A servo motor pump cluster type high-power electric drive hydraulic actuator

Abstract

The application relates to a large-power electric drive hydraulic actuator of a servo motor pump cluster type, and belongs to the technical field of servo mechanisms. The large-power electric drive hydraulic actuator comprises n servo motor pumps, a first oil supplement one-way valve, a second oil supplement one-way valve, a first hydraulic control one-way valve, a second hydraulic control one-way valve, a first safety valve, a second safety valve, a bypass valve, a first high-pressure pressure sensor, a second high-pressure pressure sensor, a low-pressure pressure sensor, a filling valve, a pressurizing oil tank and a hydraulic cylinder; n is a positive integer not less than 10; the scheme of the servo motor pump cluster is adopted, the number of motor pumps in the previous redundant electric static pressure actuator is increased from 2 to 10 or more, and the problem of electromobility of the super-large power hydraulic actuator is solved. Compared with a traditional valve control hydraulic actuator, the problem of a super-large flow servo valve and a super-large power hydraulic pump station is avoided; the application meets the demand of a super-large power electric actuator of more than 100 kW, and has the characteristics of heavy load capacity, strong impact resistance, compact structure, and electromobility.

Description

Technical Field

[0001] This invention belongs to the field of servo mechanism technology and relates to a servo motor pump cluster type high-power electro-hydraulic actuator. Background Technology

[0002] Electro-hydraulic actuators, as a novel electro-actuator technology solution, are widely used in advanced aircraft in the international aerospace field due to their advantages such as heavy-duty capacity, strong shock resistance, easy redundancy, high reliability, and energy efficiency. Domestic research institutes have been tracking technological development for many years, achieving certain results in theoretical research and prototype manufacturing, and have begun engineering application demonstrations in the aviation, aerospace, and marine fields. Electro-hydraulic actuators in aviation, aerospace, and marine fields pursue high reliability, high dynamic characteristics, and high power density, generally employing redundancy schemes for the system or key components, such as dual-redundancy or triple-redundancy architectures, to address system reliability issues. Additionally, structural integration schemes are used to address high power density. However, currently, the highest redundancy design used in electro-hydraulic actuators in the aerospace and marine fields, both domestically and internationally, is quadruple-redundancy to address system reliability issues.

[0003] Driven by the social demand and technological development trends of electrification, energy conservation, and environmental protection, the actuators of civil engineering equipment must also be developed in the direction of electrification, energy conservation, and environmental protection. Electro-hydraulic actuators combine efficient power electronic drive with the proven hydraulic transmission in engineering machinery, making them an excellent electrified actuation system solution at present. In response to the current demand for heavy-duty and ultra-high-power electrified actuators, foreign universities and enterprises have developed a variety of electro-hydraulic actuators. Considering the low-cost requirements of the civilian market, current electro-hydraulic actuators for engineering machinery all use a servo motor to drive a hydraulic pump, and then match it with a functional valve group to drive the hydraulic cylinder to achieve linear output. The power is generally in the range of several kilowatts to tens of kilowatts. Electro-hydraulic actuators with a power of more than one hundred kilowatts are currently still lacking.

[0004] Chinese invention patent CN201410601786.2 describes a dual-redundant electromechanical hydrostatic servo mechanism that employs two independent sets of motor pumps and control drive units connected in parallel to drive the hydraulic cylinder. This design primarily addresses the issue of insufficient reliability of a single set of motor pumps and control drive units to meet system requirements, and is not intended to solve the problem of ultra-high power actuation demands. Summary of the Invention

[0005] The technical problem solved by this invention is to overcome the shortcomings of the prior art and propose a servo motor pump cluster type high-power electro-hydraulic actuator to meet the requirements of ultra-high power electro-actuators of hundreds of kilowatts and above, while having the characteristics of heavy load capacity, strong impact resistance, compact structure and electrification.

[0006] The solution of the present invention is:

[0007] A servo motor pump cluster type high-power electro-hydraulic actuator includes n servo motor pumps, a first replenishing check valve, a second replenishing check valve, a first hydraulically controlled check valve, a second hydraulically controlled check valve, a first safety valve, a second safety valve, a bypass valve, a first high-pressure sensor, a second high-pressure sensor, a low-pressure sensor, a filling valve, a booster oil tank, and a hydraulic cylinder.

[0008] Among them, the oil ports A of n servo motor pumps are combined and connected to the oil inlet of the first hydraulic control check valve; the oil outlet of the first hydraulic control check valve is connected to the A chamber of the hydraulic cylinder.

[0009] A first high-pressure sensor is installed in chamber A of the hydraulic cylinder; the control port of the first hydraulically controlled check valve is connected to the ports B of n servo motor pumps; the ports B of the n servo motor pumps are connected to the inlet of the second hydraulically controlled check valve; the outlet of the second hydraulically controlled check valve is connected to chamber B of the hydraulic cylinder; a second high-pressure sensor is installed in chamber B of the hydraulic cylinder; the control port of the second hydraulically controlled check valve is connected to the ports A of the n servo motor pumps; the outlet of the first replenishing check valve is connected to the ports A of the n servo motor pumps; the inlet of the first replenishing check valve... The system is connected to the booster tank; the outlet of the second replenishing check valve is connected to the oil ports B of n servo motor pumps after they converge, and the inlet of the second replenishing check valve is connected to the booster tank; the inlet of the first safety valve is connected to the A chamber of the hydraulic cylinder, and the outlet of the first safety valve is connected to the booster tank; the inlet of the second safety valve is connected to the B chamber of the hydraulic cylinder, and the outlet of the second safety valve is connected to the booster tank; the three ports of the bypass valve are respectively connected to the A chamber of the hydraulic cylinder, the B chamber of the hydraulic cylinder, and the booster tank; the low-pressure sensor and the filling valve are both connected to the booster tank; n is a positive integer not less than 10.

[0010] In the aforementioned servo motor pump cluster type high-power electro-hydraulic actuator, a first hydraulic control check valve is installed in the oil circuit between the oil ports A of n servo motor pumps and the A chamber of the hydraulic cylinder, and a second hydraulic control check valve is installed in the oil circuit between the oil ports B of n servo motor pumps and the B chamber of the hydraulic cylinder; thus, the position holding of the hydraulic actuator in the state of shutdown or power failure is achieved.

[0011] In the aforementioned high-power electro-hydraulic actuator for a cluster of servo motor pumps, a first replenishing check valve and a second replenishing check valve are respectively bypassed in the oil passages of port A and port B of the n servo motor pumps to achieve cluster oil replenishment for the n servo motor pumps.

[0012] In the aforementioned servo motor pump cluster type high-power electro-hydraulic actuator, the maximum working pressure of the hydraulic actuator is limited by setting a first safety valve in the A chamber of the hydraulic cylinder and a second safety valve in the B chamber of the hydraulic cylinder.

[0013] In the aforementioned servo motor pump cluster type high-power electro-hydraulic actuator, the pressure in hydraulic cylinder A chamber is monitored in real time by a first high-pressure pressure sensor; and the pressure in hydraulic cylinder B chamber is monitored in real time by a second high-pressure pressure sensor.

[0014] In the aforementioned high-power electro-hydraulic actuator with a cluster of servo motor pumps, a manual bypass valve is used to achieve vacuuming and oil filling of the hydraulic actuator; a booster tank is used to replenish oil to the cluster of n servo motor pumps and to remove leaking oil from the n servo motor pumps.

[0015] In the aforementioned servo motor pump cluster type high-power electric drive hydraulic actuator, the pressure of the booster oil tank is monitored by a low-pressure pressure sensor; and the hydraulic actuator is vacuumed and filled with oil by a filling valve.

[0016] In the aforementioned servo motor pump cluster type high-power electro-hydraulic actuator, the actuation process of the hydraulic actuator includes retraction and extension actions.

[0017] In the aforementioned servo motor pump cluster type high-power electro-hydraulic actuator, the specific process of the retraction action is as follows:

[0018] n servo motor pumps receive the same control command from the host computer and simultaneously rotate in the forward direction to output flow. After converging, the flow enters the hydraulic cylinder A chamber through the first hydraulic control check valve, while simultaneously supplying control oil to the second hydraulic control check valve, which opens in the reverse direction. The oil in the hydraulic cylinder B chamber flows back to the converging oil circuit of the n servo motor pumps through the second hydraulic control check valve, and is used for the servo motor pumps to draw oil, realizing the retraction action of the hydraulic actuator. During the process, the second replenishment check valve opens to replenish oil from the booster tank during the operation of the servo motor pumps. The first replenishment check valve, the first high-pressure safety valve, the second high-pressure safety valve, and the manual bypass valve are closed.

[0019] The specific process of the extension action in the aforementioned servo motor pump cluster high-power electro-hydraulic actuator is as follows:

[0020] n servo motor pumps receive the same control command from the host computer and simultaneously rotate in opposite directions to output flow. After merging, the flow enters the hydraulic cylinder B chamber through the second hydraulic control check valve, while simultaneously supplying control oil to the first hydraulic control check valve, which opens in the reverse direction. The oil in the hydraulic cylinder A chamber flows back to the merging oil circuit of the n servo motor pumps A port through the first hydraulic control check valve, and is used for the servo motor pumps to draw oil, realizing the extension action of the hydraulic actuator. During the process, the first replenishment check valve opens to replenish oil from the booster tank during the operation of the servo motor pumps. The second replenishment check valve, the first high-pressure safety valve, the second high-pressure safety valve, and the manual bypass valve are closed.

[0021] The advantages of this invention compared to the prior art are:

[0022] (1) This invention achieves a leap in the power of the electric-driven hydraulic actuator by means of flow integration and power superposition, solves the problem of electrification of ultra-high power hydraulic actuators, and provides a new solution for ultra-high power actuators;

[0023] (2) Compared with traditional valve-controlled actuators, the present invention avoids the problems of ultra-large flow servo valves and ultra-high power hydraulic pump stations;

[0024] (3) If any set of the motor pump cluster of the present invention fails, it will not affect the normal function of the hydraulic actuator, thereby achieving high power output of the actuator and improving reliability.

[0025] (4) By increasing or decreasing the number of arrays of motor pump clusters, the present invention can easily form electric-driven hydraulic actuators of different power levels, making it easy to serialize and standardize the structure of electric-driven hydraulic actuators. Attached Figure Description

[0026] Figure 1 This is a schematic diagram of the hydraulic actuator system of the present invention. Detailed Implementation

[0027] The present invention will be further described below with reference to the embodiments.

[0028] This invention provides a servo motor pump cluster type high-power electro-hydraulic actuator, which meets the requirements of ultra-high power electro-actuators of hundreds of kilowatts and above, and has the characteristics of heavy load capacity, strong impact resistance, compact structure and electrification.

[0029] Servo motor pump cluster high-power electro-hydraulic actuator, such as Figure 1As shown, it specifically includes n servo motor pumps 1, a first replenishing check valve 21, a second replenishing check valve 22, a first hydraulic control check valve 31, a second hydraulic control check valve 32, a first safety valve 41, a second safety valve 42, a bypass valve 5, a first high-pressure sensor 61, a second high-pressure sensor 62, a low-pressure sensor 7, a filling valve 8, a booster oil tank 9, and a hydraulic cylinder 10. Among them, the oil ports A of n servo motor pumps 1 are merged and connected to the oil inlet of the first hydraulic check valve 31; the oil outlet of the first hydraulic check valve 31 is connected to the A chamber of hydraulic cylinder 10; the A chamber of hydraulic cylinder 10 is equipped with a first high-pressure sensor 61; the control oil port of the first hydraulic check valve 31 is merged and connected to the oil ports B of n servo motor pumps 1; the oil ports B of n servo motor pumps 1 are merged and connected to the oil inlet of the second hydraulic check valve 32; the oil outlet of the second hydraulic check valve 32 is connected to the B chamber of hydraulic cylinder 10; the B chamber of hydraulic cylinder 10 is equipped with a second high-pressure sensor 62; the control oil port of the second hydraulic check valve 32 is merged and connected to the oil ports A of n servo motor pumps 1; the oil outlet of the first replenishing check valve 21 is connected to the oil inlet of n servo motor pumps 10. The oil port A of the motor pump 1 is connected to the inlet of the first replenishing check valve 21 and the booster oil tank 9; the oil outlet of the second replenishing check valve 22 is connected to the oil ports B of n servo motor pumps 1 and the inlet of the second replenishing check valve 22 is connected to the booster oil tank 9; the inlet of the first safety valve 41 is connected to the A chamber of the hydraulic cylinder 10 and the outlet of the first safety valve 41 is connected to the booster oil tank 9; the inlet of the second safety valve 42 is connected to the B chamber of the hydraulic cylinder 10 and the outlet of the second safety valve 42 is connected to the booster oil tank 9; the three oil ports of the bypass valve 5 are respectively connected to the A chamber of the hydraulic cylinder 10, the B chamber of the hydraulic cylinder 10, and the booster oil tank 9; the low-pressure sensor 7 and the filling valve 8 are both connected to the booster oil tank 9; n is a positive integer not less than 10.

[0030] The present invention achieves position holding of the hydraulic actuator when it is stopped or powered off by setting a first hydraulic control check valve 31 in the oil circuit between the oil port A of n servo motor pumps 1 and the A chamber of hydraulic cylinder 10, and setting a second hydraulic control check valve 32 in the oil circuit between the oil port B of n servo motor pumps 1 and the B chamber of hydraulic cylinder 10.

[0031] By bypassing the oil flow paths at port A and port B of the n servo motor pumps 1, a first replenishing check valve 21 and a second replenishing check valve 22 are respectively installed, enabling clustered oil replenishment for the n servo motor pumps 1. A first safety valve 41 is installed at the hydraulic cylinder 10A chamber, and a second safety valve 42 is installed at the hydraulic cylinder 10B chamber, limiting the maximum working pressure of the hydraulic actuator.

[0032] The pressure in chamber 10A of hydraulic cylinder 10 is monitored in real time by the first high-pressure pressure sensor 61; the pressure in chamber 10B of hydraulic cylinder 10 is monitored in real time by the second high-pressure pressure sensor 62. The hydraulic actuator is evacuated and filled with oil via the manual bypass valve 5; the cluster of n servo motor pumps 1 is replenished with oil via the booster tank 9, and leaked oil from the n servo motor pumps 1 is collected.

[0033] The pressure in the booster tank 9 is monitored by the low-pressure pressure sensor 7; the hydraulic actuator is evacuated and filled with oil by the filling valve 8.

[0034] The actuation process of a hydraulic actuator includes retraction and extension.

[0035] The specific process of the retraction action is as follows:

[0036] n servo motor pumps 1 receive the same control command from the host computer and simultaneously rotate in the forward direction to output flow. After converging, the flow enters the hydraulic cylinder 10A chamber through the first hydraulic control check valve 31, while simultaneously supplying control oil to the second hydraulic control check valve 32, which opens in the reverse direction. The oil in the hydraulic cylinder 10B chamber flows back to the converging oil circuit of the n servo motor pumps 1B port through the second hydraulic control check valve 32, and is used for the servo motor pumps to draw oil, realizing the retraction action of the hydraulic actuator. During the process, the second replenishing oil check valve 22 opens to replenish oil from the booster oil tank during the operation of the servo motor pumps. The first replenishing oil check valve 21, the first high-pressure safety valve 41, the second high-pressure safety valve 42, and the manual bypass valve 5 are closed.

[0037] The specific process of extending the arm is as follows:

[0038] n servo motor pumps 1 receive the same control command from the host computer and simultaneously rotate in opposite directions to output flow. After merging, the flow enters the hydraulic cylinder 10B chamber through the second hydraulic control check valve 32, while simultaneously supplying control oil to the first hydraulic control check valve 31, which opens in reverse. The oil in the hydraulic cylinder 10A chamber flows back to the merging oil circuit of the n servo motor pumps 1A port through the first hydraulic control check valve 31, and is used for the servo motor pumps to draw oil, thereby realizing the extension action of the hydraulic actuator. During the process, the first replenishment check valve 21 is opened to replenish oil from the booster oil tank during the operation of the servo motor pumps. The second replenishment check valve 22, the first high-pressure safety valve 41, the second high-pressure safety valve 42, and the manual bypass valve 5 are closed.

[0039] This invention employs a servo motor pump cluster solution, increasing the number of motor pumps in previously redundant electrostatic actuators from 2-4 to 10 or more, forming a motor pump cluster. One pump is 50kW, so 10 pumps would generate 500kW. Through flow rate integration and power superposition, a leap in power order is achieved, solving the electrification problem of ultra-high power hydraulic actuators. Compared to traditional valve-controlled hydraulic actuators, it avoids the challenges of ultra-high flow rate servo valves and ultra-high power hydraulic pump stations. It provides a new solution for ultra-high power actuators.

[0040] This design employs an integrated electro-hydraulic actuator scheme, incorporating a motor-pump cluster, functional valve group, oil tank, and hydraulic cylinders. In this scheme, the motor-pump cluster is divided into two groups, arranged in a linear array on the functional valve group. The functional valve group houses hydraulic valves, a booster oil tank, and other components. The functional valve group and hydraulic cylinders are arranged parallel to each other and fixed to the hydraulic cylinders via flanges at both ends, forming an integrated electro-hydraulic actuator. This design features a simple structure and convenient installation, use, and maintenance. Other layouts can also be designed according to specific requirements.

[0041] The servo motor pump cluster high-power electro-hydraulic actuator adopts a modular integrated design. The array-type motor pump cluster and other hydraulic components of the system are integrated into the functional valve block. The oil port of the rod chamber of the hydraulic cylinder is led to the oil port flange in the middle of the cylinder barrel through a pipeline. The pipeline and the hydraulic cylinder are an integral structure, and the oil port flanges of the two chambers of the hydraulic cylinder are kept on the same plane. The functional valve group is fixed to the hydraulic cylinder as a whole by bolts. The oil inlet and outlet manifold ports of the motor pump cluster are connected to the corresponding oil ports of the two chambers of the hydraulic cylinder, realizing the oil circuit communication of the hydraulic actuator, reducing leakage points and improving reliability.

[0042] The servo motor pump cluster high-power electro-hydraulic actuator only requires external connection to the motor power supply, resolver, and sensor cables, eliminating the need for external hydraulic pipelines. The device features a compact structure, high modularity, and easy assembly, making it suitable for work environments with limited installation space.

[0043] This invention achieves a leap in the power of electro-driven hydraulic actuators by integrating flow rates and superimposing power, solving the electrification problem of ultra-high power hydraulic actuators and providing a new solution for ultra-high power actuators. Compared with traditional valve-controlled actuators, it avoids the problems of ultra-high flow servo valves and ultra-high power hydraulic pump stations.

[0044] If any set of the motor pump cluster in this invention fails, it will not affect the normal function of the hydraulic actuator, thus achieving high power output of the actuator while improving reliability.

[0045] This invention allows for the easy assembly of electro-hydraulic actuators with different power levels by increasing or decreasing the number of arrays of motor pump clusters, making it easy to serialize and standardize the structure of electro-hydraulic actuators.

[0046] Although the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art can make possible changes and modifications to the technical solutions of the present invention by utilizing the methods and techniques disclosed above without departing from the spirit and scope of the present invention. Therefore, any simple modifications, equivalent changes and alterations made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solutions of the present invention shall fall within the protection scope of the technical solutions of the present invention.

Claims

1. A servo motor pump cluster type high-power electro-hydraulic actuator, characterized in that: Includes n servo motor pumps (1), first replenishing check valve (21), second replenishing check valve (22), first hydraulic control check valve (31), second hydraulic control check valve (32), first safety valve (41), second safety valve (42), bypass valve (5), first high pressure sensor (61), second high pressure sensor (62), low pressure sensor (7), filling valve (8), booster tank (9), and hydraulic cylinder (10); Among them, the oil ports A of n servo motor pumps (1) are connected to the oil inlet of the first hydraulic control check valve (31) after they converge; the oil outlet of the first hydraulic control check valve (31) is connected to the A chamber of the hydraulic cylinder (10); The first high-pressure sensor (61) is installed in chamber A of the hydraulic cylinder (10); the control port of the first hydraulic check valve (31) is connected to the port B of the n servo motor pumps (1); the port B of the n servo motor pumps (1) is connected to the inlet of the second hydraulic check valve (32); the outlet of the second hydraulic check valve (32) is connected to chamber B of the hydraulic cylinder (10); the second high-pressure sensor (62) is installed in chamber B of the hydraulic cylinder (10); the control port of the second hydraulic check valve (32) is connected to the port A of the n servo motor pumps (1); the outlet of the first replenishing check valve (21) is connected to the port A of the n servo motor pumps (1); the inlet of the first replenishing check valve (21) and the booster tank (9) are connected to ... first replenishing check valve (21) and the booster tank (9) are connected to the first replenishing check valve (21) and the first replenishing check valve (21) and the booster tank (9) are connected to the first replenishing check valve (21) and the first replenishing check valve (21) and the booster tank (9) are connected to the first replenishing check valve (21) and the first replenishing check valve (21) and the booster tank ( The oil outlet of the second replenishing check valve (22) is connected to the oil port B of n servo motor pumps (1) after the flow is combined; the oil inlet of the second replenishing check valve (22) is connected to the booster oil tank (9); the inlet of the first safety valve (41) is connected to the A chamber of the hydraulic cylinder (10), and the outlet of the first safety valve (41) is connected to the booster oil tank (9); the inlet of the second safety valve (42) is connected to the B chamber of the hydraulic cylinder (10), and the outlet of the second safety valve (42) is connected to the booster oil tank (9); the three oil ports of the bypass valve (5) are respectively connected to the A chamber of the hydraulic cylinder (10), the B chamber of the hydraulic cylinder (10), and the booster oil tank (9); the low pressure sensor (7) and the filling valve (8) are both connected to the booster oil tank (9); n is a positive integer not less than 10; By setting a first hydraulic control check valve (31) in the oil circuit between the oil port A of the n servo motor pumps (1) and the A chamber of the hydraulic cylinder (10), and setting a second hydraulic control check valve (32) in the oil circuit between the oil port B of the n servo motor pumps (1) and the B chamber of the hydraulic cylinder (10), the position holding of the hydraulic actuator in the state of shutdown or power failure can be realized. By bypassing the oil port A and oil port B of the n servo motor pumps (1) respectively, a first oil replenishment check valve (21) and a second oil replenishment check valve (22) are respectively set to achieve cluster oil replenishment for the n servo motor pumps (1); By setting a first safety valve (41) at chamber A of hydraulic cylinder (10) and a second safety valve (42) at chamber B of hydraulic cylinder (10), the maximum working pressure of the hydraulic actuator is limited; The pressure in chamber A of the hydraulic cylinder (10) is monitored in real time by the first high-pressure pressure sensor (61); the pressure in chamber B of the hydraulic cylinder (10) is monitored in real time by the second high-pressure pressure sensor (62). The hydraulic actuator is vacuumed and filled with oil by a manual bypass valve (5); the cluster of n servo motor pumps (1) is replenished with oil by a booster tank (9), and the leaked oil from the n servo motor pumps (1) is removed by a mobile phone. The pressure of the booster tank (9) is monitored by the low-pressure pressure sensor (7); the hydraulic actuator is evacuated and filled with oil by the filling valve (8); The actuation process of a hydraulic actuator includes retraction and extension actions; The specific process of the retraction action is as follows: n servo motor pumps (1) receive the same control command from the host computer and simultaneously rotate in the forward direction to output flow. After converging, the flow enters the A chamber of the hydraulic cylinder (10) through the first hydraulic control check valve (31) and simultaneously inputs control oil to the second hydraulic control check valve (32). The second hydraulic control check valve (32) opens in the reverse direction. The oil in the B chamber of the hydraulic cylinder (10) flows back to the converging oil circuit of the B port of the n servo motor pumps (1) through the second hydraulic control check valve (32) for the servo motor pumps to suck oil and realize the retraction action of the hydraulic actuator. During the process, the second replenishment check valve (22) opens to replenish oil from the booster tank during the operation of the servo motor pumps. The first replenishment check valve (21), the first high-pressure safety valve (41), the second high-pressure safety valve (42), and the manual bypass valve (5) are closed. The specific process of extending the arm is as follows: n servo motor pumps (1) receive the same control command from the host computer and rotate in opposite directions to output flow. After the flow merges, it enters the B chamber of the hydraulic cylinder (10) through the second hydraulic control check valve (32) and simultaneously inputs control oil to the first hydraulic control check valve (31). The first hydraulic control check valve (31) opens in reverse. The oil in the A chamber of the hydraulic cylinder (10) flows back to the A port of the n servo motor pumps (1) through the first hydraulic control check valve (31) to merge the oil circuit, which is used for the servo motor pumps to suck oil and realize the extension action of the hydraulic actuator. During the process, the first replenishment check valve (21) opens to replenish oil from the booster tank during the operation of the servo motor pumps. The second replenishment check valve (22), the first high-pressure safety valve (41), the second high-pressure safety valve (42), and the manual bypass valve (5) are closed. By combining the flow and superimposing the power of n servo motor pumps (1), the power of the electric drive hydraulic actuator is increased by an order of magnitude, achieving ultra-high power output of hundreds of kilowatts or more.

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