002] The vehicle suspension system is an important part of the vehicle, used to support the vehicle body, ease the excitation of road unevenness, and attenuate vibration to play a role in vibration isolation. It is related to all dynamic performances of the vehicle, such as comfort and safety. According to its working principle, it can be divided into passive suspension, semi-active suspension, and active suspension. In order to achieve energy conservation and emission reduction of vehicles and implement the "carbon neutrality" and "carbon peak" strategies, under the promotion of my country's new energy policies, the chassis technology of new energy vehicles with full electric drive or plug-in hybrid drive has made important progress. On the other hand, the development of military vehicle chassis shows an electrification trend. The chassis technology of new energy vehicles makes the transmission and conversion of energy more efficient, more energy-saving, and more conducive to the realization of energy management and intelligent control of the whole vehicle. On the one hand, the chassis of new energy vehicles provides energy storage equipment for electromechanical suspension (energy-feeding suspension) with energy recovery function, so that the recovered vibration energy can be effectively utilized; on the other hand, it provides high-voltage and high-power energy for the active control of electromechanical suspension, which is more conducive to the active control of motors in electromechanical suspension.

[0003] Electromechanical suspension can not only realize vibration energy recovery and semi-active control, but also realize the functions of active work and active suspension, that is, the suspension that can realize the mutual conversion of mechanical energy and electrical energy is called electromechanical suspension. The technical feature of electromechanical suspension is that it uses electric motors to replace the damping elements of traditional suspension, which can realize the real-time and rapid adjustment of suspension damping parameters; on the other hand, it can actively output control force to suppress the vibration of the vehicle body.

[0004] Electromechanical suspension uses springs to support the weight of the vehicle body and buffer vibrations. Its actuator uses an electric motor as the main working element or generating element to attenuate vibrations. Although electromechanical suspension is a new type of suspension, it does not mean that its inherent characteristics are better than traditional suspensions. For traditional suspensions, since there is no inertia force or it is small, its influence on the amplitude-frequency characteristics of the suspension is generally ignored. However, for electromechanical suspensions, the influence of inertia force on suspension characteristics cannot be ignored. When there is no control, due to its own large inertial mass, the suspension characteristics deteriorate in the higher frequency area, and it will also bring more serious reliability problems.

[0005] Electromechanical suspension generally uses components such as transmission devices, motors or rotating motors in order to obtain smaller volume and better vibration reduction performance. Rotating motors have high efficiency in energy utilization and recovery and compact structure, but excessive road impact can easily damage the transmission mechanism. In addition, the maintenance of the transmission mechanism is difficult, which greatly shortens the life of the entire system. Due to the fixed connection method of the transmission device and the large rotational inertia, the impact of bad roads and frequent steering of the rotating motor type energy-feeding suspension can easily damage the transmission device and motor, so the reliability is poor. Therefore, how to minimize the adverse effects of inertia force has become the first problem to be solved in electromechanical suspension. Using the motor to generate active torque can compensate and change the adverse effects of rotational inertia. This is a method of solving the inertia problem by controlling the motor. This method has high requirements for acquisition accuracy, control time lag, motor response, etc., so it is difficult. In order to reduce the influence of inertia, the design should optimize the matching of transmission device and motor performance, reduce the transmission ratio as much as possible, and reduce the rotational inertia of rotating parts.

[0006] In order to reduce the impact of inertial mass on the electromechanical suspension system, comprehensive optimization is required from multiple dimensions. In the design stage, emphasis should be placed on optimizing the performance matching between the transmission device and the motor, and striving to reduce the transmission ratio to reduce the rotational inertia of the rotating parts. This can not only improve the overall response speed of the system, but also reduce energy loss to a certain extent and improve energy utilization efficiency. At the same time, structural optimization is also one of the key measures to reduce the impact of inertia. By enhancing the rigidity and toughness of the structure, the system's impact resistance can be effectively improved, thereby maintaining more stable performance when dealing with complex road conditions. In addition to hardware-level optimization, the selection and implementation of control strategies are also crucial. Active control or semi-active control methods can effectively reduce the acceleration of inertial mass, thereby further reducing the adverse effects of inertial mass on system performance. However, in random vibration, the acceleration of inertial mass has a large frequency of change and strong randomness, making it difficult to eliminate inertial force in software control.

[0007] The blade-type hydraulic-electric shock absorber with a hydraulic-electric conversion structure is a key component of the electromechanical suspension of military vehicles. It is generally used together with a torsion bar spring and a connecting mechanism to form an electromechanical suspension. The hydraulic-electric conversion structure is composed of a motor and a pump to realize the mutual conversion of hydraulic energy and electrical energy. This shock absorber can realize semi-active control of the suspension and can also realize active control of the suspension. However, the blade-type hydraulic-electric shock absorber with a hydraulic-electric conversion structure also has problems caused by rotational inertia. Summary of the invention

[0008] 1. Technical issues to be resolved

[0009] The technical problem to be solved by the present invention is: how to provide a blade-type hydraulic-electric shock absorber, which absorbs and dissipates the high-frequency vibration of the suspension by setting a low-damping oil-gas buffer shock absorber, thereby reducing the adverse effect of the rotational inertia of the hydraulic-electric conversion structure on the suspension performance and improving the performance of the blade-type hydraulic-electric shock absorber with a hydraulic-electric conversion structure.

[0010] (II) Technical solution

[0011] In order to solve the above technical problems, the present invention provides a blade-type hydraulic shock absorber, such as Figure 1 , Figure 2 , Figure 3 As shown, the blade-type hydraulic-electric shock absorber comprises: a housing assembly (1), a motor pump assembly (2), a blade assembly (3), a partition assembly (4), a first end cover assembly (5), a connecting arm assembly (6), a left-side small oil-gas buffer shock absorber (7), a right-side small oil-gas buffer shock absorber (8), a left-side large oil-gas buffer shock absorber (9), and a right-side large oil-gas buffer shock absorber (10);

[0012] The front side of the shell (1) is provided with a cylindrical cavity, and the blade assembly (3) and the partition assembly (4) are arranged in the cylindrical cavity; the blade assembly (3) and the partition assembly (4) divide the cylindrical cavity into a first cavity (A), a second cavity (B), a third cavity (D) and a fourth cavity (C) which are arranged in a clockwise direction; wherein the first cavity (A) and the fourth cavity (C) constitute a left half cavity, and the second cavity (B) and the third cavity (D) constitute a right half cavity; wherein, as the blade assembly (3) rotates around the axis in an integrated manner, the first cavity (A) and the third cavity (D) are synchronously enlarged or reduced, and correspondingly, the fourth cavity (C) and the second cavity (B) are synchronously reduced or enlarged;

[0013] The blade assembly (3) is provided with a first connecting hole and a second connecting hole, the first cavity (A) and the third cavity (D) are connected through the first connecting hole, and the fourth cavity (C) and the second cavity (B) are connected through the second connecting hole;

[0014] A vibration damping valve mounting hole is respectively provided on both ends of the partition assembly (4), and two vibration damping valves are mounted on the vibration damping valve mounting holes; wherein the two vibration damping valves are divided into a first vibration damping valve and a second vibration damping valve; the first vibration damping valve is connected to the first cavity (A) and the second cavity (B); the second vibration damping valve is connected to the third cavity (D) and the fourth cavity (C);

[0015] like Figure 6As shown, the electric pump assembly (2) comprises a hydraulic pump (201), a motor (202), a rotor connecting sleeve (203), and a second end cover assembly (204); wherein the hydraulic pump (201) is provided with a first oil port (201A) and a second oil port (201B); the rotor connecting sleeve (203) connects the input and output shafts (201C) of the hydraulic pump (201) and the rotor (202A) of the motor (202);

[0016] like Figure 4 As shown, the housing assembly (1) is provided with a first hole (101) at a position corresponding to the first oil port (201A) of the electric pump assembly (2), and the housing (1) is provided with a second hole (102) at a position corresponding to the second oil port (201B) of the electric pump assembly (2);

[0017] The back of the housing (1) is provided with a first cylindrical cavity (105) with threads, a second cylindrical cavity (106), a third cylindrical cavity (107), and a fourth cylindrical cavity (108); the first cylindrical cavity (105) with threads is connected to the small oil-gas buffer shock absorber (7) on the left side through threads, the second cylindrical cavity (106) with threads is connected to the small oil-gas buffer shock absorber (8) on the right side, the third cylindrical cavity (107) with threads is connected to the large oil-gas buffer shock absorber (9) on the left side through threads, and the fourth cylindrical cavity (108) with threads is connected to the large oil-gas buffer shock absorber (10) on the right side; the first cylindrical cavity (105) and the third cylindrical cavity (107) are connected through a third hole (103), and the second cylindrical cavity (106) and the fourth cylindrical cavity (108) are connected through a fourth hole (104);

[0018] Furthermore, the first hole (101) is connected to the third hole (103), and the second hole (102) is connected to the fourth hole (104);

[0019] like Figure 5 As shown, the left small oil-gas buffer shock absorber (7) comprises: a first cylinder body (701), a first damping valve (702), a first floating piston (703), a first sealing end cover (704), a first inflation valve (705), and a first locking nut (706); the first damping valve (702), the first floating piston (703), and the first sealing end cover (704) are arranged in the axial direction inside the first cylinder body (701); wherein a first oil chamber (7Y) is formed between the first damping valve (702) and the first floating piston (703), and a first air chamber (7Q) is formed between the first floating piston (703) and the first sealing end cover (704);

[0020] The right small oil-gas buffer shock absorber (8) comprises: a second cylinder body (801), a second damping valve (802), a second floating piston (803), a second sealing end cover (804), a second inflation valve (805), and a second locking nut (806); the second damping valve (802), the second floating piston (803), and the second sealing end cover (804) are arranged in the axial direction inside the second cylinder body (801); a second oil chamber (8Y) is formed between the second damping valve (802) and the second floating piston (803), and a second air chamber (8Q) is formed between the second floating piston (803) and the second sealing end cover (804);

[0021] The left large oil-gas buffer shock absorber (9) comprises: a third cylinder body (901), a third damping valve (902), a third floating piston (903), a third sealing end cover (904), a third inflation valve (905), and a third locking nut (906); the third damping valve (902), the third floating piston (903), and the third sealing end cover (904) are arranged in the axial direction inside the third cylinder body (901); a third oil chamber (9Y) is formed between the third damping valve (902) and the third floating piston (903), and a third air chamber (9Q) is formed between the third floating piston (903) and the third sealing end cover (904);

[0022] The right large oil-gas buffer shock absorber (10) comprises: a fourth cylinder body (1001), a fourth damping valve (1002), a fourth floating piston (1003), a fourth sealing end cover (1004), a fourth inflation valve (1005), and a fourth locking nut (1006); inside the fourth cylinder body (1001), the fourth damping valve (1002), the fourth floating piston (1003), and the fourth sealing end cover (1004) are arranged one by one along the axial direction; wherein a fourth oil chamber (10Y) is formed between the fourth damping valve (1002) and the fourth floating piston (1003), and a fourth air chamber (10Q) is formed between the fourth floating piston (1003) and the fourth sealing end cover (1004).

[0023] The partition assembly (4) is fixedly connected in the cylindrical cavity through the axis, thereby dividing the cylindrical cavity into two equal parts, defined as a left half cavity and a right half cavity; the blade assembly (3) is rotatably arranged in the cylindrical cavity through the axis, a part of the blade assembly (3) is placed in the left half cavity, and the other part is placed in the right half cavity, so that the blade assembly (3) and the partition assembly (4) divide the cylindrical cavity into a first cavity (A), a second cavity (B), a third cavity (D) and a fourth cavity (C) distributed in a clockwise direction.

[0024] like Figure 1As shown, the electric pump assembly (2) is used to convert the hydraulic energy inside the small oil-gas buffer shock absorber (7) on the left, the small oil-gas buffer shock absorber (8) on the right, the large oil-gas buffer shock absorber (9) on the left, and the large oil-gas buffer shock absorber (10) on the right into electrical energy, which is output by the motor and absorbs vibration energy through an external dissipation resistor or an energy recovery device. By controlling the dissipation resistor or the energy recovery device, the function of the semi-active suspension can be realized; on the other hand, under the premise of the active work of the motor, the motor drives the hydraulic pump to rotate, thereby converting electrical energy into hydraulic energy, driving the connecting arm assembly (6) to rotate, and realizing active vibration reduction of the suspension.

[0025] The sum of the damping coefficients of the first damping valve (702), the first damping valve (702), the first damping valve (702), and the first damping valve (702) is smaller than the damping coefficients of the first vibration reduction valve and the second vibration reduction valve.

[0026] like Figure 2 , Figure 3 As shown, the connecting arm assembly (6) is connected to the blade assembly (3) via a spline; the first end cover assembly (5) is connected to the partition assembly (4) via screws, and the partition assembly (4) is fixed to the shell assembly (1), while also playing the role of sealing the oil.

[0027] like Figure 7 As shown, in actual application, the blade-type hydraulic shock absorber (Y3) is installed on the vehicle body (Y1); the connecting arm assembly (6) of the blade-type hydraulic shock absorber (Y3) is connected to one end of the connecting rod (Y4), and the other end of the connecting rod (Y4) is connected to the balancing elbow (Y5); one end of the balancing elbow (Y5) is fixedly connected to the torsion bar (Y6) and connected to the vehicle body (Y1) through a bearing, and the other end of the torsion bar (Y6) is fixedly connected to the vehicle body (Y1); the limiter (Y2) is fixed to the vehicle body (Y1) and is used to limit the upward rotation angle of the balancing elbow (Y5), thereby protecting the torsion bar (Y6) and the blade-type hydraulic shock absorber (Y3); the other end of the balancing elbow (Y5) is connected to the load-bearing wheel (Y7); the load-bearing wheel (Y7) is arranged on the crawler (Y8), and the crawler (Y8) is in contact with the ground.

[0028] like Figure 8As shown, during the driving process of the vehicle, the uneven road surface causes the crawler track (Y8) to fluctuate up and down, thereby causing the road wheel (Y7) to vibrate vertically; the vertical vibration of the road wheel (Y7) is transmitted to the torsion bar (Y6) through the balancing elbow (Y5), and the torsion bar (Y6) achieves vibration buffering; at the same time, the vibration of the road wheel (Y7) is transmitted to the connecting rod (Y4) through the balancing elbow (Y5), and the connecting rod (Y4) causes the connecting arm assembly (6) of the blade-type hydraulic shock absorber (Y3) to rotate, thereby causing the blade assembly (3) connected to the connecting arm assembly (6) to rotate, and then the motor (202) of the electric pump assembly (2) is dragged by the hydraulic pump (201), thereby converting the mechanical energy of the suspension vibration into electrical energy;

[0029] When the connecting arm assembly (6) rotates, the oil flows between the first cavity (A), the third cavity (D) and the second cavity (B), the fourth cavity (C). At this time, the first damping valve and the second damping valve play a role in partial suspension damping. When the suspension is actively controlled, the damping effect of the damping valve is conducive to the stability of control.

[0030] Another part of the suspension damping is generated by the electric pump assembly (2); the first hole (101) of the vane-type hydraulic-electric shock absorber (Y2) is connected to the first oil port (201A) of the hydraulic pump (201) of the electric pump assembly (2), and the second hole (102) is connected to the second oil port (201B) of the hydraulic pump (201) of the electric pump assembly (2); and in order to dissipate high-frequency vibration and reduce the adverse effect of the rotational inertia of the electric pump assembly (2) on the suspension during high-frequency vibration, the first cavity (A) and the third cavity (D) are connected to the right small oil-gas buffer shock absorber (8) and the right large oil-gas buffer shock absorber (10) through the fourth hole (104); the second cavity (B) and the fourth cavity (C) are connected to the left small oil-gas buffer shock absorber (7) and the left large oil-gas buffer shock absorber (9) through the third hole (103);

[0031] Thus, when the connecting arm assembly (6) rotates, the oil also enters or flows out of the electric pump assembly (2) through the first hole (101) and the second hole (102), thereby driving the electric pump assembly (2) to rotate, and the motor (202) converts hydraulic energy into electrical energy; the alternating current generated by the motor (202) enters the three-phase rectifier bridge through the three-phase windings ua, ub, uc of the motor (202), and becomes direct current after rectification; the direct current enters the dissipation resistor Rr after passing through the switch tube Dr; the switch tube Dr receives the PWM control signal through the control line Cr, and controls the connection or disconnection of the dissipation resistor Rr under the control of the PWM control signal, thereby adjusting the power consumption of the dissipation resistor Rr, and forming an electromagnetic damping force that hinders the relative movement of the wheel and the vehicle body (Y1); wherein the duty cycle of the PWM control signal determines the conduction time of the dissipation resistor Rr.

[0032] like Figure 2-Figure 6As shown, when the connecting arm assembly (6) rotates upward, the blade assembly (3) rotates clockwise (from Figure 3 The view direction is clockwise), at this time, the first cavity (A) and the third cavity (D) are compressed, the second cavity (B) and the fourth cavity (C) are stretched, and part of the oil flows from the first cavity (A) and the third cavity (D) through the first damping valve and the second damping valve into the second cavity (B) and the fourth cavity (C);

[0033] At the same time, a portion of the oil flows from the third cavity (D) through the fourth hole (104), enters the right small oil-gas buffer shock absorber (8) and the right large oil-gas buffer shock absorber (10), flows through the second damping valve (802) and the fourth damping valve (1002), enters the second oil chamber (8Y) and the fourth oil chamber (10Y), and then pushes the second floating piston (803) and the fourth floating piston (1003), compressing the second air chamber (8Q) and the fourth air chamber (10Q);

[0034] At the same time, the first air chamber (7Q) and the third air chamber (9Q) of the left small oil-gas buffer shock absorber (7) and the left large oil-gas buffer shock absorber (9) are extended, pushing the first floating piston (703) and the third floating piston (903), so that the oil in the first oil chamber (7Y) and the third oil chamber (9Y) enters the fourth cavity (C) through the first damping valve (702) and the third damping valve (902);

[0035] At the same time, a portion of the oil flows from the third cavity (D) through the fourth hole (104) into the second hole (102), and then enters the second oil port (201B) of the hydraulic pump (201), driving the hydraulic pump (201) of the electric pump assembly (2) to rotate. At this time, the hydraulic pump acts as a hydraulic motor, thereby driving the motor (202) to rotate and generate electricity. The generated electricity is dissipated by heat generated by the dissipation resistor Rr, and the oil flows through the first oil port (201A) of the hydraulic pump (201) into the first hole (101), and then enters the third hole (103), and then flows into the fourth cavity (C);

[0036] Since the sum of the damping coefficients of the first damping valve (702), the second damping valve (802), the third damping valve (902) and the fourth damping valve (1002) is smaller than the damping coefficients of the first damping valve and the second damping valve, and the damping force generated by the first damping valve (702), the second damping valve (802), the third damping valve (902) and the fourth damping valve (1002) is smaller than the inertia force generated by the rotational inertia of the electric pump assembly (2), the oil initially passes through the second damping valve (802) and the fourth damping valve (1002) at a relatively large flow rate and enters the second oil chamber (8Y) and the fourth oil chamber (10Y), thereby pushing the second floating piston (803) and the fourth floating piston (1003) and compressing the second air chamber (8Q) and the fourth air chamber (10Q). When the pressure of the second air chamber (8Q) and the fourth air chamber (10Q) increases, the pressure difference before and after the second damping valve (802) and the fourth damping valve (1002) decreases, and the flow rate through the second damping valve (802) and the fourth damping valve (1002) decreases. At this time, the flow rate of oil through the first damping valve, the second damping valve and the hydraulic pump (201) increases; therefore, high-frequency vibration energy will be preferentially absorbed by the second damping valve (802) and the fourth damping valve (1002), thereby facilitating the role of the blade-type shock absorber at the first main frequency, reducing the role of the first damping valve, the second damping valve and the electric pump (2) of the blade-type shock absorber at the second main frequency, thereby reducing the damping force and inertia force at high frequencies, facilitating the reduction of sprung mass acceleration, and reducing suspension energy consumption.

[0037] like Figure 2-Figure 6 As shown, when the connecting arm assembly (6) rotates downward, the blade assembly (3) rotates counterclockwise (from Figure 3 The view direction is counterclockwise), at this time, the first cavity (A) and the third cavity (D) are stretched, the second cavity (B) and the fourth cavity (C) are compressed, and part of the oil flows from the second cavity (B) and the fourth cavity (C) through the first damping valve and the second damping valve into the first cavity (A) and the third cavity (D);

[0038] At the same time, a portion of the oil flows from the fourth cavity (C) through the third hole (103), enters the left small oil-gas buffer shock absorber (7) and the left large oil-gas buffer shock absorber (9), flows through the first damping valve (702) and the third damping valve (902), enters the first oil chamber (7Y) and the third oil chamber (9Y), and then pushes the first floating piston (703) and the third floating piston (903), compressing the first air chamber (7Q) and the third air chamber (9Q);

[0039] At the same time, the second air chamber (8Q) and the fourth air chamber (10Q) of the right small oil-gas buffer shock absorber (8) and the right large oil-gas buffer shock absorber (10) are extended, pushing the second floating piston (803) and the fourth floating piston (1003), so that the oil in the second oil chamber (8Y) and the fourth oil chamber (10Y) enters the third cavity (D) through the second damping valve (802) and the fourth damping valve (1002);

[0040] At the same time, a portion of the oil flows from the fourth cavity (C) through the third hole (103) into the first hole (101), and then enters the first oil port (201A) of the hydraulic pump (201), driving the hydraulic pump (201) of the electric pump assembly (2) to rotate. At this time, the hydraulic pump acts as a hydraulic motor, thereby driving the motor (202) to rotate and generate electricity. The generated electricity is dissipated by heat through the dissipation resistor Rr, and the oil flows through the second oil port (201B) of the hydraulic pump (201) into the second hole (102), and then enters the fourth hole (104), and then flows into the third cavity (D);

[0041] Since the sum of the damping coefficients of the first damping valve (702), the second damping valve (802), the third damping valve (902) and the fourth damping valve (1002) is smaller than the damping coefficients of the first damping valve and the second damping valve, and the damping force generated by the first damping valve (702), the second damping valve (802), the third damping valve (902) and the fourth damping valve (1002) is smaller than the inertia force generated by the rotational inertia of the electric pump assembly (2), the oil initially passes through the first damping valve (702) and the third damping valve (902) at a relatively large flow rate and enters the first oil chamber (7Y) and the third oil chamber (9Y), thereby pushing the first floating piston (703) and the third floating piston (903) and compressing the first air chamber (7Q) and the third air chamber (9Q). When the pressure of the first air chamber (7Q) and the third air chamber (9Q) increases, the pressure difference before and after the first damping valve (702) and the third damping valve (902) decreases, and the flow rate through the first damping valve (702) and the third damping valve (902) decreases. At this time, the flow rate of oil through the first damping valve, the second damping valve and the hydraulic pump (201) increases; therefore, high-frequency vibration energy will be preferentially absorbed by the first damping valve (702) and the third damping valve (902), which is conducive to exerting the role of the blade-type shock absorber at the first main frequency, reducing the role of the first damping valve, the second damping valve and the electric pump (2) of the blade-type shock absorber at the second main frequency, thereby reducing the damping force and inertia force at high frequencies, which is conducive to reducing the acceleration of the sprung mass and reducing the energy consumption of the suspension.

[0042] Wherein, the blade-type hydraulic shock absorber further comprises: a first oil pressure sensor (11), a second oil pressure sensor (12);

[0043] like Figure 2As shown, the first oil pressure sensor (11) is used to measure the oil pressure of the left small oil-gas buffer shock absorber (7), the left large oil-gas buffer shock absorber (9) and the change of the oil pressure on the left side of the electric pump assembly (2); the second oil pressure sensor (12) is used to measure the oil pressure of the right small oil-gas buffer shock absorber (8) and the right large oil-gas buffer shock absorber (10) and the change of the oil pressure on the right side of the electric pump assembly (2).

[0044] (III) Beneficial effects

[0045] Compared with the prior art, the beneficial effects of the present invention are: low-pass filtering of random vibration transmitted by the wheel is achieved through the oil-gas buffer shock absorber, most of the high-frequency vibration is dissipated by the buffer and vibration reduction structure with small damping, which is conducive to reducing the adverse effect of the rotational inertia of the liquid-electric conversion structure (electric pump) on the suspension vibration reduction performance, and improving the smoothness of the vehicle body (sprung mass). BRIEF DESCRIPTION OF THE DRAWINGS

[0046] Figure 1 This is the section of the blade-type hydraulic shock absorber;

[0047] Figure 2 Outline drawing of blade type hydraulic shock absorber;

[0048] Figure 3 Cavity section of blade-type hydraulic shock absorber;

[0049] Figure 4 Shell assembly structure;

[0050] Figure 5 Oil-gas buffer shock absorber assembly structure;

[0051] Figure 6 Electric pump assembly structure;

[0052] Figure 7 Schematic diagram of electromechanical suspension application based on blade-type hydraulic shock absorber;

[0053] Figure 8 Damping coefficient control principle of blade-type hydraulic-electric shock absorber.

[0054] In the figure: 401 is a vibration reduction valve. DETAILED DESCRIPTION

[0055] In order to make the purpose, content, and advantages of the present invention more clear, the specific implementation methods of the present invention are further described in detail below in conjunction with the accompanying drawings and examples.

[0056] Example 1

[0057] The practical application of the blade-type hydraulic shock absorber of this embodiment is as follows: Figure 7As shown, the present invention absorbs and dissipates the high-frequency vibration of the suspension by setting a low-damping oil-gas buffer shock absorber, thereby reducing the adverse effect of the rotational inertia of the liquid-electric conversion structure on the suspension performance and improving the performance of the blade-type liquid-electric shock absorber with a liquid-electric conversion structure.

[0058] Specifically, if Figure 1 , Figure 2 , Figure 3 As shown, the blade-type hydraulic-electric shock absorber provided by the present invention comprises: a housing assembly (1), a motor pump assembly (2), a blade assembly (3), a partition assembly (4), a first end cover assembly (5), a connecting arm assembly (6), a left-side small oil-gas buffer shock absorber (7), a right-side small oil-gas buffer shock absorber (8), a left-side large oil-gas buffer shock absorber (9), and a right-side large oil-gas buffer shock absorber (10);

[0059] The front side of the shell (1) is provided with a cylindrical cavity, and the blade assembly (3) and the partition assembly (4) are arranged in the cylindrical cavity; the blade assembly (3) and the partition assembly (4) divide the cylindrical cavity into a first cavity (A), a second cavity (B), a third cavity (D) and a fourth cavity (C) which are arranged in a clockwise direction; wherein the first cavity (A) and the fourth cavity (C) constitute a left half cavity, and the second cavity (B) and the third cavity (D) constitute a right half cavity; wherein, as the blade assembly (3) rotates around the axis in an integrated manner, the first cavity (A) and the third cavity (D) are synchronously enlarged or reduced, and correspondingly, the fourth cavity (C) and the second cavity (B) are synchronously reduced or enlarged;

[0060] The blade assembly (3) is provided with a first connecting hole and a second connecting hole, the first cavity (A) and the third cavity (D) are connected through the first connecting hole, and the fourth cavity (C) and the second cavity (B) are connected through the second connecting hole;

[0061] A vibration damping valve mounting hole is respectively provided on both ends of the partition assembly (4), and two vibration damping valves are mounted on the vibration damping valve mounting holes; wherein the two vibration damping valves are divided into a first vibration damping valve and a second vibration damping valve; the first vibration damping valve is connected to the first cavity (A) and the second cavity (B); the second vibration damping valve is connected to the third cavity (D) and the fourth cavity (C);

[0062] like Figure 6 As shown, the electric pump assembly (2) comprises a hydraulic pump (201), a motor (202), a rotor connecting sleeve (203), and a second end cover assembly (204); wherein the hydraulic pump (201) is provided with a first oil port (201A) and a second oil port (201B); the rotor connecting sleeve (203) connects the input and output shafts (201C) of the hydraulic pump (201) and the rotor (202A) of the motor (202);

[0063] like Figure 4 As shown, the housing assembly (1) is provided with a first hole (101) at a position corresponding to the first oil port (201A) of the electric pump assembly (2), and the housing (1) is provided with a second hole (102) at a position corresponding to the second oil port (201B) of the electric pump assembly (2);

[0064] The back of the housing (1) is provided with a first cylindrical cavity (105) with threads, a second cylindrical cavity (106), a third cylindrical cavity (107), and a fourth cylindrical cavity (108); the first cylindrical cavity (105) with threads is connected to the small oil-gas buffer shock absorber (7) on the left side through threads, the second cylindrical cavity (106) with threads is connected to the small oil-gas buffer shock absorber (8) on the right side, the third cylindrical cavity (107) with threads is connected to the large oil-gas buffer shock absorber (9) on the left side through threads, and the fourth cylindrical cavity (108) with threads is connected to the large oil-gas buffer shock absorber (10) on the right side; the first cylindrical cavity (105) and the third cylindrical cavity (107) are connected through a third hole (103), and the second cylindrical cavity (106) and the fourth cylindrical cavity (108) are connected through a fourth hole (104);

[0065] Furthermore, the first hole (101) is connected to the third hole (103), and the second hole (102) is connected to the fourth hole (104);

[0066] like Figure 5 As shown, the left small oil-gas buffer shock absorber (7) comprises: a first cylinder body (701), a first damping valve (702), a first floating piston (703), a first sealing end cover (704), a first inflation valve (705), and a first locking nut (706); the first damping valve (702), the first floating piston (703), and the first sealing end cover (704) are arranged in the axial direction inside the first cylinder body (701); wherein a first oil chamber (7Y) is formed between the first damping valve (702) and the first floating piston (703), and a first air chamber (7Q) is formed between the first floating piston (703) and the first sealing end cover (704);

[0067] The right small oil-gas buffer shock absorber (8) comprises: a second cylinder body (801), a second damping valve (802), a second floating piston (803), a second sealing end cover (804), a second inflation valve (805), and a second locking nut (806); the second damping valve (802), the second floating piston (803), and the second sealing end cover (804) are arranged in the axial direction inside the second cylinder body (801); a second oil chamber (8Y) is formed between the second damping valve (802) and the second floating piston (803), and a second air chamber (8Q) is formed between the second floating piston (803) and the second sealing end cover (804);

[0068] The left large oil-gas buffer shock absorber (9) comprises: a third cylinder body (901), a third damping valve (902), a third floating piston (903), a third sealing end cover (904), a third inflation valve (905), and a third locking nut (906); the third damping valve (902), the third floating piston (903), and the third sealing end cover (904) are arranged in the axial direction inside the third cylinder body (901); a third oil chamber (9Y) is formed between the third damping valve (902) and the third floating piston (903), and a third air chamber (9Q) is formed between the third floating piston (903) and the third sealing end cover (904);

[0069] The right large oil-gas buffer shock absorber (10) comprises: a fourth cylinder body (1001), a fourth damping valve (1002), a fourth floating piston (1003), a fourth sealing end cover (1004), a fourth inflation valve (1005), and a fourth locking nut (1006); inside the fourth cylinder body (1001), the fourth damping valve (1002), the fourth floating piston (1003), and the fourth sealing end cover (1004) are arranged one by one along the axial direction; wherein a fourth oil chamber (10Y) is formed between the fourth damping valve (1002) and the fourth floating piston (1003), and a fourth air chamber (10Q) is formed between the fourth floating piston (1003) and the fourth sealing end cover (1004).

[0070] The partition assembly (4) is fixedly connected in the cylindrical cavity through the axis, thereby dividing the cylindrical cavity into two equal parts, defined as a left half cavity and a right half cavity; the blade assembly (3) is rotatably arranged in the cylindrical cavity through the axis, a part of the blade assembly (3) is placed in the left half cavity, and the other part is placed in the right half cavity, so that the blade assembly (3) and the partition assembly (4) divide the cylindrical cavity into a first cavity (A), a second cavity (B), a third cavity (D) and a fourth cavity (C) distributed in a clockwise direction.

[0071] like Figure 1 As shown, the electric pump assembly (2) is used to convert the hydraulic energy inside the small oil-gas buffer shock absorber (7) on the left, the small oil-gas buffer shock absorber (8) on the right, the large oil-gas buffer shock absorber (9) on the left, and the large oil-gas buffer shock absorber (10) on the right into electrical energy, which is output by the motor and absorbs vibration energy through an external dissipation resistor or an energy recovery device. By controlling the dissipation resistor or the energy recovery device, the function of the semi-active suspension can be realized; on the other hand, under the premise of the active work of the motor, the motor drives the hydraulic pump to rotate, thereby converting electrical energy into hydraulic energy, driving the connecting arm assembly (6) to rotate, and realizing active vibration reduction of the suspension.

[0072] The sum of the damping coefficients of the first damping valve (702), the first damping valve (702), the first damping valve (702), and the first damping valve (702) is smaller than the damping coefficients of the first vibration reduction valve and the second vibration reduction valve.

[0073] like Figure 2 , Figure 3 As shown, the connecting arm assembly (6) is connected to the blade assembly (3) via a spline; the first end cover assembly (5) is connected to the partition assembly (4) via screws, and the partition assembly (4) is fixed to the shell assembly (1), while also playing the role of sealing the oil.

[0074] like Figure 7 As shown, in actual application, the blade-type hydraulic shock absorber (Y3) is installed on the vehicle body (Y1); the connecting arm assembly (6) of the blade-type hydraulic shock absorber (Y3) is connected to one end of the connecting rod (Y4), and the other end of the connecting rod (Y4) is connected to the balancing elbow (Y5); one end of the balancing elbow (Y5) is fixedly connected to the torsion bar (Y6) and connected to the vehicle body (Y1) through a bearing, and the other end of the torsion bar (Y6) is fixedly connected to the vehicle body (Y1); the limiter (Y2) is fixed to the vehicle body (Y1) and is used to limit the upward rotation angle of the balancing elbow (Y5), thereby protecting the torsion bar (Y6) and the blade-type hydraulic shock absorber (Y3); the other end of the balancing elbow (Y5) is connected to the load-bearing wheel (Y7); the load-bearing wheel (Y7) is arranged on the crawler (Y8), and the crawler (Y8) is in contact with the ground.

[0075] like Figure 8 As shown, during the driving process of the vehicle, the uneven road surface causes the crawler track (Y8) to fluctuate up and down, thereby causing the road wheel (Y7) to vibrate vertically; the vertical vibration of the road wheel (Y7) is transmitted to the torsion bar (Y6) through the balancing elbow (Y5), and the torsion bar (Y6) achieves vibration buffering; at the same time, the vibration of the road wheel (Y7) is transmitted to the connecting rod (Y4) through the balancing elbow (Y5), and the connecting rod (Y4) causes the connecting arm assembly (6) of the blade-type hydraulic shock absorber (Y3) to rotate, thereby causing the blade assembly (3) connected to the connecting arm assembly (6) to rotate, and then the motor (202) of the electric pump assembly (2) is dragged by the hydraulic pump (201), thereby converting the mechanical energy of the suspension vibration into electrical energy;

[0076] When the connecting arm assembly (6) rotates, the oil flows between the first cavity (A), the third cavity (D) and the second cavity (B), the fourth cavity (C). At this time, the first damping valve and the second damping valve play a role in partial suspension damping. When the suspension is actively controlled, the damping effect of the damping valve is conducive to the stability of control.

[0077] Another part of the suspension damping is generated by the electric pump assembly (2); the first hole (101) of the vane-type hydraulic-electric shock absorber (Y2) is connected to the first oil port (201A) of the hydraulic pump (201) of the electric pump assembly (2), and the second hole (102) is connected to the second oil port (201B) of the hydraulic pump (201) of the electric pump assembly (2); and in order to dissipate high-frequency vibration and reduce the adverse effect of the rotational inertia of the electric pump assembly (2) on the suspension during high-frequency vibration, the first cavity (A) and the third cavity (D) are connected to the right small oil-gas buffer shock absorber (8) and the right large oil-gas buffer shock absorber (10) through the fourth hole (104); the second cavity (B) and the fourth cavity (C) are connected to the left small oil-gas buffer shock absorber (7) and the left large oil-gas buffer shock absorber (9) through the third hole (103);

[0078] Thus, when the connecting arm assembly (6) rotates, the oil also enters or flows out of the electric pump assembly (2) through the first hole (101) and the second hole (102), thereby driving the electric pump assembly (2) to rotate, and the motor (202) converts hydraulic energy into electrical energy; the alternating current generated by the motor (202) enters the three-phase rectifier bridge through the three-phase windings ua, ub, uc of the motor (202), and becomes direct current after rectification; the direct current enters the dissipation resistor Rr after passing through the switch tube Dr; the switch tube Dr receives the PWM control signal through the control line Cr, and controls the connection or disconnection of the dissipation resistor Rr under the control of the PWM control signal, thereby adjusting the power consumption of the dissipation resistor Rr, and forming an electromagnetic damping force that hinders the relative movement of the wheel and the vehicle body (Y1); wherein the duty cycle of the PWM control signal determines the conduction time of the dissipation resistor Rr.

[0079] like Figure 2-Figure 6 As shown, when the connecting arm assembly (6) rotates upward, the blade assembly (3) rotates clockwise (from Figure 3 The view direction is clockwise), at this time, the first cavity (A) and the third cavity (D) are compressed, the second cavity (B) and the fourth cavity (C) are stretched, and part of the oil flows from the first cavity (A) and the third cavity (D) through the first damping valve and the second damping valve into the second cavity (B) and the fourth cavity (C);

[0080] At the same time, a portion of the oil flows from the third cavity (D) through the fourth hole (104), enters the right small oil-gas buffer shock absorber (8) and the right large oil-gas buffer shock absorber (10), flows through the second damping valve (802) and the fourth damping valve (1002), enters the second oil chamber (8Y) and the fourth oil chamber (10Y), and then pushes the second floating piston (803) and the fourth floating piston (1003), compressing the second air chamber (8Q) and the fourth air chamber (10Q);

[0081] At the same time, the first air chamber (7Q) and the third air chamber (9Q) of the left small oil-gas buffer shock absorber (7) and the left large oil-gas buffer shock absorber (9) are extended, pushing the first floating piston (703) and the third floating piston (903), so that the oil in the first oil chamber (7Y) and the third oil chamber (9Y) enters the fourth cavity (C) through the first damping valve (702) and the third damping valve (902);

[0082] At the same time, a portion of the oil flows from the third cavity (D) through the fourth hole (104) into the second hole (102), and then enters the second oil port (201B) of the hydraulic pump (201), driving the hydraulic pump (201) of the electric pump assembly (2) to rotate. At this time, the hydraulic pump acts as a hydraulic motor, thereby driving the motor (202) to rotate and generate electricity. The generated electricity is dissipated by heat generated by the dissipation resistor Rr, and the oil flows through the first oil port (201A) of the hydraulic pump (201) into the first hole (101), and then enters the third hole (103), and then flows into the fourth cavity (C);

[0083] Since the sum of the damping coefficients of the first damping valve (702), the second damping valve (802), the third damping valve (902) and the fourth damping valve (1002) is smaller than the damping coefficients of the first damping valve and the second damping valve, and the damping force generated by the first damping valve (702), the second damping valve (802), the third damping valve (902) and the fourth damping valve (1002) is smaller than the inertia force generated by the rotational inertia of the electric pump assembly (2), the oil initially passes through the second damping valve (802) and the fourth damping valve (1002) at a relatively large flow rate and enters the second oil chamber (8Y) and the fourth oil chamber (10Y), thereby pushing the second floating piston (803) and the fourth floating piston (1003) and compressing the second air chamber (8Q) and the fourth air chamber (10Q). When the pressure of the second air chamber (8Q) and the fourth air chamber (10Q) increases, the pressure difference before and after the second damping valve (802) and the fourth damping valve (1002) decreases, and the flow rate through the second damping valve (802) and the fourth damping valve (1002) decreases. At this time, the flow rate of oil through the first damping valve, the second damping valve and the hydraulic pump (201) increases; therefore, high-frequency vibration energy will be preferentially absorbed by the second damping valve (802) and the fourth damping valve (1002), thereby facilitating the role of the blade-type shock absorber at the first main frequency, reducing the role of the first damping valve, the second damping valve and the electric pump (2) of the blade-type shock absorber at the second main frequency, thereby reducing the damping force and inertia force at high frequencies, facilitating the reduction of sprung mass acceleration, and reducing suspension energy consumption.

[0084] like Figure 2-Figure 6 As shown, when the connecting arm assembly (6) rotates downward, the blade assembly (3) rotates counterclockwise (from Figure 3The view direction is counterclockwise), at this time, the first cavity (A) and the third cavity (D) are stretched, the second cavity (B) and the fourth cavity (C) are compressed, and part of the oil flows from the second cavity (B) and the fourth cavity (C) through the first damping valve and the second damping valve into the first cavity (A) and the third cavity (D);

[0085] At the same time, a portion of the oil flows from the fourth cavity (C) through the third hole (103), enters the left small oil-gas buffer shock absorber (7) and the left large oil-gas buffer shock absorber (9), flows through the first damping valve (702) and the third damping valve (902), enters the first oil chamber (7Y) and the third oil chamber (9Y), and then pushes the first floating piston (703) and the third floating piston (903), compressing the first air chamber (7Q) and the third air chamber (9Q);

[0086] At the same time, the second air chamber (8Q) and the fourth air chamber (10Q) of the right small oil-gas buffer shock absorber (8) and the right large oil-gas buffer shock absorber (10) are extended, pushing the second floating piston (803) and the fourth floating piston (1003), so that the oil in the second oil chamber (8Y) and the fourth oil chamber (10Y) enters the third cavity (D) through the second damping valve (802) and the fourth damping valve (1002);

[0087] At the same time, a portion of the oil flows from the fourth cavity (C) through the third hole (103) into the first hole (101), and then enters the first oil port (201A) of the hydraulic pump (201), driving the hydraulic pump (201) of the electric pump assembly (2) to rotate. At this time, the hydraulic pump acts as a hydraulic motor, thereby driving the motor (202) to rotate and generate electricity. The generated electricity is dissipated by heat through the dissipation resistor Rr, and the oil flows through the second oil port (201B) of the hydraulic pump (201) into the second hole (102), and then enters the fourth hole (104), and then flows into the third cavity (D);

[0088] Since the sum of the damping coefficients of the first damping valve (702), the second damping valve (802), the third damping valve (902) and the fourth damping valve (1002) is smaller than the damping coefficients of the first damping valve and the second damping valve, and the damping force generated by the first damping valve (702), the second damping valve (802), the third damping valve (902) and the fourth damping valve (1002) is smaller than the inertia force generated by the rotational inertia of the electric pump assembly (2), the oil initially passes through the first damping valve (702) and the third damping valve (902) at a relatively large flow rate and enters the first oil chamber (7Y) and the third oil chamber (9Y), thereby pushing the first floating piston (703) and the third floating piston (903) and compressing the first air chamber (7Q) and the third air chamber (9Q). When the pressure of the first air chamber (7Q) and the third air chamber (9Q) increases, the pressure difference before and after the first damping valve (702) and the third damping valve (902) decreases, and the flow rate through the first damping valve (702) and the third damping valve (902) decreases. At this time, the flow rate of oil through the first damping valve, the second damping valve and the hydraulic pump (201) increases; therefore, high-frequency vibration energy will be preferentially absorbed by the first damping valve (702) and the third damping valve (902), which is conducive to exerting the role of the blade-type shock absorber at the first main frequency, reducing the role of the first damping valve, the second damping valve and the electric pump (2) of the blade-type shock absorber at the second main frequency, thereby reducing the damping force and inertia force at high frequencies, which is conducive to reducing the acceleration of the sprung mass and reducing the energy consumption of the suspension.

[0089] Wherein, the blade-type hydraulic shock absorber further comprises: a first oil pressure sensor (11), a second oil pressure sensor (12);

[0090] like Figure 2 As shown, the first oil pressure sensor (11) is used to measure the oil pressure of the left small oil-gas buffer shock absorber (7), the left large oil-gas buffer shock absorber (9) and the change of the oil pressure on the left side of the electric pump assembly (2); the second oil pressure sensor (12) is used to measure the oil pressure of the right small oil-gas buffer shock absorber (8) and the right large oil-gas buffer shock absorber (10) and the change of the oil pressure on the right side of the electric pump assembly (2).

[0091] The above is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the technical principles of the present invention. These improvements and modifications should also be regarded as the scope of protection of the present invention.

Claims

1. A blade-type hydraulic shock absorber, characterized in that: The vane-type hydraulic-electric shock absorber comprises: a housing assembly (1), a motor pump assembly (2), a vane assembly (3), a partition assembly (4), a first end cover assembly (5), a connecting arm assembly (6), a left-side small oil-gas buffer shock absorber (7), a right-side small oil-gas buffer shock absorber (8), a left-side large oil-gas buffer shock absorber (9), and a right-side large oil-gas buffer shock absorber (10); The front side of the shell (1) is provided with a cylindrical cavity, and the blade assembly (3) and the partition assembly (4) are arranged in the cylindrical cavity; the blade assembly (3) and the partition assembly (4) divide the cylindrical cavity into a first cavity (A), a second cavity (B), a third cavity (D) and a fourth cavity (C) which are arranged in a clockwise direction; wherein the first cavity (A) and the fourth cavity (C) constitute a left half cavity, and the second cavity (B) and the third cavity (D) constitute a right half cavity; wherein, as the blade assembly (3) rotates around the axis in an integrated manner, the first cavity (A) and the third cavity (D) are synchronously enlarged or reduced, and correspondingly, the fourth cavity (C) and the second cavity (B) are synchronously reduced or enlarged; The blade assembly (3) is provided with a first connecting hole and a second connecting hole, the first cavity (A) and the third cavity (D) are connected through the first connecting hole, and the fourth cavity (C) and the second cavity (B) are connected through the second connecting hole; A vibration damping valve mounting hole is respectively provided on both ends of the partition assembly (4), and two vibration damping valves are mounted on the vibration damping valve mounting holes; wherein the two vibration damping valves are divided into a first vibration damping valve and a second vibration damping valve; the first vibration damping valve is connected to the first cavity (A) and the second cavity (B); the second vibration damping valve is connected to the third cavity (D) and the fourth cavity (C); The electric pump assembly (2) comprises a hydraulic pump (201), a motor (202), and a rotor connecting sleeve (203); wherein the hydraulic pump (201) is provided with a first oil port (201A) and a second oil port (201B); and the rotor connecting sleeve (203) connects the input and output shafts (201C) of the hydraulic pump (201) and the rotor (202A) of the motor (202); The housing assembly (1) is provided with a first hole (101) at a position corresponding to the first oil port (201A) of the electric pump assembly (2), and a second hole (102) is provided at a position corresponding to the second oil port (201B) of the electric pump assembly (2); The back of the housing (1) is provided with a first cylindrical cavity (105) with threads, a second cylindrical cavity (106), a third cylindrical cavity (107), and a fourth cylindrical cavity (108); the first cylindrical cavity (105) with threads is connected to the small oil-gas buffer shock absorber (7) on the left side through threads, the second cylindrical cavity (106) with threads is connected to the small oil-gas buffer shock absorber (8) on the right side, the third cylindrical cavity (107) with threads is connected to the large oil-gas buffer shock absorber (9) on the left side through threads, and the fourth cylindrical cavity (108) with threads is connected to the large oil-gas buffer shock absorber (10) on the right side; the first cylindrical cavity (105) and the third cylindrical cavity (107) are connected through a third hole (103), and the second cylindrical cavity (106) and the fourth cylindrical cavity (108) are connected through a fourth hole (104); Furthermore, the first hole (101) is connected to the third hole (103), and the second hole (102) is connected to the fourth hole (104); The left-side small oil-gas buffer shock absorber (7) comprises: a first cylinder body (701), a first damping valve (702), a first floating piston (703), and a first sealing end cover (704); the first damping valve (702), the first floating piston (703), and the first sealing end cover (704) are arranged in the first cylinder body (701) along the axial direction; wherein a first oil chamber (7Y) is formed between the first damping valve (702) and the first floating piston (703), and a first air chamber (7Q) is formed between the first floating piston (703) and the first sealing end cover (704); The right small oil-gas buffer shock absorber (8) comprises: a second cylinder body (801), a second damping valve (802), a second floating piston (803), and a second sealing end cover (804); the second damping valve (802), the second floating piston (803), and the second sealing end cover (804) are arranged in the axial direction inside the second cylinder body (801); a second oil chamber (8Y) is formed between the second damping valve (802) and the second floating piston (803), and a second air chamber (8Q) is formed between the second floating piston (803) and the second sealing end cover (804); The left large oil-gas buffer shock absorber (9) comprises: a third cylinder body (901), a third damping valve (902), a third floating piston (903), and a third sealing end cover (904); the third damping valve (902), the third floating piston (903), and the third sealing end cover (904) are arranged in the axial direction inside the third cylinder body (901); a third oil chamber (9Y) is formed between the third damping valve (902) and the third floating piston (903), and a third air chamber (9Q) is formed between the third floating piston (903) and the third sealing end cover (904); The right large oil-gas buffer shock absorber (10) comprises: a fourth cylinder body (1001), a fourth damping valve (1002), a fourth floating piston (1003), and a fourth sealing end cover (1004); inside the fourth cylinder body (1001), the fourth damping valve (1002), the fourth floating piston (1003), and the fourth sealing end cover (1004) are arranged one by one along the axial direction; wherein a fourth oil chamber (10Y) is formed between the fourth damping valve (1002) and the fourth floating piston (1003), and a fourth air chamber (10Q) is formed between the fourth floating piston (1003) and the fourth sealing end cover (1004).

2. The blade-type hydraulic shock absorber according to claim 1, characterized in that: The partition assembly (4) is fixedly connected in the cylindrical cavity through the axis, thereby dividing the cylindrical cavity into two equal parts, defined as a left half cavity and a right half cavity; the blade assembly (3) is rotatably arranged in the cylindrical cavity through the axis, a part of the blade assembly (3) is placed in the left half cavity, and the other part is placed in the right half cavity, so that the blade assembly (3) and the partition assembly (4) divide the cylindrical cavity into a first cavity (A), a second cavity (B), a third cavity (D) and a fourth cavity (C) distributed in a clockwise direction.

3. The blade-type hydraulic shock absorber according to claim 2, characterized in that: The electric pump assembly (2) is used to convert the hydraulic energy inside the left small oil-gas buffer shock absorber (7), the right small oil-gas buffer shock absorber (8), the left large oil-gas buffer shock absorber (9), and the right large oil-gas buffer shock absorber (10) into electrical energy, which is output by the motor and absorbed by the external dissipation resistor or the electric energy recovery device. By controlling the dissipation resistor or the electric energy recovery device, the function of the semi-active suspension can be realized; on the other hand, under the premise of the active work of the motor, the motor drives the hydraulic pump to rotate, thereby converting the electrical energy into hydraulic energy, driving the connecting arm assembly (6) to rotate, and realizing the active vibration reduction of the suspension.

4. The blade-type hydraulic shock absorber according to claim 3, characterized in that: The sum of the damping coefficients of the first damping valve (702), the first damping valve (702), the first damping valve (702), and the first damping valve (702) is smaller than the damping coefficients of the first vibration reduction valve and the second vibration reduction valve.

5. The blade-type hydraulic shock absorber according to claim 4, characterized in that: The connecting arm assembly (6) is connected to the blade assembly (3) via a spline; the first end cover assembly (5) is connected to the partition assembly (4), and the partition assembly (4) is fixedly connected to the shell assembly (1), and at the same time plays a role in sealing oil.

6. The blade-type hydraulic shock absorber according to claim 5, characterized in that: In practical application, the blade-type hydraulic shock absorber (Y3) is installed on the vehicle body (Y1); the connecting arm assembly (6) of the blade-type hydraulic shock absorber (Y3) is connected to one end of the connecting rod (Y4), and the other end of the connecting rod (Y4) is connected to the balancing elbow (Y5); one end of the balancing elbow (Y5) is fixedly connected to the torsion bar (Y6) and connected to the vehicle body (Y1) through a bearing, and the other end of the torsion bar (Y6) is fixedly connected to the vehicle body (Y1); the limiter (Y2) is fixed to the vehicle body (Y1) and is used to limit the upward rotation angle of the balancing elbow (Y5), thereby protecting the torsion bar (Y6) and the blade-type hydraulic shock absorber (Y3); the other end of the balancing elbow (Y5) is connected to the load-bearing wheel (Y7); the load-bearing wheel (Y7) is arranged on the crawler (Y8), and the crawler (Y8) is in contact with the ground.

7. The blade-type hydraulic shock absorber according to claim 6, characterized in that: During the driving process of the vehicle, the uneven road surface causes the crawler track (Y8) to fluctuate up and down, thereby causing the road wheel (Y7) to vibrate vertically; the vertical vibration of the road wheel (Y7) is transmitted to the torsion bar (Y6) through the balancing elbow (Y5), and the torsion bar (Y6) achieves vibration buffering; at the same time, the vibration of the road wheel (Y7) is transmitted to the connecting rod (Y4) through the balancing elbow (Y5), and the connecting rod (Y4) causes the connecting arm assembly (6) of the blade-type hydraulic shock absorber (Y3) to rotate, thereby causing the blade assembly (3) connected to the connecting arm assembly (6) to rotate, and then the motor (202) of the electric pump assembly (2) is dragged by the hydraulic pump (201), thereby converting the mechanical energy of the suspension vibration into electrical energy; When the connecting arm assembly (6) rotates, the oil flows between the first cavity (A), the third cavity (D) and the second cavity (B), the fourth cavity (C). At this time, the first damping valve and the second damping valve play a role in partial suspension damping. When the suspension is actively controlled, the damping effect of the damping valve is conducive to the stability of control. Another part of the suspension damping is generated by the electric pump assembly (2); the first hole (101) of the vane-type hydraulic-electric shock absorber (Y2) is connected to the first oil port (201A) of the hydraulic pump (201) of the electric pump assembly (2), and the second hole (102) is connected to the second oil port (201B) of the hydraulic pump (201) of the electric pump assembly (2); and in order to dissipate high-frequency vibration and reduce the adverse effect of the rotational inertia of the electric pump assembly (2) on the suspension during high-frequency vibration, the first cavity (A) and the third cavity (D) are connected to the right small oil-gas buffer shock absorber (8) and the right large oil-gas buffer shock absorber (10) through the fourth hole (104); the second cavity (B) and the fourth cavity (C) are connected to the left small oil-gas buffer shock absorber (7) and the left large oil-gas buffer shock absorber (9) through the third hole (103); Thus, when the connecting arm assembly (6) rotates, oil also enters or flows out of the electric pump assembly (2) through the first hole (101) and the second hole (102), thereby driving the electric pump assembly (2) to rotate, and the motor (202) converts hydraulic energy into electrical energy; the alternating current generated by the motor (202) enters the three-phase rectifier bridge through the three-phase windings ua, ub, uc of the motor (202), and becomes direct current after rectification; The direct current passes through the switch tube Dr and enters the dissipation resistor Rr; the switch tube Dr receives the PWM control signal through the control line Cr, and controls the connection or disconnection of the dissipation resistor Rr under the control of the PWM control signal, thereby adjusting the power consumption of the dissipation resistor Rr, forming an electromagnetic damping force that hinders the relative movement between the wheel and the vehicle body (Y1); wherein, the duty cycle of the PWM control signal determines the conduction time of the dissipation resistor Rr.

8. The blade-type hydraulic-electric shock absorber according to claim 7, characterized in that: When the connecting arm assembly (6) rotates upward, the blade assembly (3) rotates clockwise, and the first cavity (A) and the third cavity (D) are compressed, and the second cavity (B) and the fourth cavity (C) are extended, and a part of the oil flows from the first cavity (A) and the third cavity (D) through the first damping valve and the second damping valve into the second cavity (B) and the fourth cavity (C); At the same time, a portion of the oil flows from the third cavity (D) through the fourth hole (104), enters the right small oil-gas buffer shock absorber (8) and the right large oil-gas buffer shock absorber (10), flows through the second damping valve (802) and the fourth damping valve (1002), enters the second oil chamber (8Y) and the fourth oil chamber (10Y), and then pushes the second floating piston (803) and the fourth floating piston (1003), compressing the second air chamber (8Q) and the fourth air chamber (10Q); At the same time, the first air chamber (7Q) and the third air chamber (9Q) of the left small oil-gas buffer shock absorber (7) and the left large oil-gas buffer shock absorber (9) are extended, pushing the first floating piston (703) and the third floating piston (903), so that the oil in the first oil chamber (7Y) and the third oil chamber (9Y) enters the fourth cavity (C) through the first damping valve (702) and the third damping valve (902); At the same time, a portion of the oil flows from the third cavity (D) through the fourth hole (104) into the second hole (102), and then enters the second oil port (201B) of the hydraulic pump (201), driving the hydraulic pump (201) of the electric pump assembly (2) to rotate. At this time, the hydraulic pump acts as a hydraulic motor, thereby driving the motor (202) to rotate and generate electricity. The generated electricity is dissipated by heat generated by the dissipation resistor Rr, and the oil flows through the first oil port (201A) of the hydraulic pump (201) into the first hole (101), and then enters the third hole (103), and then flows into the fourth cavity (C); Since the sum of the damping coefficients of the first damping valve (702), the second damping valve (802), the third damping valve (902) and the fourth damping valve (1002) is smaller than the damping coefficients of the first damping valve and the second damping valve, and the damping force generated by the first damping valve (702), the second damping valve (802), the third damping valve (902) and the fourth damping valve (1002) is smaller than the inertia force generated by the rotational inertia of the electric pump assembly (2), the oil initially passes through the second damping valve (802) and the fourth damping valve (1002) at a relatively large flow rate and enters the second oil chamber (8Y) and the fourth oil chamber (10Y), thereby pushing the second floating piston (803) and the fourth floating piston (1003) and compressing the second air chamber (8Q) and the fourth air chamber (10Q). When the pressure of the second air chamber (8Q) and the fourth air chamber (10Q) increases, the pressure difference before and after the second damping valve (802) and the fourth damping valve (1002) decreases, and the flow rate through the second damping valve (802) and the fourth damping valve (1002) decreases. At this time, the flow rate of oil through the first damping valve, the second damping valve and the hydraulic pump (201) increases; therefore, high-frequency vibration energy will be preferentially absorbed by the second damping valve (802) and the fourth damping valve (1002), thereby facilitating the role of the blade-type shock absorber at the first main frequency, reducing the role of the first damping valve, the second damping valve and the electric pump (2) of the blade-type shock absorber at the second main frequency, thereby reducing the damping force and inertia force at high frequencies, facilitating the reduction of sprung mass acceleration, and reducing suspension energy consumption.

9. The blade-type hydraulic shock absorber according to claim 7, characterized in that: When the connecting arm assembly (6) rotates downward, the blade assembly (3) rotates counterclockwise, and the first cavity (A) and the third cavity (D) are stretched, and the second cavity (B) and the fourth cavity (C) are compressed, and a portion of the oil flows from the second cavity (B) and the fourth cavity (C) through the first damping valve and the second damping valve into the first cavity (A) and the third cavity (D); At the same time, a portion of the oil flows from the fourth cavity (C) through the third hole (103), enters the left small oil-gas buffer shock absorber (7) and the left large oil-gas buffer shock absorber (9), flows through the first damping valve (702) and the third damping valve (902), enters the first oil chamber (7Y) and the third oil chamber (9Y), and then pushes the first floating piston (703) and the third floating piston (903), compressing the first air chamber (7Q) and the third air chamber (9Q); At the same time, the second air chamber (8Q) and the fourth air chamber (10Q) of the right small oil-gas buffer shock absorber (8) and the right large oil-gas buffer shock absorber (10) are extended, pushing the second floating piston (803) and the fourth floating piston (1003), so that the oil in the second oil chamber (8Y) and the fourth oil chamber (10Y) enters the third cavity (D) through the second damping valve (802) and the fourth damping valve (1002); At the same time, a portion of the oil flows from the fourth cavity (C) through the third hole (103) into the first hole (101), and then enters the first oil port (201A) of the hydraulic pump (201), driving the hydraulic pump (201) of the electric pump assembly (2) to rotate. At this time, the hydraulic pump acts as a hydraulic motor, thereby driving the motor (202) to rotate and generate electricity. The generated electricity is dissipated by heat through the dissipation resistor Rr, and the oil flows through the second oil port (201B) of the hydraulic pump (201) into the second hole (102), and then enters the fourth hole (104), and then flows into the third cavity (D); Since the sum of the damping coefficients of the first damping valve (702), the second damping valve (802), the third damping valve (902) and the fourth damping valve (1002) is smaller than the damping coefficients of the first damping valve and the second damping valve, and the damping force generated by the first damping valve (702), the second damping valve (802), the third damping valve (902) and the fourth damping valve (1002) is smaller than the inertia force generated by the rotational inertia of the electric pump assembly (2), the oil initially passes through the first damping valve (702) and the third damping valve (902) at a relatively large flow rate and enters the first oil chamber (7Y) and the third oil chamber (9Y), thereby pushing the first floating piston (703) and the third floating piston (903) and compressing the first air chamber (7Q) and the third air chamber (9Q). When the pressure of the first air chamber (7Q) and the third air chamber (9Q) increases, the pressure difference before and after the first damping valve (702) and the third damping valve (902) decreases, and the flow rate through the first damping valve (702) and the third damping valve (902) decreases. At this time, the flow rate of oil through the first damping valve, the second damping valve and the hydraulic pump (201) increases; therefore, high-frequency vibration energy will be preferentially absorbed by the first damping valve (702) and the third damping valve (902), which is conducive to exerting the role of the blade-type shock absorber at the first main frequency, reducing the role of the first damping valve, the second damping valve and the electric pump (2) of the blade-type shock absorber at the second main frequency, thereby reducing the damping force and inertia force at high frequencies, which is conducive to reducing the acceleration of the sprung mass and reducing the energy consumption of the suspension.

10. The blade-type hydraulic shock absorber according to claim 1, characterized in that: The vane-type hydraulic shock absorber further comprises: a first oil pressure sensor (11) and a second oil pressure sensor (12); The first oil pressure sensor (11) is used to measure the oil pressure of the left small oil-gas buffer shock absorber (7), the left large oil-gas buffer shock absorber (9) and the change of the oil pressure on the left side of the electric pump assembly (2); the second oil pressure sensor (12) is used to measure the oil pressure of the right small oil-gas buffer shock absorber (8) and the right large oil-gas buffer shock absorber (10) and the change of the oil pressure on the right side of the electric pump assembly (2).

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