Novel double-electromagnetic-valve full-active suspension actuator

Abstract

The utility model provides a novel double-electromagnetic-valve full-active suspension actuator. The novel double-electromagnetic-valve full-active suspension actuator comprises a shock absorber, a hydraulic valve block, a recovery electromagnetic valve and a compression electromagnetic valve. The hydraulic valve block is arranged at the cylinder bottom in a sealed mode and internally provided with a compression oil channel communicated with the lower cavity of the working cylinder and a recovery oil channel communicated with the upper cavity of the working cylinder, and the compression oil channel and the recovery oil channel are outwards connected with a power pump. The recovery electromagnetic valve is arranged on the outer wall of the oil storage cylinder, is communicated with the upper cavity and the oil storage cylinder, and is also provided with a recovery one-way valve communicated with the oil storage cylinder and the upper cavity; the compression electromagnetic valve is connected to the valve block and communicated with the lower cavity and the oil storage cylinder, and is further provided with a compression one-way valve communicated with the oil storage cylinder and the lower cavity. According to the novel double-electromagnetic-valve full-active suspension actuator, the structure is optimized, the occupied space of a chassis is reduced, the actuator has multiple working modes including a full-active mode, an active ADS mode and an ADS mode, full-active adjustment with higher jacking capacity and compression capacity can be achieved, the damping adjustment broadband in the ADS mode is increased, and the energy recovery function is achieved.

Description

Technical Field

[0001] The utility model relates to the technical field of active suspensions, and particularly relates to a novel double-solenoid-valve fully active suspension actuator. Background Art

[0002] A fully active suspension system senses different driving conditions through sensor technology, controls the output actions of an active suspension actuator according to system strategies, and adjusts the vehicle attitude and the stiffness and damping performance of the suspension in real time. It can balance the handling stability and ride comfort of the vehicle, and improve the passing performance and safety of the vehicle. At present, the widely used air suspension has a slow response time and cannot adjust the vehicle body attitude in real time; the damping adjustable suspension equipped with a solenoid valve or a magnetorheological shock absorber cannot adjust the vehicle body height and the suspension stiffness without an external power source.

[0003] The fully active suspension actuator provides an active jacking force for the suspension through an external power pump to actively control the vehicle attitude. However, the existing active suspension actuators have problems of large chassis space occupation and high energy consumption of the active jacking force. Summary of the Utility Model

[0004] In order to better solve the above problems, the utility model provides a novel double-solenoid-valve fully active suspension actuator, which can optimize the structure, reduce the chassis space occupation, and achieve fully active adjustment with greater jacking and compression capabilities, increase the damping adjustment bandwidth in the ADS mode, and realize the energy recovery function.

[0005] To achieve the above object, an embodiment of the utility model provides a novel double-solenoid-valve fully active suspension actuator, which includes a shock absorber, and also includes a rebound solenoid valve, a compression solenoid valve, and a hydraulic valve block; the hydraulic valve block is arranged at the bottom of the oil storage cylinder of the shock absorber, and internally has a compression oil passage communicating upward to the lower cavity of the working cylinder and a rebound oil passage communicating upward to the intermediate cylinder. Compression oil pipe joints and rebound oil pipe joints that can be connected to both ends of a power pump are respectively arranged outside the compression oil passage and the rebound oil passage; the oil inlet end of the rebound solenoid valve communicates with the upper cavity of the working cylinder through the intermediate cylinder, and the oil outlet end communicates with the oil storage cylinder; the rebound solenoid valve is provided with a rebound check valve, the oil inlet end communicates with the oil storage cylinder, and the oil outlet end communicates with the upper cavity of the working cylinder through the intermediate cylinder; the oil inlet end of the compression solenoid valve communicates with the compression oil passage, and the oil outlet end communicates with the oil storage cylinder through; the compression solenoid valve is provided with a compression check valve, the oil inlet end communicates with the oil storage cylinder, and the oil outlet end communicates with the compression oil passage;

[0006] The new dual-solenoid valve fully active suspension actuator includes a fully active mode, an active ADS mode, and an ADS mode. In the fully active mode, the oil in the upper chamber of the working cylinder flows through the intermediate cylinder into the return oil passage and then into the power pump. After being pressurized by the power pump, it flows through the compression oil passage into the lower chamber of the working cylinder, causing the piston rod to move upward. The oil in the lower chamber of the working cylinder flows through the compression oil passage into the power pump. After being pressurized by the power pump, it flows through the return oil passage into the intermediate cylinder and then into the upper chamber of the working cylinder, causing the piston rod to move downward. In the active ADS mode, when the piston rod moves upward, the oil in the upper chamber of the working cylinder flows through the intermediate cylinder into the return solenoid valve, then through the compression check valve into the compression oil passage and then into the lower chamber of the working cylinder. The power pump pressurizes the upper chamber of the working cylinder to increase the return damping or pressurizes the lower chamber of the working cylinder to reduce the return damping. When the piston rod moves downward, the oil in the lower chamber of the working cylinder flows through the compression oil passage into the compression solenoid valve, then through the return check valve into the intermediate cylinder and then into the upper chamber of the working cylinder. The power pump pressurizes the lower chamber of the working cylinder to increase the compression damping or pressurizes the upper chamber of the working cylinder to reduce the compression damping. In the ADS mode, the power pump is turned off. When the piston rod moves upward, the oil in the upper chamber of the working cylinder flows through the intermediate cylinder into the return solenoid valve, then through the compression check valve into the compression oil passage and then into the lower chamber of the working cylinder. When the piston rod moves downward, the oil in the lower chamber of the working cylinder flows through the compression oil passage into the compression solenoid valve, then through the return check valve into the intermediate cylinder and then into the upper chamber of the working cylinder.

[0007] Optionally, it further includes an accumulator, which is connected to the oil storage cylinder. In the fully active mode, when the piston rod moves upward, the oil in the accumulator flows into the oil storage cylinder and then through the return check valve into the intermediate cylinder, and flows into the return oil passage together with the oil flowing into the intermediate cylinder from the upper chamber of the working cylinder. When the piston rod moves downward, part of the oil in the lower chamber of the working cylinder flows through the compression solenoid valve into the accumulator when passing through the compression oil passage. In the active ADS mode and the ADS mode, when the piston rod moves upward, the oil in the accumulator flows into the oil storage cylinder, through the compression check valve into the compression oil passage and then into the lower chamber of the working cylinder. When the piston rod moves downward, part of the oil passing through the compression solenoid valve flows into the accumulator

[0008] Optionally, the power pump is drivingly connected to a generator. The new dual-solenoid valve fully active suspension actuator further includes an energy recovery mode. In the energy recovery mode, the power pump is switched to the power generation mode. When the piston rod moves upward, the oil in the upper chamber of the working cylinder flows through the intermediate cylinder into the return oil passage and then into the power pump, and then through the power pump into the compression oil passage and then into the lower chamber of the working cylinder. When the piston rod moves downward, the oil in the lower chamber of the working cylinder flows through the compression oil passage into the power pump, and then through the power pump into the return oil passage and then through the diversion chamber into the upper chamber of the working cylinder. The oil flowing through the power pump drives the power pump to rotate and then drives the generator to generate electricity.

[0009] Compared with the prior art, the beneficial effects of the new dual-solenoid valve fully active suspension actuator of the present invention are:

[0010] The structure of the new dual-solenoid valve fully active suspension actuator is reasonably designed. By centrally arranging the compression solenoid valve, the rebound solenoid valve, the hydraulic valve block, the power pump, etc. at the end of the shock absorber body, the structure is optimized. Compared with the structure with two solenoid valves arranged outside the cylinder, it can reduce the occupied chassis space, and there is no need for much avoidance design at the cylinder barrel, which is more conducive to chassis development and vehicle layout.

[0011] The new dual-solenoid valve fully active suspension actuator has multiple working modes. In the fully active working mode, when the piston rod moves up and down, the jacking ability and compression ability are provided by the pressurization method of the power pump, realizing the fully active jacking and compression functions, and the jacking ability and compression ability are greater, which can realize the functions of actively raising and lowering the body and taking off in place; in the ADS mode, the adjustment of the rebound damping and compression damping can be realized by controlling the valve opening of the rebound solenoid valve and the compression solenoid valve; in the active ADS mode, the damping adjustment with a wider bandwidth can be further realized by pressurizing the upper and lower chambers of the working cylinder with the power pump; in the energy recovery mode, the energy recovery function can be realized by using the oil flow through the power pump to drive the external power generation module to generate electricity. Description of the Drawings

[0012] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0013] Figure 1 Structural schematic of the new dual-solenoid valve fully active suspension actuator according to the embodiment of the present invention Figure 1 ;

[0014] Figure 2 Structural schematic of the new dual-solenoid valve fully active suspension actuator according to the embodiment of the present invention Figure 2 ;

[0015] Figure 3 Principle schematic diagram of the new dual-solenoid valve fully active suspension actuator according to the embodiment of the present invention;

[0016] Figure 4 Principle schematic diagram in the fully active mode according to the embodiment of the present invention;

[0017] Figure 5 Principle schematic diagram of small damping in the active ADS mode according to the embodiment of the present invention;

[0018] Figure 6 Principle schematic diagram of large damping in the active ADS mode according to the embodiment of the present invention;

[0019] Figure 7 It is a schematic diagram of the principle under the ADS mode of the embodiment of the present utility model;

[0020] Figure 8 It is a schematic diagram of the principle under the energy recovery mode of the embodiment of the present utility model.

[0021] Reference numerals:

[0022] 1. Oil storage cylinder; 2. Working cylinder; 3. Intermediate cylinder; 4. Guide assembly; 5. Piston rod; 6. Hydraulic valve block; 7. Recovery solenoid valve; 8. Compression solenoid valve; 9. Accumulator; 10. Recovery oil pipe joint; 11. Compression oil pipe joint; 12. Upper chamber; 13. Lower chamber; 14. Recovery check valve; 15. Compression check valve; 16. Power pump; 17. Generator. Specific embodiments

[0023] In order to make the above objects, features and advantages of the present utility model more obvious and understandable, the following will describe the specific embodiments of the present utility model in detail with reference to the accompanying drawings. Many specific details are set forth in the following description in order to fully understand the present utility model. However, the present utility model can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without departing from the connotation of the present utility model. Therefore, the present utility model is not limited by the matrix embodiments disclosed below.

[0024] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those of ordinary skill in the technical field to which the present utility model belongs. The terms used herein in the specification of the present utility model are only for the purpose of describing specific embodiments and are not intended to limit the present utility model. The term "and / or" used herein includes any and all combinations of one or more of the related listed items.

[0025] As Figures 1 - 3 shown, the novel double-solenoid fully active suspension actuator shock absorber of the embodiment of the present utility model includes an oil storage cylinder 1, an intermediate cylinder 3 and a working cylinder 2 which are coaxially sleeved. The oil storage cylinder 1 is located outside, the working cylinder 2 is coaxially sleeved in the oil storage cylinder 1, and the intermediate cylinder 3 is sealingly sleeved between the working cylinder 2 and the oil storage cylinder 1; a working chamber is formed in the working cylinder 2, a diversion chamber is formed between the inner side wall of the intermediate cylinder 3 and the working cylinder 2, and an oil storage chamber is formed between the oil storage cylinder 1 and the working cylinder 2 (including a part of the outer side wall of the intermediate cylinder 3). The working chamber, the diversion chamber and the oil storage chamber are filled with hydraulic oil.

[0026] The shock absorber further includes a piston assembly, which includes a piston rod 5 and a guide assembly 4. The guide assembly 4 is sealingly arranged at the top ends of the oil storage cylinder 1 and the working cylinder 2, and a guide hole is provided at the center. The piston rod 5 is arranged in the working chamber, with its upper end extending out from the guide hole and its lower end dividing the working chamber into an upper chamber 12 and a lower chamber 13. Here, the guide assembly 4 can be a downward multi-step convex structure. The lower step extends into the top end of the working cylinder 2, the middle step extends into the top end of the oil storage cylinder 1, and the upper step is stuck outside the top end of the oil storage cylinder 1. Seals are provided at the joints of each step, such as oil seals and sealing rings. The size of the guide hole matches that of the piston rod 5 (the inner diameter of the guide hole is equal to the outer diameter of the piston rod 5), and the piston rod 5 can move up and down along the guide hole. A through hole is provided in the outer wall of the upper chamber 12 of the working cylinder 2 corresponding to the upper part of the intermediate cylinder 3, so that the upper chamber 12 of the working cylinder 2 communicates with the diversion chamber.

[0027] The novel double-solenoid valve fully active suspension actuator further includes a hydraulic valve block 6, a rebound solenoid valve 7, a compression solenoid valve 8, and an accumulator 9.

[0028] The hydraulic valve block 6 is sealingly arranged at the bottom ends of the oil storage cylinder 1 and the working cylinder 2. The hydraulic valve block 6 has multiple oil passages inside, including a compression oil passage and a rebound oil passage. The upper end of the compression oil passage communicates with the bottom of the lower chamber 13 of the working cylinder 2, and the upper end of the rebound oil passage communicates with the bottom of the diversion chamber. The lower ends of the compression oil passage and the rebound oil passage extend outwards, and a compression oil pipe joint 11 and a rebound oil pipe joint 10 are respectively arranged at the outer ends. The two oil pipe joints are respectively connected to both ends of the power pump 16. Here, the power pump 16 is externally connected to the actuator of the embodiment of the present invention through the two oil pipe joints.

[0029] The rebound solenoid valve 7 can be connected to the outer wall of the oil storage cylinder 1. By installing an outward-extending tubular valve seat on the outer side wall of the oil storage cylinder 1, the rebound solenoid valve 7 can be fixedly installed in the valve seat and sealed. There are two through holes inside the valve seat, which are an oil inlet and an oil outlet respectively. The inner side of the oil inlet communicates with the inside of the intermediate cylinder 3, and the inner side of the oil outlet communicates with the inside of the oil storage cylinder 1. A communicating rebound oil path is formed inside the valve seat on the outer sides of the oil inlet and the oil outlet; that is, the oil inlet end of the rebound solenoid valve 7 communicates with the diversion chamber and thus can communicate with the upper chamber 12 of the working cylinder 2, and the oil outlet end communicates with the oil storage chamber (oil storage cylinder). The oil in the upper chamber 12 of the working cylinder 2 can flow into the diversion chamber and then flow into the oil storage chamber through the rebound solenoid valve 7. The rebound solenoid valve 7 also has a rebound check valve 14. The oil path of the rebound check valve 14 is opposite to that of the rebound oil path of the rebound solenoid valve 7. The oil inlet end of the rebound check valve 14 communicates with the oil storage chamber, and the oil outlet end communicates with the diversion chamber, so that the oil in the oil storage chamber can flow into the diversion chamber through the rebound check valve 14.

[0030] The compression solenoid valve 8 can be connected to the hydraulic valve block 6. By installing an outward-extending valve seat inside the hydraulic valve block 6, the compression solenoid valve 8 can be fixedly installed and sealed within the valve seat. The inner side of the valve seat has two through holes, namely the oil inlet and the oil outlet. The inner side of the oil inlet is connected to the compression oil passage inside the valve block, and the inner side of the oil outlet is connected upward to the bottom of the oil storage cylinder 1. The outer sides of the oil inlet and the oil outlet form a connected compression oil circuit within the valve seat; that is, the oil inlet end of the compression solenoid valve 8 is connected to the compression oil passage, and the oil outlet end is connected to the oil storage cavity through a connection. The oil in the compression oil passage can flow into the oil storage cavity through the compression solenoid valve 8. This compression solenoid valve 8 also has a compression check valve 15. The oil passage of the compression check valve 15 is in the opposite direction to that of the compression oil passage of the compression solenoid valve 8. The oil inlet end of the compression check valve 15 is connected to the oil storage cavity, and the oil outlet end is connected to the compression oil passage, so that the oil in the oil storage cavity can flow into the compression oil passage through the compression check valve 15.

[0031] The accumulator 9 can be connected to the hydraulic valve block 6. The accumulator 9 includes two chambers, an air chamber and an oil chamber. The air chamber is filled with high-pressure gas, and oil can flow into or out of the oil chamber. There is an accumulator oil passage in the valve block. One end of the accumulator oil passage is connected to the oil chamber of the accumulator 9, and the other end is connected to the bottom of the oil storage cavity. That is, the accumulator 9 is connected to the bottom of the oil storage cavity through the accumulator oil passage. The accumulator 9 can adjust the pressure of the shock absorber by converting to actively store and release oil, and perform oil compensation adjustment on the shock absorber to compensate for the oil volume occupied by the piston rod.

[0032] One end of the power pump 16 is connected to the upper chamber 12 of the working cylinder 2 through the oil return passage and the diversion cavity, and the other end is connected to the lower chamber 13 of the working cylinder 2 through the compression oil passage. The power pump 16 is externally connected through two oil pipe joints and the hydraulic valve block 6 to realize the connection of the oil passages of the upper and lower chambers 13 of the working cylinder 2, and can pressurize the upper and lower chambers of the working cylinder 2. By controlling the magnitude of the pressurization, a pressure difference can be generated between the upper and lower chambers. The input end of the generator 17 is connected to the power pump. Specifically, the impeller of the power pump can be connected to the power input end of the generator through a connecting shaft, and the rotation of the impeller of the power pump can be used to drive the generator to generate electricity.

[0033] As Figures 3 - 8 shown, the working modes of the novel dual-solenoid valve fully active suspension actuator according to the embodiments of the present invention include a fully active mode, an active ADS mode, an ADS mode, and an energy recovery mode.

[0034] In the fully active working mode, part of the oil in the upper chamber 12 of the working cylinder 2 flows into the diversion chamber (intermediate cylinder), then through the diversion chamber into the oil recovery channel, and then through the oil recovery channel into the power pump 16. After being pressurized by the power pump 16, it flows into the compression oil channel, and then through the compression oil channel into the lower chamber 13 of the working cylinder 2, causing the piston rod 5 to move upward. Part of the oil in the lower chamber 13 of the working cylinder 2 flows into the compression oil channel, through the compression oil channel into the power pump 16, after being pressurized by the power pump 16, it flows into the oil recovery channel, through the oil recovery channel into the diversion chamber, and then through the diversion chamber into the upper chamber 12 of the working cylinder 2, causing the piston rod 5 to move downward. In this active working mode, the external power pump 16 drives the oil flow by pressurizing the oil, and can control the pressures in the upper and lower chambers of the working cylinder 2 to make the piston rod move upward or downward, generating a jacking capacity and a compression capacity, and can achieve the fully active jacking function with a large jacking capacity and the fully active compression function with a large compression capacity, thus being able to achieve the functions of actively lifting the vehicle body and taking off in place.

[0035] Meanwhile, in the fully active working mode, the accumulator 9 can adjust the pressure in the hydraulic oil circuit by converting the active storage and release of oil, and perform oil compensation adjustment on the shock absorber. When the piston rod 5 moves upward, the oil in the accumulator 9 flows into the oil storage chamber, through the oil storage chamber into the return check valve 14, and then through the return check valve 14 into the diversion chamber, and together with the oil flowing into the diversion chamber from the upper chamber 12 of the working cylinder 2, it flows into the oil recovery channel. After being pressurized by the power pump 16, it flows into the upper chamber 12 of the working cylinder 2. When the piston rod 5 moves downward, after the oil in the lower chamber 13 of the working cylinder 2 flows into the compression oil channel, part of the oil in the compression oil channel flows into the compression solenoid valve 8, through the compression solenoid valve 8 into the oil storage chamber, and then through the oil storage chamber into the accumulator 9.

[0036] In the active ADS mode, the power pump 16 can pressurize the upper chamber 12 of the working cylinder 2 through the oil recovery channel, or pressurize the lower chamber 13 of the working cylinder 2 through the compression oil channel. When the piston rod 5 moves upward, part of the oil in the upper chamber 12 of the working cylinder 2 flows into the diversion chamber, through the diversion chamber into the return solenoid valve 7, and then through the return solenoid valve 7 into the oil storage chamber and then into the compression check valve 15, and then through the compression check valve 15 into the compression oil channel, and after passing through the compression oil channel, it flows into the lower chamber 13 of the working cylinder 2. During this return stroke, the pressure difference between the upper and lower chambers of the working cylinder can be controlled by controlling the valve opening of the return solenoid valve and the pressurization method of the power pump, thereby generating a return damping force; if a large return damping is required, as Figure 6 shown in (left), the power pump 16 can pressurize the upper chamber 12 of the working cylinder 2 to increase the pressure difference between the upper and lower chambers, thereby increasing the return damping force; if a small return damping is required, as Figure 5As shown in (left), the lower chamber 13 of the working cylinder 2 can be pressurized by the power pump 16 to reduce the pressure difference between the upper and lower chambers, thereby reducing the return damping force and increasing the return damping adjustment bandwidth. When the piston rod 5 moves downward, some of the oil in the lower chamber 13 of the working cylinder 2 flows into the compression oil passage, then flows through the compression solenoid valve 8, and then into the oil storage chamber and then into the return check valve 14, and then through the return check valve 14 into the diversion chamber, and then into the upper chamber 12 of the working cylinder 2 after passing through the diversion chamber. During this compression stroke, the pressure difference between the upper and lower chambers of the working cylinder can be controlled by controlling the valve opening of the return solenoid valve and the power pump pressurization method, thereby generating a compression damping force; if a large compression damping is required, such as Figure 6 As shown in (right), the lower chamber 13 of the working cylinder 2 can be pressurized by the power pump 16 to increase the pressure difference between the upper and lower chambers, thereby increasing the compression damping force; if a small compression damping is required, such as Figure 5 As shown in (right), the upper chamber 12 of the working cylinder 2 can be pressurized by the power pump 16 to reduce the pressure difference between the upper and lower chambers, thereby reducing the compression damping force and increasing the compression damping adjustment bandwidth.

[0037] At the same time, when the piston rod 5 moves upward, the accumulator 9 releases oil, and the oil in the accumulator 9 flows into the oil storage chamber, and together with the oil flowing out of the upper chamber 12 of the working cylinder 2 and passing through the return solenoid valve 7, it flows into the compression check valve 15, and then through the compression check valve 15 into the compression oil passage and then into the lower chamber 13 of the working cylinder 2; when the piston rod 5 moves downward, the accumulator 9 stores oil, and some of the oil flowing out of the lower chamber 13 of the working cylinder 2 and passing through the compression solenoid valve 8 into the oil storage chamber flows into the accumulator 9.

[0038] In the ADS mode, the power pump 16 is turned off; when the piston rod 5 moves upward, the oil in the upper chamber 12 of the working cylinder 2 flows through the diversion chamber into the return solenoid valve 7, and then through the compression check valve 15 into the compression oil passage and then into the lower chamber 13 of the working cylinder 2; when the piston rod 5 moves downward, the oil in the lower chamber 13 of the working cylinder 2 flows through the compression oil passage into the compression solenoid valve 8, and then through the return check valve 14 into the diversion chamber and then into the upper chamber 12 of the working cylinder 2. The oil flow direction in this ADS mode is the same as that in the active ADS mode, except that there is no pressurization by the power pump 16, and the return damping is adjusted by controlling the valve opening of the return solenoid valve 7, and the compression damping is adjusted by controlling the valve opening of the compression solenoid valve 8.

[0039] At the same time, when the piston rod 5 moves upward, the accumulator 9 releases oil, and the oil in the accumulator 9 flows into the oil storage chamber, then through the compression check valve 15 into the compression oil passage and then into the lower chamber 13 of the working cylinder 2; when the piston rod 5 moves downward, the accumulator 9 stores oil, and some of the oil passing through the compression solenoid valve 8 flows into the accumulator 9. The way of oil compensation for the accumulator 9 in the active ADS mode is the same.

[0040] In the energy recovery mode, the power pump 16 is switched to the power generation mode. Here, a power generation module (such as the generator 17) is externally connected to the power pump 16. In the power generation mode, the rotation mode of the power pump 16 is changed from the actively electrically driven rotation mode to the passive rotation mode, and it can rotate with the flow of the oil fluid, driving the power generation module to generate electricity. When the piston rod 5 moves upward, the oil fluid in the upper chamber 12 of the working cylinder 2 flows into the diversion chamber, then flows into the oil recovery channel through the diversion chamber, then flows into the power pump 16 through the oil recovery channel, flows into the compression oil channel after passing through the power pump 16, and then flows into the lower chamber 13 of the working cylinder 2 through the compression oil channel; when the piston rod 5 moves downward, the oil fluid in the lower chamber 13 of the working cylinder 2 flows into the compression oil channel, flows into the power pump 16 through the compression oil channel, flows into the oil recovery channel after passing through the power pump 16, then flows into the diversion chamber and then into the upper chamber 12 of the working cylinder 2. When the oil fluid flows through the power pump 16, the oil fluid can drive the power pump 16 to rotate, thereby driving the externally connected generator 17 to rotate for power generation, realizing energy recovery.

[0041] Meanwhile, when the piston rod 5 moves upward, the accumulator 9 releases the oil fluid. The oil fluid in the accumulator 9 flows into the oil storage chamber, and then flows into the lower chamber 13 of the working cylinder 2 through the compression check valve 15 and into the compression oil channel; when the piston rod 5 moves downward, the accumulator 9 stores the oil fluid, the compression solenoid valve 8 is closed, and a part of the oil fluid flowing into the diversion chamber flows into the accumulator 9 through the recovery solenoid valve 7.

[0042] In this new type of double solenoid valve fully active suspension actuator, the recovery solenoid valve 7, the compression solenoid valve 8 and the hydraulic valve block 6 are arranged at the end or near the end of the shock absorber cylinder body. The structure is optimized by integrating it at the end of the shock absorber body. Compared with the existing structure with two solenoid valves arranged outside the cylinder barrel, it can reduce the space occupied by the actuator on the chassis, and there is no need for much avoidance design outside the end, which will not affect the overall structural strength and reduce the pre-research and production costs of the shock absorber.

[0043] According to an exemplary embodiment of the present invention, this new type of double solenoid valve fully active suspension actuator includes two groups of shock absorbers, which are the left and right shock absorbers of the fully active suspension respectively. Each shock absorber is connected to the above-mentioned recovery and compression solenoid valves, as well as the hydraulic valve block and the power pump, and has multiple working modes. This new type of double solenoid valve fully active suspension actuator can be applied to the vehicle active suspension system, and cooperate with the electric pump assembly (including two groups of motor - hydraulic pump units on the left and right, respectively used to drive the left and right shock absorbers). The control system of the active suspension system sends control signals to components such as the recovery solenoid valve 7, the compression solenoid valve 8, and the power pump 16 according to the real-time vehicle driving conditions. It can realize continuously adjustable recovery and compression damping by controlling the power pump 16 to pressurize the upper and lower chambers of the working cylinder 2 and controlling the opening degree of the electromagnetic valves, and increase the adjustable range of the recovery and compression damping, improve the active lifting and compression capabilities, thereby improving the vehicle body control ability, ensuring smooth vehicle driving, and improving the vehicle driving comfort.

[0044] In actual application scenarios, equipment or components such as the oil storage cylinder 1, working cylinder 2, piston assembly, rebound solenoid valve 7, compression solenoid valve 8, and power pump 16 in the novel double-solenoid full-active suspension actuator of the embodiment of the present utility model can be designed accordingly according to the shock absorber specification signals, damping force adjustment requirements, etc. in the actual working conditions, or equipment with corresponding functions and specifications in the prior art can be adopted.

[0045] Moreover, in the embodiment of the present utility model, equipment or components such as the rebound solenoid valve 7, compression solenoid valve 8, accumulator 9, etc. are not limited to the above setting methods. In actual applications, the actual installation positions of each equipment or component can also be adjusted to achieve the actual application or other functions of the novel double-solenoid full-active suspension actuator. For example, the position of the rebound solenoid valve 7 on the outer wall of the oil storage cylinder 1 can be flexibly arranged, or it can also be installed on the hydraulic valve block 6, as long as the above functions can be achieved.

[0046] It should be noted that according to the needs of implementation, each component described in the embodiment of the present utility model can be split into more components, or two or more components or parts of components can be combined into new components to achieve the purpose of the embodiment of the present utility model.

[0047] The above embodiments only represent several implementation manners of the present utility model, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of the patent of the present utility model. It should be pointed out that for those of ordinary skill in the art, without departing from the concept of the present utility model, several modifications and improvements can still be made, and these all belong to the protection scope of the present utility model. Therefore, the protection scope of the patent of the present utility model should be subject to the appended claims.

Claims

1. A novel double solenoid valve fully active suspension actuator, including a shock absorber, characterized in that, It also includes a rebound solenoid valve, a compression solenoid valve, and a hydraulic valve block; among them, the hydraulic valve block is arranged at the bottom of the oil storage cylinder of the shock absorber and has a compression oil passage communicating upward to the lower chamber of the working cylinder and a rebound oil passage communicating upward to the intermediate cylinder inside. Compression oil pipe joints and rebound oil pipe joints that can be connected to both ends of the power pump are respectively arranged outside the compression oil passage and the rebound oil passage; the inlet end of the rebound solenoid valve communicates with the upper chamber of the working cylinder through the intermediate cylinder, and the outlet end communicates with the oil storage cylinder; the rebound solenoid valve is equipped with a rebound check valve, the inlet end communicates with the oil storage cylinder, and the outlet end communicates with the upper chamber of the working cylinder through the intermediate cylinder; the inlet end of the compression solenoid valve communicates with the compression oil passage, and the outlet end communicates with the oil storage cylinder through; the compression solenoid valve is equipped with a compression check valve, the inlet end communicates with the oil storage cylinder, and the outlet end communicates with the compression oil passage; the novel double-solenoid valve fully active suspension actuator includes a full active mode, an active ADS mode, and an ADS mode, in the full active mode, the oil in the upper chamber of the working cylinder flows through the intermediate cylinder into the rebound oil passage and then into the power pump, and after being pressurized by the power pump, it flows into the lower chamber of the working cylinder through the compression oil passage, causing the piston rod to move upward; the oil in the lower chamber of the working cylinder flows through the compression oil passage into the power pump, and after being pressurized by the power pump, it flows into the intermediate cylinder through the rebound oil passage and then into the upper chamber of the working cylinder, causing the piston rod to move downward; in the active ADS mode, when the piston rod moves upward, the oil in the upper chamber of the working cylinder flows through the intermediate cylinder into the rebound solenoid valve, then through the compression check valve into the compression oil passage and then into the lower chamber of the working cylinder, and the power pump pressurizes the upper chamber of the working cylinder to increase the rebound damping or pressurizes the lower chamber of the working cylinder to reduce the rebound damping; when the piston rod moves downward, the oil in the lower chamber of the working cylinder flows through the compression oil passage into the compression solenoid valve, then through the rebound check valve into the intermediate cylinder and then into the upper chamber of the working cylinder, and the power pump pressurizes the lower chamber of the working cylinder to increase the compression damping or pressurizes the upper chamber of the working cylinder to reduce the compression damping; in the ADS mode, the power pump is closed; when the piston rod moves upward, the oil in the upper chamber of the working cylinder flows through the intermediate cylinder into the rebound solenoid valve, then through the compression check valve into the compression oil passage and then into the lower chamber of the working cylinder; when the piston rod moves downward, the oil in the lower chamber of the working cylinder flows through the compression oil passage into the compression solenoid valve, then through the rebound check valve into the intermediate cylinder and then into the upper chamber of the working cylinder.

2. The novel double-solenoid fully active suspension actuator according to claim 1, wherein It also includes an accumulator, and the accumulator communicates with the oil storage cylinder; in the full active mode, when the piston rod moves upward, the oil in the accumulator flows into the oil storage cylinder and then through the rebound check valve into the intermediate cylinder, and flows into the rebound oil passage together with the oil flowing into the intermediate cylinder from the upper chamber of the working cylinder; when the piston rod moves downward, part of the oil in the lower chamber of the working cylinder flows through the compression solenoid valve into the accumulator when passing through the compression oil passage; in the active ADS mode and the ADS mode, when the piston rod moves upward, the oil in the accumulator flows into the oil storage cylinder, passes through the compression check valve into the compression oil passage and then into the lower chamber of the working cylinder; when the piston rod moves downward, part of the oil passing through the compression solenoid valve flows into the accumulator.

3. A novel double solenoid fully active suspension actuator according to claim 1, characterized in that, The power pump is drivingly connected to a generator. The novel double solenoid valve fully active suspension actuator further includes an energy recovery mode. In the energy recovery mode, the power pump is switched to a power generation mode. When the piston rod moves upward, the oil in the upper chamber of the working cylinder flows through the intermediate cylinder into the oil return channel and then into the power pump, and then flows through the power pump into the compression oil channel and then into the lower chamber of the working cylinder. When the piston rod moves downward, the oil in the lower chamber of the working cylinder flows through the compression oil channel into the power pump, and then flows through the power pump into the oil return channel and then into the upper chamber of the working cylinder through the diversion cavity. The oil flowing through the power pump drives the power pump to rotate and thus drives the generator to generate electricity.

Images