Hydraulic pressure supercharger hydraulic control system and control method
By designing a hydraulic pressure supercharger hydraulic control system for steel pipe hydraulic test, the problems of large pressure range and high equipment energy consumption caused by different steel pipe specifications in the prior art are solved, and the rapid conversion of high-pressure water pressure is achieved. and rapid boost, reducing energy consumption and maintenance costs.
Patent Information
- Application Number
- CN202411550843.9
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2024-11-01
- Publication Date
- 2025-02-21
AI Technical Summary
During the steel pipe hydraulic test, due to the different specifications of the steel pipe, the required pressure range is large, which causes the existing hydraulic test machines to be equipped with multiple pressure oil pumps, which has high energy consumption and high maintenance costs.
A hydraulic control system for hydraulic supercharger is designed, including a large chamber reversing module, a small chamber reversing module, a large chamber pressure relief module, a small chamber pressure relief module, a pressure sensor, an overflow valve, a pressure measuring joint, and an increase The pressure device, pressure oil port and return oil port can control the hydraulic system through a single low-power pressure source.
The rapid conversion and rapid boost of the hydraulic pressure test pressure from a low-pressure water pressure of ≤20MPa to a high-pressure water pressure of 20-200MPa is achieved, which reduces the energy consumption of the equipment, simplifies the structure, and improves the flexibility of pressure control.
Smart Images
Figure CN119491845A_ABST
Abstract
Description
Technical Field
[0001] The invention belongs to the technical field of pressurization of a steel pipe water pressure testing machine, and in particular relates to a hydraulic control system and a control method of a water pressure booster. Background Art
[0002] During the hydraulic test of steel pipes, due to the different specifications of steel pipes such as wall thickness, diameter, length, etc., the required pressure of the steel pipes is also different, and the pressure variation range is large, usually varying in the range of 10-200MPa. At the same time, due to the large variation range of steel pipe specifications, the range of pressure increase volume to reach the target pressure is also large. For example, the required pressure increase volume of a 10m long Ф88.9mm steel pipe at 160MPa is 3.3L, while the required pressure increase volume of a 15m long Ф610mm steel pipe at 40MPa is 53.6L.
[0003] Since the boosting volume, target pressure and boosting speed of steel pipes of different specifications are different, the hydraulic system of a single station of the same hydraulic testing machine usually needs to be equipped with at least two pressure oil pumps (high-pressure oil pump, low-pressure oil pump) to meet the changes in the target pressure and flow of the hydraulic system. The equipment consumes a lot of energy and has high maintenance costs. Summary of the invention
[0004] In order to solve the above technical problems, the present invention provides a hydraulic control system and a control method for a water pressure booster.
[0005] The technical solution adopted by the present invention is: A hydraulic pressure booster hydraulic control system, comprising a large chamber reversing module, a small chamber reversing module, a large chamber pressure relief module, a small chamber pressure relief module, a relief valve, a booster, a pressure oil port and an oil return port; The supercharger is at least provided with a large oil chamber, a small oil chamber, a high-pressure water interface, and a piston connected to the large oil chamber and the small oil chamber and movable up and down in the large oil chamber and the small oil chamber. The small oil chamber is provided with a supercharger oil chamber small chamber interface, and the large oil chamber is provided with a supercharger oil chamber large chamber interface. The large cavity reversing module at least includes a first electromagnetic reversing valve and a first cartridge valve, and the first electromagnetic reversing valve and the first cartridge valve are connected through a first control cover plate; the first cartridge valve has a control oil port A2 and two oil ports A1 and A3; The small cavity reversing module at least includes a second electromagnetic reversing valve and a second cartridge valve, and the second electromagnetic reversing valve and the second cartridge valve are connected through a second control cover plate; the second cartridge valve has a control oil port B2 and three oil ports B1, B3, and B4; The large chamber pressure relief module at least includes a third electromagnetic reversing valve and a third cartridge valve, and the third electromagnetic reversing valve and the third cartridge valve are connected through a third control cover plate; the third cartridge valve has a control oil port C2 and two oil ports C1 and C3; The small cavity pressure relief module at least includes a fourth electromagnetic reversing valve and a fourth cartridge valve, and the fourth electromagnetic reversing valve and the fourth cartridge valve are connected through a fourth control cover plate; the fourth cartridge valve has a control oil port D2 and three oil ports D1, D3, and D4; The large cavity interface of the supercharger oil chamber is connected with the third electromagnetic reversing valve, the C1 port of the third cartridge valve, and the A3 port of the first cartridge valve in sequence; the small cavity interface of the supercharger oil chamber is connected with the overflow valve, the fourth electromagnetic reversing valve, the D1 port of the fourth cartridge valve, and the B3 port of the second cartridge valve in sequence; the pressure oil port is connected with the first electromagnetic reversing valve, the A1 port of the first cartridge valve, the second electromagnetic reversing valve, and the B1 and B4 ports of the second cartridge valve in sequence; the return oil port is connected with the first electromagnetic reversing valve, the second electromagnetic reversing valve, the third electromagnetic reversing valve, the fourth electromagnetic reversing valve, the C3 port of the third cartridge valve, and the D3 and D4 ports of the fourth cartridge valve in sequence; the A2 port of the first cartridge valve is connected with the first electromagnetic reversing valve; the B2 port of the second cartridge valve is connected with the second electromagnetic reversing valve; the C2 port of the third cartridge valve is connected with the third electromagnetic reversing valve; and the D2 port on the fourth cartridge valve is connected with the fourth electromagnetic reversing valve.
[0006] It also includes a pressure sensor; the pressure sensor is connected to the external transmission pipeline of the large cavity interface of the supercharger oil chamber; the large cavity interface of the supercharger oil chamber is connected to the third electromagnetic reversing valve, the C1 port of the third cartridge valve, and the A3 port of the first cartridge valve in sequence through the pressure sensor.
[0007] It also includes a pressure measuring joint; the pressure measuring joint is respectively connected to the large cavity interface of the supercharger oil cavity, the small cavity interface of the supercharger oil cavity, the large cavity reversing module, the small cavity reversing module, the large cavity pressure relief module, the small cavity pressure relief module and the overflow valve.
[0008] The pressure channel of the A2 port of the first solenoid reversing valve and the first cartridge valve is placed in the first control cover plate; the pressure channel of the B2 port of the second solenoid reversing valve and the second cartridge valve is placed in the second control cover plate; the pressure channel of the C2 port of the third solenoid reversing valve and the third cartridge valve is placed in the third control cover plate; the pressure channel of the D2 port of the fourth solenoid reversing valve and the fourth cartridge valve is placed in the fourth control cover plate.
[0009] The booster is composed of a single hydraulic cylinder and a plunger sleeve. One side of the hydraulic cylinder has two interfaces, namely, a large-chamber interface of the booster oil chamber and a small-chamber interface of the booster oil chamber, and one side of the plunger sleeve has a high-pressure water interface.
[0010] A displacement sensor is installed on the side of the hydraulic cylinder.
[0011] A high-pressure water pressure hydraulic control method, using a water pressure booster hydraulic control system, comprises the following steps: Step 1: Implement hydraulic control of high-pressure water pressure and proceed to step 2; implement hydraulic control of low-pressure water pressure and proceed to step 3; Step 2: Liquid enters the small oil chamber of the supercharger, the second solenoid reversing valve and the third solenoid reversing valve are energized, the first solenoid reversing valve and the fourth solenoid reversing valve are de-energized, and the high-pressure oil enters the small oil chamber of the supercharger from the second cartridge valve, and the oil in the large oil chamber of the supercharger enters the oil return port through the C3 port of the third cartridge valve, and the supercharger piston moves upward; Liquid enters the large oil chamber of the supercharger, the second and third solenoid reversing valves lose power, the first and fourth solenoid reversing valves gain power, and the high-pressure oil enters the large oil chamber of the supercharger from the A3 port of the first cartridge valve, and the oil in the small oil chamber of the supercharger enters the oil return port through the D4 port of the fourth cartridge valve, and the piston of the supercharger moves downward to complete the high-pressure water pressure boosting; Step 3: Liquid enters the small oil chamber of the supercharger, the second solenoid reversing valve and the third solenoid reversing valve are energized, the first solenoid reversing valve and the fourth solenoid reversing valve are de-energized, and the high-pressure oil enters the small oil chamber of the supercharger from the second cartridge valve, and the oil in the large oil chamber of the supercharger enters the oil return port through the C3 port of the third cartridge valve, and the piston of the supercharger moves upward; The large and small oil chambers of the supercharger are filled with liquid at the same time, the third solenoid reversing valve and the fourth solenoid reversing valve lose power, the first solenoid reversing valve and the second solenoid reversing valve are energized, and the high-pressure oil enters the large oil chamber of the supercharger from the A3 port of the first cartridge valve and enters the small oil chamber of the supercharger from the B3 port of the second cartridge valve. Due to the difference in area between the rod chamber and the rodless chamber of the supercharger, the piston of the supercharger moves downward, and the high-pressure oil in the small oil chamber of the supercharger is squeezed, and enters the large oil chamber of the supercharger through the second cartridge valve and the first cartridge valve, accelerating the downward movement of the supercharger piston and quickly achieving 1:1 oil-water supercharging.
[0012] The high pressure ranges from 20 to 200 MPa.
[0013] The low pressure range is ≤20MPa.
[0014] The beneficial effects of the present invention are: (1) The hydraulic control system of the water pressure booster of the present invention is composed of a large chamber reversing module, a small chamber reversing module, a large chamber pressure relief module, a small chamber pressure relief module, a pressure sensor, a relief valve, a pressure measuring joint, a booster, a pressure oil port and an oil return port. The present invention can use a single low-power pressure source to control the hydraulic system to achieve functions such as rapid conversion and rapid pressure increase of the water pressure test pressure from a low pressure of ≤20MPa to a high pressure of 20-200MPa.
[0015] (2) The present invention has a simple structure, a flexible pressure control method, and saves energy.
[0016] (3) The provision of the pressure measuring joint in the present invention facilitates the pressure testing during maintenance and brings convenience to maintenance.
[0017] The above description is only an overview of the technical solution of the present invention. In order to more clearly understand the technical means of the present invention and implement it according to the contents of the specification, the following is a detailed description of the preferred embodiments of the present invention in conjunction with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS
[0018] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.
[0019] Figure 1 It is the hydraulic principle diagram of the present invention.
[0020] In the figure: 1. Large cavity reversing module; 101. First solenoid reversing valve; 102. First control cover plate; 103. First cartridge valve; 2. Small cavity reversing module; 201. Second solenoid reversing valve; 202. Second control cover plate; 203. Second cartridge valve; 3. Pressure sensor; 4. Large cavity pressure relief module; 401. Third cartridge valve; 402. Third control cover plate; 403. Third solenoid reversing valve; 5. Small cavity pressure relief module; 501. Fourth cartridge valve; 502. Fourth control cover plate; 503. Fourth solenoid reversing valve; 6. Overflow valve; 7. Pressure measuring joint; 8. Supercharger; 801. Displacement sensor; P-pressure oil port, T-return oil port, X1A-supercharger oil chamber large cavity interface, X1B-supercharger oil chamber small cavity interface, X2-high pressure water interface. DETAILED DESCRIPTION
[0021] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.
[0022] Embodiment 1: according to Figure 1 A hydraulic pressure booster hydraulic control system shown includes a large chamber reversing module 1, a small chamber reversing module 2, a large chamber pressure relief module 4, a small chamber pressure relief module 5, a relief valve 6, a booster 8, a pressure oil port P and an oil return port T; The supercharger 8 is at least provided with a large oil chamber, a small oil chamber, a high-pressure water interface X2, and a piston connected to the large oil chamber and the small oil chamber and movable up and down in the large oil chamber and the small oil chamber. The small oil chamber is provided with a supercharger oil chamber small chamber interface X1B, and the large oil chamber is provided with a supercharger oil chamber large chamber interface X1A. The large cavity reversing module 1 at least includes a first electromagnetic reversing valve 101 and a first cartridge valve 103, and the first electromagnetic reversing valve 101 and the first cartridge valve 103 are connected through a first control cover plate 102; the first cartridge valve 103 has a control oil port A2 and two oil ports A1 and A3; The small chamber reversing module 2 at least includes a second electromagnetic reversing valve 201 and a second cartridge valve 203, and the second electromagnetic reversing valve 201 and the second cartridge valve 203 are connected through a second control cover plate 202; the second cartridge valve 203 has a control oil port B2 and three oil ports B1, B3, and B4; The large chamber pressure relief module 4 at least includes a third electromagnetic reversing valve 403 and a third cartridge valve 401, and the third electromagnetic reversing valve 403 and the third cartridge valve 401 are connected through a third control cover plate 402; the third cartridge valve 401 has a control oil port C2 and two oil ports C1 and C3; The small cavity pressure relief module 5 at least includes a fourth electromagnetic reversing valve 503 and a fourth cartridge valve 501, which are connected via a fourth control cover plate 502; the fourth cartridge valve 501 has a control oil port D2 and three oil ports D1, D3, and D4; The large cavity interface X1A of the supercharger oil chamber is connected to the third electromagnetic reversing valve 403, the C1 port of the third cartridge valve 401, and the A3 port of the first cartridge valve 103 in sequence; the small cavity interface X1B of the supercharger oil chamber is connected to the relief valve 6, the fourth electromagnetic reversing valve 503, the D1 port of the fourth cartridge valve 503, and the B3 port of the second cartridge valve 203 in sequence; the pressure oil port P is connected to the first electromagnetic reversing valve 101, the A1 port of the first cartridge valve 103, the second electromagnetic reversing valve 201, and the B1 and B4 ports of the second cartridge valve 203 in sequence; the return oil Port T is connected to the first solenoid reversing valve 101, the second solenoid reversing valve 201, the third solenoid reversing valve 403, the fourth solenoid reversing valve 503, the C3 port of the third cartridge valve 401, and the D3 and D4 ports of the fourth cartridge valve 501 in sequence; the A2 port of the first cartridge valve 103 is connected to the first solenoid reversing valve 101; the B2 port of the second cartridge valve 203 is connected to the second solenoid reversing valve 201; the C2 port of the third cartridge valve 401 is connected to the third solenoid reversing valve 403; and the D2 port on the fourth cartridge valve 501 is connected to the fourth solenoid reversing valve 503.
[0023] In specific application, when the first solenoid reversing valve 101 is de-energized, the high-pressure oil flows to the A1 and A2 ports of the first cartridge valve 103, and the A1 and A3 ports are not connected. When the first solenoid reversing valve 101 is energized, the A1 and A3 ports of the first cartridge valve 103 are connected.
[0024] When the second solenoid reversing valve 201 is powered off, the high pressure oil flows to the B1, B2 and B4 ports of the second cartridge valve 203, and the B1 and B3 ports are not connected. When the second solenoid reversing valve 201 is powered on, the B1 and B3 ports of the second cartridge valve 203 are connected.
[0025] When the third solenoid reversing valve 403 is powered off, the high pressure oil flows to the C1 and C2 ports of the third cartridge valve 401, and the C1 and C3 ports are not connected. When the third solenoid reversing valve 403 is powered on, the C1 and C3 ports of the third cartridge valve 401 are connected.
[0026] When the fourth solenoid reversing valve 503 is powered off, the high pressure oil flows to the D1 and D2 ports of the fourth cartridge valve 501, and the D1, D3, and D4 ports are not connected. When the fourth solenoid reversing valve 503 is powered on, the D1, D3, and D4 ports of the fourth cartridge valve 501 are connected.
[0027] In some embodiments, a pressure sensor 3 is further included; the pressure sensor 3 is connected to the external transmission pipeline of the large cavity interface X1A of the supercharger oil chamber; the large cavity interface X1A of the supercharger oil chamber is sequentially connected to the pressure sensor 3, the third electromagnetic reversing valve 401, the C1 port of the third cartridge valve 401, and the A3 port of the first cartridge valve 103. The pressure sensor 3 can be used to obtain pressure data in real time to understand the operating status.
[0028] In some embodiments, a pressure measuring joint 7 is further included; the pressure measuring joint 7 is respectively connected to the large cavity interface X1A of the supercharger oil cavity, the small cavity interface X1B of the supercharger oil cavity, the large cavity reversing module 1, the small cavity reversing module 2, the large cavity pressure relief module 4, the small cavity pressure relief module 5 and the relief valve 6. The arrangement of the pressure measuring joint 7 facilitates the implementation of the detection.
[0029] In actual use, the pressure channel of the A2 port of the first solenoid reversing valve 101 and the first cartridge valve 103 is placed in the first control cover plate 102; the pressure channel of the B2 port of the second solenoid reversing valve 201 and the second cartridge valve 203 is placed in the second control cover plate 202; the pressure channel of the C2 port of the third solenoid reversing valve 401 and the third cartridge valve 401 is placed in the third control cover plate 402; the pressure channel of the D2 port of the fourth solenoid reversing valve 503 and the fourth cartridge valve 501 is placed in the fourth control cover plate 502.
[0030] In some embodiments, the booster 8 is composed of a single hydraulic cylinder and a plunger sleeve; there are two interfaces on one side of the hydraulic cylinder, namely the large cavity interface X1A of the booster oil chamber and the small cavity interface X1B of the booster oil chamber, and there is a high-pressure water interface X2 on one side of the plunger sleeve.
[0031] In some embodiments, a displacement sensor 801 is installed on the side of the hydraulic cylinder. The displacement sensor 801 can accurately grasp the operating state of the hydraulic cylinder.
[0032] The technical solution of the present invention can realize rapid conversion and rapid pressurization of the water pressure test pressure from a low pressure water pressure of 3-20MPa to a high pressure water pressure of 20-200MPa.
[0033] The 20-200MPa high pressure water pressure control process is as follows: Liquid enters the small oil chamber of the supercharger 8, and its piston moves upward, and low-pressure water enters the plunger sleeve cavity from the large oil chamber interface X1A of the supercharger; Liquid enters the large oil chamber of the supercharger 8, and its piston moves downward. Since the piston area is several times the area of the piston rod end, the low-pressure water in the plunger sleeve cavity is compressed, and the water pressure working pressure is several times the oil pressure in the large oil chamber of the supercharger. Finally, the compressed high-pressure water flows out from the high-pressure water interface X2.
[0034] The specific control method of 20-200MPa high pressure water pressure is as follows: The small oil chamber of the supercharger 8 flows into the liquid, the second solenoid reversing valve 201 and the third solenoid reversing valve 401 are energized, the first solenoid reversing valve 101 and the fourth solenoid reversing valve 503 are de-energized, the high-pressure oil flows into the small oil chamber of the supercharger 8 from the second cartridge valve 203, the oil in the large oil chamber of the supercharger 8 flows into the oil return port T through the C3 port of the third cartridge valve 401, and the piston of the supercharger 8 moves upward; Liquid enters the large oil chamber of the supercharger 8, the second solenoid reversing valve 201 and the third solenoid reversing valve 401 lose power, the first solenoid reversing valve 101 and the fourth solenoid reversing valve 503 gain power, the high-pressure oil enters the large oil chamber of the supercharger 8 from the A3 port of the first cartridge valve 103, the oil in the small oil chamber of the supercharger 8 enters the oil return port T through the D4 port of the fourth cartridge valve 501, the piston of the supercharger 8 moves downward, and the high-pressure water pressure boosting is completed; The control process of low-pressure water pressure (≤20MPa) hydraulic pressure is as follows: Liquid enters the small oil chamber of the supercharger 8, the piston moves upward, and low-pressure water enters the plunger sleeve cavity from the high-pressure water interface X2; Liquid is simultaneously introduced into the large and small oil chambers of the supercharger 8, and the piston moves downward rapidly. Since the pressure increase ratio between the oil chamber and the water chamber is 1:1 at this time, that is, the system working oil pressure is equal to the working water pressure, the target water pressure of ≤20MPa can be achieved.
[0035] The specific control method of low-pressure water pressure (≤20MPa) hydraulic pressure is as follows: The small oil chamber of the supercharger 8 flows into the liquid, the second solenoid reversing valve 201 and the third solenoid reversing valve 401 are energized, the first solenoid reversing valve 101 and the fourth solenoid reversing valve 503 are de-energized, the high-pressure oil flows into the small oil chamber of the supercharger 8 from the second cartridge valve 203, the oil in the large oil chamber of the supercharger 8 flows into the oil return port T through the C3 port of the third cartridge valve 401, and the piston of the supercharger 8 moves upward; The large and small oil chambers of the supercharger 8 are filled with liquid at the same time, the third solenoid reversing valve 401 and the fourth solenoid reversing valve 503 lose power, the first solenoid reversing valve 101 and the second solenoid reversing valve 201 are energized, and the high-pressure oil enters the large oil chamber of the supercharger 8 from the A3 port of the first cartridge valve 103, and enters the small oil chamber of the supercharger 8 from the B3 port of the second cartridge valve 203. Due to the difference in area between the rod chamber and the rodless chamber of the supercharger 8, the piston of the supercharger 8 moves downward, and the high-pressure oil in the small oil chamber of the supercharger 8 is squeezed, and enters the large oil chamber of the supercharger 8 through the second cartridge valve 203 and the first cartridge valve 103, accelerating the downward movement of the piston of the supercharger 8, and quickly achieving a 1:1 oil-water pressurization.
[0036] The present invention uses a single low-power pressure source to control the hydraulic system to achieve functions such as rapid conversion of the water pressure test pressure from a low pressure water pressure of ≤20MPa to a high pressure water pressure of 20-200MPa, rapid pressurization, etc. The present invention has a simple structure, a flexible pressure control method, and saves energy consumption.
[0037] In the absence of conflicts, technicians in this field can combine the relevant technical features in the above examples according to actual conditions to achieve corresponding technical effects. The specific combinations are not described here one by one.
[0038] It should be noted that all directional indications (such as up, down, left, right, front, back, etc.) in the embodiments of the present invention are only used to explain the relative position relationship, movement status, etc. between the components under a certain specific posture (as shown in the accompanying drawings). If the specific posture changes, the directional indication will also change accordingly.
[0039] In addition, the descriptions of "first", "second", etc. in the present invention are only for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" or "second" may explicitly or implicitly include at least one of the features.
[0040] The above are only preferred embodiments of the present invention. The present invention will not be limited to the embodiments shown herein, but should conform to the widest scope consistent with the principles and novel features disclosed herein. Any simple modification, equivalent changes and modifications made to the above embodiments according to the technical essence of the present invention still fall within the scope of the technical solution of the present invention.
Claims
1. A hydraulic pressure booster hydraulic control system, characterized in that: It comprises a large cavity reversing module (1), a small cavity reversing module (2), a large cavity pressure relief module (4), a small cavity pressure relief module (5), a relief valve (6), a booster (8), a pressure oil port (P) and an oil return port (T); The supercharger (8) is provided with at least a large oil chamber, a small oil chamber, a high-pressure water interface (X2), and a piston connected to the large oil chamber and the small oil chamber and movable up and down in the large oil chamber and the small oil chamber, the small oil chamber being provided with a supercharger small oil chamber interface (X1B), and the large oil chamber being provided with a supercharger large oil chamber interface (X1A); The large-cavity reversing module (1) comprises at least a first electromagnetic reversing valve (101) and a first cartridge valve (103), wherein the first electromagnetic reversing valve (101) and the first cartridge valve (103) are connected via a first control cover plate (102); the first cartridge valve (103) is provided with a control oil port A2 and two oil ports A1 and A3; The small cavity reversing module (2) comprises at least a second electromagnetic reversing valve (201) and a second cartridge valve (203), wherein the second electromagnetic reversing valve (201) and the second cartridge valve (203) are connected via a second control cover plate (202); the second cartridge valve (203) is provided with a control oil port B2 and three oil ports B1, B3, B4; The large chamber pressure relief module (4) comprises at least a third electromagnetic reversing valve (403) and a third cartridge valve (401), wherein the third electromagnetic reversing valve (403) and the third cartridge valve (401) are connected via a third control cover plate (402); the third cartridge valve (401) is provided with a control oil port C2 and two oil ports C1 and C3; The small cavity pressure relief module (5) comprises at least a fourth electromagnetic reversing valve (503) and a fourth cartridge valve (501), wherein the fourth electromagnetic reversing valve (503) and the fourth cartridge valve (501) are connected via a fourth control cover plate (502); the fourth cartridge valve (501) is provided with a control oil port D2 and three oil ports D1, D3, and D4; The large cavity interface (X1A) of the supercharger oil chamber is connected in sequence to the third electromagnetic reversing valve (403), the C1 port of the third cartridge valve (401), and the A3 port of the first cartridge valve (103); the small cavity interface (X1B) of the supercharger oil chamber is connected in sequence to the overflow valve (6), the fourth electromagnetic reversing valve (503), the D1 port of the fourth cartridge valve (503), and the B3 port of the second cartridge valve (203); the pressure oil port (P) is connected in sequence to the first electromagnetic reversing valve (101), the A1 port of the first cartridge valve (103), the second electromagnetic reversing valve (201), and the B1 and B4 ports of the second cartridge valve (203); the oil return port (T) is connected in sequence to the first electromagnetic reversing valve (101), the second electromagnetic reversing valve (201), the third electromagnetic reversing valve (403), the fourth electromagnetic reversing valve (503), the C3 port of the third cartridge valve (401), and the D3 and D4 ports of the fourth cartridge valve (501); the A2 port of the first cartridge valve (103) is connected to the first electromagnetic reversing valve (101); the B2 port of the second cartridge valve (203) is connected to the second electromagnetic reversing valve (201); the C2 port of the third cartridge valve (401) is connected to the third electromagnetic reversing valve (403); and the D2 port on the fourth cartridge valve (501) is connected to the fourth electromagnetic reversing valve (503).
2. A hydraulic pressure booster hydraulic control system according to claim 1, characterized in that: It also includes a pressure sensor (3); the pressure sensor (3) is connected to an external transmission pipeline of a large cavity interface (X1A) of the supercharger oil cavity; the large cavity interface (X1A) of the supercharger oil cavity is sequentially connected to a third electromagnetic reversing valve (403), a C1 port of a third cartridge valve (401), and an A3 port of a first cartridge valve (103) via the pressure sensor (3).
3. A hydraulic pressure booster hydraulic control system according to claim 1 or 2, characterized in that: It also includes a pressure measuring joint (7); the pressure measuring joint (7) is respectively connected to the large cavity interface (X1A) of the supercharger oil cavity, the small cavity interface (X1B) of the supercharger oil cavity, the large cavity reversing module (1), the small cavity reversing module (2), the large cavity pressure relief module (4), the small cavity pressure relief module (5) and the overflow valve (6).
4. A hydraulic pressure booster hydraulic control system according to claim 1, characterized in that: The pressure channel at the A2 port of the first electromagnetic reversing valve (101) and the first cartridge valve (103) is disposed in the first control cover plate (102); the pressure channel at the B2 port of the second electromagnetic reversing valve (201) and the second cartridge valve (203) is disposed in the second control cover plate (202); the pressure channel at the C2 port of the third electromagnetic reversing valve (403) and the third cartridge valve (401) is disposed in the third control cover plate (402); and the pressure channel at the D2 port of the fourth electromagnetic reversing valve (503) and the fourth cartridge valve (503) is disposed in the fourth control cover plate (502).
5. A hydraulic pressure booster hydraulic control system according to claim 1, characterized in that: The booster (8) is composed of a single hydraulic cylinder and a plunger sleeve. One side of the hydraulic cylinder has two interfaces, namely a large-chamber interface (X1A) of the booster oil chamber and a small-chamber interface (X1B) of the booster oil chamber. One side of the plunger sleeve has a high-pressure water interface (X2).
6. A hydraulic pressure booster hydraulic control system according to claim 5, characterized in that: A displacement sensor (801) is installed on the side of the hydraulic cylinder.
7. A high-pressure water pressure hydraulic control method, characterized in that: The hydraulic control system of the water pressure booster according to any one of claims 1 to 3 comprises the following steps: Step 1: Implement hydraulic control of high-pressure water pressure and proceed to step 2; implement hydraulic control of low-pressure water pressure and proceed to step 3; Step 2: Liquid enters the small oil chamber of the supercharger (8), the second solenoid reversing valve (201) and the third solenoid reversing valve (403) are energized, the first solenoid reversing valve (101) and the fourth solenoid reversing valve (503) are de-energized, the high-pressure oil enters the small oil chamber of the supercharger (8) from the second cartridge valve (203), the oil in the large oil chamber of the supercharger (8) enters the oil return port (T) through the C3 port of the third cartridge valve (401), and the piston of the supercharger (8) moves upward; Liquid enters the large oil chamber of the booster (8), the second solenoid reversing valve (201) and the third solenoid reversing valve (403) lose power, the first solenoid reversing valve (101) and the fourth solenoid reversing valve (503) gain power, the high-pressure oil enters the large oil chamber of the booster (8) from the A3 port of the first cartridge valve (103), the oil in the small oil chamber of the booster (8) enters the oil return port (T) through the D4 port of the fourth cartridge valve (503), the piston of the booster (8) moves downward, and the high-pressure water pressure boosting is completed; Step 3: Liquid enters the small oil chamber of the supercharger (8), the second solenoid reversing valve (201) and the third solenoid reversing valve (403) are energized, the first solenoid reversing valve (101) and the fourth solenoid reversing valve (503) are de-energized, the high-pressure oil enters the small oil chamber of the supercharger (8) from the second cartridge valve (203), the oil in the large oil chamber of the supercharger (8) enters the oil return port (T) through the C3 port of the third cartridge valve (401), and the piston of the supercharger (8) moves upward; Liquid is simultaneously introduced into the large and small oil chambers of the supercharger (8), the third solenoid reversing valve (403) and the fourth solenoid reversing valve (503) lose power, the first solenoid reversing valve (101) and the second solenoid reversing valve (201) gain power, and the high-pressure oil enters the large oil chamber of the supercharger (8) from the A3 port of the first cartridge valve (103) and enters the small oil chamber of the supercharger (8) from the B3 port of the second cartridge valve (203). Due to the difference in area between the rod chamber and the rodless chamber of the supercharger (8), the piston of the supercharger (8) moves downward, and the high-pressure oil in the small oil chamber of the supercharger (8) is squeezed and enters the large oil chamber of the supercharger (8) through the second cartridge valve (203) and the first cartridge valve (103), thereby accelerating the downward movement of the piston of the supercharger (8) and quickly achieving a 1:1 oil-water supercharging.
8. A high-pressure water pressure hydraulic control method according to claim 7, characterized in that: The high pressure ranges from 20 to 200 MPa.
9. A high-pressure water pressure hydraulic control method according to claim 7, characterized in that: The low pressure range is ≤20MPa.