Energy storage type servo hydraulic high-speed proportional loading hydraulic system and method

Abstract

The invention provides an energy storage type servo hydraulic high-speed proportional loading hydraulic system and method. An inlet of a high-pressure electric pump set is connected with an oil tank, and an outlet of the high-pressure electric pump set is connected with a first high-pressure electromagnetic valve and a pressure reducing valve through a first one-way valve and a filtering module; an energy accumulator group and a pilot pressure regulating energy accumulator are connected behind the first high-pressure electromagnetic valve; the energy accumulator group is connected with a rod cavity of the loading hydraulic cylinder through a proportional servo pilot valve; the pilot pressure regulating energy accumulator is connected with the control end of the proportional servo pilot valve; the pressure reducing valve is connected with the loading hydraulic cylinder through a three-position four-way electromagnetic valve and a hydraulic lock; and a proportional overflow valve and a loading cylinder buffer overflow valve are arranged between the hydraulic lock and the loading hydraulic cylinder. When the large-flow proportional servo valve is used for loading, the opening degree of the large-flow proportional servo valve is accurately controlled, high-pressure oil stored in the energy accumulator set is rapidly released in a proportional mode, then the loading hydraulic cylinder is driven to achieve large-load acceleration traction, and the analog loading speed is achieved.

Description

Technical Field

[0001] The invention belongs to the technical field of hydraulic energy storage, and in particular relates to an energy storage type servo hydraulic high-speed proportional loading hydraulic system and method. Background Art

[0002] During the reliability inspection, maintenance or testing of aviation equipment, loading equipment is needed to carry out loading tests. The loading hydraulic cylinder in the loading equipment needs to be driven and controlled by the loading hydraulic system. During the specific loading test, the loading hydraulic cylinder needs to be driven to achieve accelerated traction of large loads in order to achieve the purpose of simulating the loading speed. Summary of the invention

[0003] The purpose of the present invention is to provide an energy storage servo hydraulic high-speed proportional loading hydraulic system and method. This hydraulic system adopts hydraulic energy storage technology, and charges and stores energy in the accumulator group through a small-power motor pump group in the system. When used for loading, the opening of the large-flow proportional servo valve is accurately controlled to proportionally and quickly release the high-pressure stored oil in the accumulator group, thereby driving the loading hydraulic cylinder to achieve accelerated traction of a large load to achieve a simulated loading speed.

[0004] In order to realize the above technical features, the object of the present invention is achieved as follows: an energy storage servo hydraulic high-speed proportional loading hydraulic system, comprising a high-pressure electric pump group, the inlet of the high-pressure electric pump group is connected to the oil tank, and the outlet of the high-pressure electric pump group is connected to the first high-pressure solenoid valve and the pressure reducing valve through a first one-way valve and a filter module; An accumulator group and a pilot pressure regulating accumulator are connected after the first high-pressure solenoid valve. The accumulator group is connected to the rod chamber of the loading hydraulic cylinder through a proportional servo pilot valve. The pilot pressure regulating accumulator is connected to the control end of the proportional servo pilot valve. The pressure reducing valve is connected to the loading hydraulic cylinder through a three-position four-way solenoid valve and a hydraulic lock; A proportional relief valve and a loading cylinder buffer relief valve are installed between the hydraulic lock and the loading hydraulic cylinder.

[0005] The filter module includes an oil suction filter, a first-level high-pressure oil filter, a second-level high-pressure oil filter and an oil return filter; the oil suction filter is installed at the inlet end of the high-pressure electric pump group; the first-level high-pressure oil filter and the second-level high-pressure oil filter are installed in series between the one-way valve and the first high-pressure solenoid valve; the oil return filter is installed on the oil return pipeline; a radiator is installed on the oil return pipeline and before the oil return filter.

[0006] A system safety valve for limiting the maximum system pressure is installed on the pipeline between the first one-way valve and the first high-pressure solenoid valve, and the other end of the system safety valve is connected to the radiator on the oil return pipeline.

[0007] The pressure reducing valve is used to adjust the debugging pressure and loading reset pressure of the loading hydraulic cylinder; The high-voltage electric pump group uses a variable frequency motor pump group, which can adjust the output flow of the pump group in real time and thus control the debugging and running speed of the loading hydraulic cylinder; The three-position four-way solenoid valve is used for debugging / resetting the oil circuit switching of the loading hydraulic cylinder; The filtering accuracies of the filtering modules are: 10 μm for the suction oil filter, 5 μm for the first-stage high-pressure oil filter, 3 μm for the second-stage high-pressure oil filter and 20 μm for the return oil filter.

[0008] It also includes a pressure monitoring system, which includes a first pressure sensor, a second pressure sensor, a third pressure sensor and a fourth pressure sensor; the first pressure sensor is installed on the pipeline between the first high-pressure solenoid valve and the accumulator group; the second pressure sensor is installed on the pipeline between the pilot pressure regulating accumulator and the proportional servo pilot valve; the third pressure sensor is installed on the pipeline between the proportional servo pilot valve and the loading hydraulic cylinder; the fourth pressure sensor is installed on the pipeline between the hydraulic lock and the loading hydraulic cylinder.

[0009] The pilot pressure regulating accumulator is connected to the proportional servo pilot valve via a pilot pressure relief valve and a second high-pressure solenoid valve; The first high-pressure solenoid valve, the second high-pressure solenoid valve and the proportional servo pilot valve are opened and closed to control the charging, releasing and unloading of the accumulator group; The proportional relief valve is used for proportional control of the oil flow diameter of the buffer cylinder oil when the accumulator group loads the loading hydraulic cylinder. When the loading hydraulic cylinder accelerates loading, the opening of the proportional relief valve is automatically controlled to increase proportionally to reduce the flow resistance of the return oil buffer. When the loading is completed and the loading hydraulic cylinder buffer decelerates, the opening is synchronously reduced to increase the return oil buffer pressure and realize reverse braking of the loading hydraulic cylinder.

[0010] A low liquid level sensor, a temperature sensor, an air filter and a liquid level gauge are installed inside the oil tank.

[0011] An operating method of an energy storage servo hydraulic high-speed proportional loading hydraulic system, the operating method is implemented by the energy storage servo hydraulic high-speed proportional loading hydraulic system, and includes the following operating conditions: Accumulator group charging control: Used to charge the accumulator group and limit the maximum pressure of the system through the system safety valve; Release and pressurization control of accumulator group: When the accumulator group releases high-pressure oil to pressurize the loading hydraulic cylinder, the loading flow is controlled by a large-flow proportional servo pilot valve, so that the high-pressure oil released by the accumulator group can be smoothly and continuously loaded into the rod chamber of the loading hydraulic cylinder, realizing continuous acceleration of the high-speed loading device; Loading hydraulic cylinder debugging / loading reset control: The oil circuit switching for loading hydraulic cylinder debugging and piston rod loading and resetting is switched by a three-position four-way solenoid valve, which cooperates with the proportional flow control of the variable frequency motor of the high-pressure electric pump group to adjust the running speed of the piston rod in real time; Unloading control of accumulator group: The accumulator group is unloaded through a dedicated second high-pressure solenoid valve. In order to prevent the presence of high-pressure oil in the accumulator group when the accumulator group is unloaded, a throttling device is set in the unloading oil circuit to limit the flow of the high-pressure oil in the accumulator group alone, so as to prevent the high-pressure oil from being unloaded to the oil tank instantly and at a large flow rate.

[0012] The specific process of pressure charging control of the accumulator group is as follows: The oil is pumped by the high-pressure electric pump group, and the high-pressure oil is charged into the accumulator group and the pilot pressure regulating accumulator through the high-pressure electric pump group, the first non-return valve, the first high-pressure oil filter, the second high-pressure oil filter, and the first high-pressure solenoid valve in sequence. During the charging process, the system pressure is limited by the system safety valve; The specific process of release and pressurization control of the accumulator group is as follows: The high-pressure oil is released through the accumulator group, and the high-pressure oil enters the rod chamber of the loading hydraulic cylinder through the proportional servo pilot valve. The proportional servo pilot valve is controlled by the pilot pressure-regulating accumulator, and the high-pressure oil supply of the accumulator group is controlled by the proportional servo pilot valve, so that the high-pressure oil released by the accumulator group can be smoothly and continuously loaded into the rod chamber of the loading hydraulic cylinder, thereby realizing continuous acceleration of the high-speed loading device.

[0013] The specific process of debugging / loading reset control of the loading hydraulic cylinder is as follows: The oil is pumped by the high-pressure electric pump group. The high-pressure oil enters the three-position four-way solenoid valve through the high-pressure electric pump group, the first one-way valve, the first-stage high-pressure oil filter, the second-stage high-pressure oil filter, and the pressure reducing valve in turn. The debugging / loading reset control of the loading hydraulic cylinder is controlled by switching the three-position four-way solenoid valve. At the same time, the proportional flow control of the high-pressure electric pump group is used to adjust the running speed of the piston rod in real time. The specific process of unloading control of the accumulator group is as follows: When the accumulator group needs to be unloaded, the unloading process is controlled by the second high-pressure solenoid valve, and a throttling device is provided in the unloading oil circuit to limit the flow of the high-pressure oil of the accumulator group alone, thereby preventing the high-pressure oil from being unloaded to the oil tank instantaneously and at a large flow rate.

[0014] The present invention has the following beneficial effects: 1. The hydraulic system of the loading equipment of the present invention is mainly a hydraulic energy storage technology. The accumulator group is pressurized and stored by a small-power motor pump group in the system. When used for loading, the system accurately controls the opening of a large-flow proportional servo valve to proportionally and quickly release the high-pressure stored oil in the accumulator group, thereby driving the loading hydraulic cylinder to achieve accelerated traction of a large load to achieve a simulated loading speed.

[0015] 2. The high-pressure electric pump group of the present invention has two main functions: one is to charge and store energy in the accumulator group and the pilot pressure regulating accumulator; the other is to load the stroke debugging of the hydraulic cylinder and prepare the loading position of the piston rod before loading. The system uses a variable frequency motor pump group, which can adjust the output flow of the pump group in real time and thus control the debugging operation speed of the cylinder.

[0016] 3. It can be used for oil filtration in hydraulic system through the filter module.

[0017] 4. The system safety valve is used to limit the maximum system pressure, that is, to limit the maximum pressure for charging and storing energy in the accumulator group, thereby ensuring the safety of the system.

[0018] 5. The pressure reducing valve is used to adjust the debugging pressure and loading reset pressure of the loading hydraulic cylinder.

[0019] 6. A three-position four-way solenoid valve is used to load the hydraulic cylinder for debugging / resetting the oil circuit switching.

[0020] 7. The proportional relief valve is used to proportionally control the oil flow diameter of the buffer cylinder oil when the accumulator group is used to load the loading hydraulic cylinder. When the hydraulic cylinder accelerates loading, the opening of the proportional relief valve is automatically controlled to increase proportionally to reduce the flow resistance of the return oil buffer. When the loading is completed and the hydraulic cylinder buffer is decelerated, the opening is synchronously reduced to increase the return oil buffer pressure and realize the reverse braking of the hydraulic cylinder.

[0021] 8. The reverse brake buffer pressure of the hydraulic cylinder is mechanically limited by the loading cylinder buffer overflow valve. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The present invention will be further described below in conjunction with the accompanying drawings and embodiments.

[0023] Figure 1 It is a hydraulic system diagram of the present invention.

[0024] Figure 2 This is a diagram of the pressure charging control process of the accumulator group of the present invention.

[0025] Figure 3 This is a diagram of the release and pressurization control process of the accumulator group of the present invention.

[0026] Figure 4This is a diagram of the debugging / loading reset control process of the loading hydraulic cylinder of the present invention.

[0027] Figure 5 This is a diagram of the unloading control process of the accumulator group of the present invention.

[0028] In the figure: 1. Oil suction filter; 2. High-pressure electric pump group; 3. First non-return valve; 4. First-stage high-pressure oil filter; 5. Second-stage high-pressure oil filter; 6. Pressure reducing valve; 7. First high-pressure solenoid valve; 8. First pressure sensor; 9. Accumulator group; 10. Three-position four-way solenoid valve; 11. System safety valve; 12. Low liquid level sensor; 13. Temperature sensor; 14. Air filter; 15. Liquid level gauge; 16. Return oil filter; 17. Radiator; 18. Hydraulic lock; 19. Second non-return valve; 20. Pilot pressure regulating accumulator; 21. Second pressure sensor; 22. Pilot pressure relief valve; 23. Second high-pressure solenoid valve; 24. Proportional servo pilot valve; 25. Third pressure sensor; 26. Loading hydraulic cylinder; 27. Fourth pressure sensor; 28. Proportional overflow valve; 29. ​​Loading cylinder buffer overflow valve. DETAILED DESCRIPTION

[0029] The embodiments of the present invention are further described below in conjunction with the accompanying drawings.

[0030] Embodiment 1: See also Figure 1-5 A storage servo hydraulic high-speed proportional loading hydraulic system includes a high-pressure electric pump group 2, the inlet of the high-pressure electric pump group 2 is connected to the oil tank, and the outlet of the high-pressure electric pump group 2 is connected to the first high-pressure solenoid valve 7 and the pressure reducing valve 6 through the first one-way valve 3 and the filter module; the accumulator group 9 and the pilot pressure regulating accumulator 20 are connected after the first high-pressure solenoid valve 7, and the accumulator group 9 is connected to the rod chamber of the loading hydraulic cylinder 26 through the proportional servo pilot valve 24; the pilot pressure regulating accumulator 20 is connected to the control end of the proportional servo pilot valve 24; the pressure reducing valve 6 is connected to the loading hydraulic cylinder 26 through the three-position four-way solenoid valve 10 and the hydraulic lock 18; a proportional overflow valve 28 and a loading cylinder buffer overflow valve 29 are installed between the hydraulic lock 18 and the loading hydraulic cylinder 26. This hydraulic system adopts hydraulic energy storage technology. The accumulator group is charged and stored by a small-power motor pump group in the system. When used for loading, the opening of the large-flow proportional servo valve is precisely controlled to proportionally and quickly release the high-pressure stored oil in the accumulator group, thereby driving the loading hydraulic cylinder to achieve accelerated traction of large loads to achieve simulated loading speed.

[0031] Furthermore, the filter module includes an oil suction filter 1, a primary high-pressure oil filter 4, a secondary high-pressure oil filter 5 and a return oil filter 16; the oil suction filter 1 is installed at the inlet end of the high-pressure electric pump group 2; the primary high-pressure oil filter 4 and the secondary high-pressure oil filter 5 are installed in series between the check valve 3 and the first high-pressure solenoid valve 7; the return oil filter 16 is installed on the return oil pipeline; a radiator 17 is installed on the return oil pipeline and before the return oil filter 16. The above-mentioned filter module can be used to effectively filter the oil of the system.

[0032] Furthermore, a system safety valve 11 for limiting the maximum system pressure is installed on the pipeline between the first one-way valve 3 and the first high-pressure solenoid valve 7, and the other end of the system safety valve 11 is connected to the radiator 17 on the oil return pipeline, that is, the maximum pressure for charging and storing energy in the accumulator group 9 is limited, thereby ensuring the safety of the system.

[0033] Furthermore, the pressure reducing valve 6 is used to adjust the debugging pressure and the loading reset pressure of the loading hydraulic cylinder.

[0034] Furthermore, the high-pressure electric pump group 2 uses a variable frequency motor pump group, which can adjust the output flow of the pump group in real time and thus control the debugging operation speed of the loading hydraulic cylinder 26.

[0035] Furthermore, the three-position four-way solenoid valve 10 is used for switching the debugging / resetting oil circuit of the loading hydraulic cylinder 26 , thereby controlling the action of the loading hydraulic cylinder 26 .

[0036] Furthermore, the filtering accuracies of the filtering modules are: 10 μm for the oil suction filter 1, 5 μm for the primary high-pressure oil filter 4, 3 μm for the secondary high-pressure oil filter 5 and 20 μm for the return oil filter 16. The above filtering accuracies ensure the oil filtering effect.

[0037] Furthermore, it also includes a pressure monitoring system, which includes a first pressure sensor 8, a second pressure sensor 21, a third pressure sensor 25 and a fourth pressure sensor 27; the first pressure sensor 8 is installed on the pipeline between the first high-pressure solenoid valve 7 and the accumulator group 9; the second pressure sensor 21 is installed on the pipeline between the pilot pressure regulating accumulator 20 and the proportional servo pilot valve 24; the third pressure sensor 25 is installed on the pipeline between the proportional servo pilot valve 24 and the loading hydraulic cylinder 26; the fourth pressure sensor 27 is installed on the pipeline between the hydraulic lock 18 and the loading hydraulic cylinder 26. The pressure monitoring system mentioned above ensures the pressure display during the system operation, thereby ensuring the safety of the system operation.

[0038] Furthermore, the pilot pressure regulating accumulator 20 is connected to the proportional servo pilot valve 24 through the pilot pressure relief valve 22 and the second high-pressure solenoid valve 23; the first high-pressure solenoid valve 7, the second high-pressure solenoid valve 23 and the proportional servo pilot valve 24 are opened and closed to control the charging, releasing and unloading of the accumulator group. The proportional servo pilot valve 24 is controlled by the pilot pressure regulating accumulator 20, and the high-pressure oil supply of the accumulator group 9 is controlled by the proportional servo pilot valve 24, so that the high-pressure oil released by the accumulator group 9 can be smoothly and continuously loaded into the rod chamber of the loading hydraulic cylinder 26, so as to realize the continuous acceleration of the high-speed loading device.

[0039] Furthermore, the proportional relief valve 28 is used for proportional control of the oil flow diameter of the buffer cylinder oil when the accumulator group 9 loads the loading hydraulic cylinder 26. When the loading hydraulic cylinder 26 accelerates loading, the opening of the proportional relief valve 28 is automatically controlled to increase proportionally to reduce the flow resistance of the return oil buffer. When the loading is completed and the loading hydraulic cylinder 26 buffers and decelerates, the opening is synchronously reduced to increase the return oil buffer pressure and realize reverse braking of the loading hydraulic cylinder 26.

[0040] Furthermore, a low liquid level sensor 12, a temperature sensor 13, an air filter 14 and a liquid level meter 15 are installed inside the oil tank. The safety of the oil tank is ensured by the above accessories.

[0041] Embodiment 2: See also Figure 2-5 , an operating method of an energy storage servo hydraulic high-speed proportional loading hydraulic system, the operating method is implemented by the energy storage servo hydraulic high-speed proportional loading hydraulic system, and includes the following operating conditions: Accumulator group charging control: Used to charge the accumulator group 9 and limit the maximum pressure of the system through the system safety valve 11; Release and pressurization control of accumulator group: When the accumulator group 9 releases high-pressure oil to pressurize the loading hydraulic cylinder 26, the loading flow is controlled by the large-flow proportional servo pilot valve 24, so that the high-pressure oil released by the accumulator group 9 can be smoothly and continuously loaded into the rod chamber of the loading hydraulic cylinder 26, thereby realizing continuous acceleration of the high-speed loading device; Loading hydraulic cylinder debugging / loading reset control: The oil circuit switching for debugging the loading hydraulic cylinder 26 and loading and resetting the piston rod is switched by the three-position four-way solenoid valve 10, which cooperates with the proportional flow control of the variable frequency motor of the high-pressure electric pump group to adjust the running speed of the piston rod in real time; Unloading control of accumulator group: The accumulator group is unloaded through a dedicated second high-pressure solenoid valve 23. In order to prevent the presence of high-pressure oil in the accumulator group when the accumulator group is unloaded, a throttling device is provided in the unloading oil circuit to limit the flow of the high-pressure oil in the accumulator group alone, so as to prevent the high-pressure oil from being unloaded to the oil tank instantaneously and at a large flow rate.

[0042] Embodiment 3: See also Figure 2 The specific process of pressure charging control of the accumulator group is as follows: The high-pressure electric pump group 2 is used to pump oil, and the high-pressure oil is sequentially charged into the accumulator group 9 and the pilot pressure regulating accumulator 20 through the high-pressure electric pump group 2, the first non-return valve 3, the first high-pressure oil filter 4, the second high-pressure oil filter 5, and the first high-pressure solenoid valve 7. During the charging process, the system pressure is limited by the system safety valve 11; Embodiment 4: See also Figure 3 The specific process of release and pressurization control of the accumulator group is as follows: The high-pressure oil is released through the accumulator group 9, and the high-pressure oil enters the rod chamber of the loading hydraulic cylinder 26 through the proportional servo pilot valve 24. The proportional servo pilot valve 24 is controlled by the pilot pressure-regulating accumulator 20, and the high-pressure oil supply of the accumulator group 9 is controlled by the proportional servo pilot valve 24, so that the high-pressure oil released by the accumulator group 9 can be smoothly and continuously loaded into the rod chamber of the loading hydraulic cylinder 26, thereby realizing continuous acceleration of the high-speed loading device.

[0043] Embodiment 5: See also Figure 4 The specific process of debugging / loading reset control of the loading hydraulic cylinder is as follows: The high-pressure electric pump group 2 is used to pump oil, and the high-pressure oil enters the three-position four-way solenoid valve 10 through the high-pressure electric pump group 2, the first one-way valve 3, the first-level high-pressure oil filter 4, the second-level high-pressure oil filter 5, and the pressure reducing valve 6 in sequence. The three-position four-way solenoid valve 10 is switched to control the debugging / loading reset control of the loading hydraulic cylinder 26. At the same time, the proportional flow control of the high-pressure electric pump group 2 is used to adjust the running speed of the piston rod in real time; Embodiment 6: See also Figure 5 The specific process of unloading control of the accumulator group is as follows: When the accumulator group 9 needs to be unloaded, the unloading process is controlled by the second high-pressure solenoid valve 23, and a throttling device is provided in the unloading oil circuit to limit the flow of the high-pressure oil of the accumulator group 9 alone, thereby preventing the high-pressure oil from being unloaded to the oil tank instantaneously and at a large flow rate.

Claims

1. An energy storage servo hydraulic high-speed proportional loading hydraulic system, characterized in that: It comprises a high-pressure electric pump group (2), wherein the inlet of the high-pressure electric pump group (2) is connected to the oil tank, and the outlet of the high-pressure electric pump group (2) is connected to the first high-pressure electromagnetic valve (7) and the pressure reducing valve (6) via a first one-way valve (3) and a filter module; An accumulator group (9) and a pilot pressure regulating accumulator (20) are connected after the first high-pressure solenoid valve (7); the accumulator group (9) is connected to a rod chamber of a loading hydraulic cylinder (26) via a proportional servo pilot valve (24); the pilot pressure regulating accumulator (20) is connected to a control end of the proportional servo pilot valve (24); The pressure reducing valve (6) is connected to the loading hydraulic cylinder (26) via a three-position four-way solenoid valve (10) and a hydraulic lock (18); A proportional overflow valve (28) and a loading cylinder buffer overflow valve (29) are installed between the hydraulic lock (18) and the loading hydraulic cylinder (26).

2. According to claim 1, an energy storage servo hydraulic high-speed proportional loading hydraulic system is characterized in that: The filter module comprises an oil suction filter (1), a primary high-pressure oil filter (4), a secondary high-pressure oil filter (5) and an oil return filter (16); the oil suction filter (1) is installed at the inlet end of the high-pressure electric pump group (2); the primary high-pressure oil filter (4) and the secondary high-pressure oil filter (5) are installed in series between the one-way valve (3) and the first high-pressure solenoid valve (7); the oil return filter (16) is installed on the oil return pipeline; and a radiator (17) is installed on the oil return pipeline and before the oil return filter (16).

3. According to claim 2, an energy storage servo hydraulic high-speed proportional loading hydraulic system is characterized in that: A system safety valve (11) for limiting the maximum pressure of the system is installed on the pipeline between the first one-way valve (3) and the first high-pressure solenoid valve (7), and the other end of the system safety valve (11) is connected to a radiator (17) on the oil return pipeline.

4. According to claim 2, an energy storage servo hydraulic high-speed proportional loading hydraulic system is characterized in that: The pressure reducing valve (6) is used to adjust the debugging pressure and the loading reset pressure of the loading hydraulic cylinder; The high-pressure electric pump group (2) uses a variable frequency motor pump group, which can adjust the output flow of the pump group in real time and thus control the debugging operation speed of the loading hydraulic cylinder (26); The three-position four-way solenoid valve (10) is used for debugging / resetting the oil circuit switching of the loading hydraulic cylinder (26); The filtering accuracies of the filtering modules are: the oil suction filter (1) is 10 μm, the first-stage high-pressure oil filter (4) is 5 μm, the second-stage high-pressure oil filter (5) is 3 μm, and the return oil filter (16) is 20 μm.

5. According to claim 1, the energy storage servo hydraulic high-speed proportional loading hydraulic system is characterized by: The invention also comprises a pressure monitoring system, wherein the pressure monitoring system comprises a first pressure sensor (8), a second pressure sensor (21), a third pressure sensor (25) and a fourth pressure sensor (27); the first pressure sensor (8) is installed on the pipeline between the first high-pressure solenoid valve (7) and the accumulator group (9); the second pressure sensor (21) is installed on the pipeline between the pilot pressure regulating accumulator (20) and the proportional servo pilot valve (24); the third pressure sensor (25) is installed on the pipeline between the proportional servo pilot valve (24) and the loading hydraulic cylinder (26); and the fourth pressure sensor (27) is installed on the pipeline between the hydraulic lock (18) and the loading hydraulic cylinder (26).

6. The energy storage servo hydraulic high-speed proportional loading hydraulic system according to claim 1, characterized in that: The pilot pressure regulating accumulator (20) is connected to the proportional servo pilot valve (24) via a pilot pressure relief valve (22) and a second high-pressure solenoid valve (23); The first high-pressure solenoid valve (7), the second high-pressure solenoid valve (23) and the proportional servo pilot valve (24) are opened and closed to control the charging, releasing and unloading of the accumulator group; The proportional relief valve (28) is used for proportional control of the oil passage diameter of the buffer cylinder oil when the accumulator group (9) loads the loading hydraulic cylinder (26). When the loading hydraulic cylinder (26) accelerates loading, the opening of the proportional relief valve (28) is automatically controlled to increase in proportion to reduce the flow resistance of the return oil buffer. When loading is completed and the loading hydraulic cylinder (26) buffers and decelerates, the opening is synchronously reduced to increase the return oil buffer pressure, thereby realizing reverse braking of the loading hydraulic cylinder (26).

7. The energy storage servo hydraulic high-speed proportional loading hydraulic system according to claim 1, characterized in that: A low liquid level sensor (12), a temperature sensor (13), an air filter (14) and a liquid level meter (15) are installed inside the oil tank.

8. An operating method of an energy storage servo hydraulic high-speed proportional loading hydraulic system, characterized in that: The operation method is implemented by using the energy storage servo hydraulic high-speed proportional loading hydraulic system described in any one of claims 1 to 7, and includes the following operating conditions: Accumulator group charging control: It is used to charge the accumulator group (9) and to limit the maximum pressure of the system through the system safety valve (11); Release and pressurization control of accumulator group: When the accumulator group (9) releases high-pressure oil to pressurize the loading hydraulic cylinder (26), the loading flow rate is controlled by a large-flow proportional servo pilot valve (24), so that the high-pressure oil released by the accumulator group (9) can be smoothly and continuously loaded into the rod chamber of the loading hydraulic cylinder (26), thereby achieving continuous acceleration of the high-speed loading device; Debugging / loading reset control of loading hydraulic cylinder: The oil circuit switching for debugging the loading hydraulic cylinder (26) and loading and resetting the piston rod is switched by a three-position four-way solenoid valve (10), and the proportional flow control of the variable frequency motor of the high-pressure electric pump group is coordinated to adjust the running speed of the piston rod in real time; Unloading control of accumulator group: The accumulator group is unloaded through a dedicated second high-pressure solenoid valve (23). In order to prevent the presence of high-pressure oil in the accumulator group when the accumulator group is unloaded, a throttling device is provided in the unloading oil circuit to limit the flow of the high-pressure oil in the accumulator group alone, so as to prevent the high-pressure oil from being unloaded to the oil tank instantaneously and at a large flow rate.

9. The operating method of the energy storage servo hydraulic high-speed proportional loading hydraulic system according to claim 8, characterized in that: The specific process of pressure charging control of the accumulator group is as follows: The high-pressure electric pump group (2) is used to pump oil, and the high-pressure oil is sequentially charged into the accumulator group (9) and the pilot pressure regulating accumulator (20) through the high-pressure electric pump group (2), the first non-return valve (3), the first high-pressure oil filter (4), the second high-pressure oil filter (5), and the first high-pressure solenoid valve (7). During the charging process, the system pressure is limited by the system safety valve (11); The specific process of release and pressurization control of the accumulator group is as follows: High-pressure oil is released through the accumulator group (9), and the high-pressure oil enters the rod chamber of the loading hydraulic cylinder (26) through the proportional servo pilot valve (24). The proportional servo pilot valve (24) is controlled by the pilot pressure regulating accumulator (20), and the high-pressure oil supply of the accumulator group (9) is controlled through the proportional servo pilot valve (24), so that the high-pressure oil released by the accumulator group (9) can be stably and continuously loaded into the rod chamber of the loading hydraulic cylinder (26), thereby realizing continuous acceleration of the high-speed loading device.

10. The operating method of the energy storage servo hydraulic high-speed proportional loading hydraulic system according to claim 8, characterized in that: The specific process of debugging / loading reset control of the loading hydraulic cylinder is as follows: The high-pressure electric pump group (2) is used to pump oil, and the high-pressure oil enters the three-position four-way solenoid valve (10) through the high-pressure electric pump group (2), the first non-return valve (3), the first high-pressure oil filter (4), the second high-pressure oil filter (5), and the pressure reducing valve (6) in sequence. The three-position four-way solenoid valve (10) is switched to control the debugging / loading reset control of the loading hydraulic cylinder (26). At the same time, the proportional flow control of the high-pressure electric pump group (2) is used to adjust the running speed of the piston rod in real time. The specific process of unloading control of the accumulator group is as follows: When the accumulator group (9) needs to be unloaded, the unloading process is controlled by the second high-pressure solenoid valve (23), and a throttling device is provided in the unloading oil circuit to limit the flow of the high-pressure oil of the accumulator group (9) alone, thereby preventing the high-pressure oil from being unloaded to the oil tank instantaneously and at a large flow rate.

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