Automatic control overflow control valve system and method for high-pressure hydraulic pump

Abstract

The application discloses a kind of high-pressure hydraulic pump automatic control overflow control valve system and method, the technical field of fluid pressure control, including high-pressure valve body, piston cone sleeve, hydraulic control cavity and control module;Piston cone sleeve is integrated component, it is embedded in high-pressure valve body, the front end of piston cone sleeve is sealing cone face, its rear end is driven piston;High-pressure valve body, piston cone sleeve rear portion, the upper plug between high-pressure valve body upper end is enclosed and forms the hydraulic control cavity, and high-pressure liquid is filled in hydraulic control cavity;Control module is connected with hydraulic control cavity, for real-time acquisition pressure, temperature parameter in hydraulic control cavity, and automatically adjusts control pressure in control cavity to control overflow and sealing action of valve body.The application provides a kind of long-term stable, accurate and reliable operation pressure control core equipment for the superhigh pressure high-temperature simulation experiment in the field of deep oil and gas development, fundamentally guarantees the continuity of experiment, process stability and data integrity.

Description

Technical Field

[0001] This invention belongs to the technical field of fluid pressure control, specifically relating to an automatic control overflow valve system and method for a high-pressure hydraulic pump. Background Technology

[0002] In the exploration and development of oil and gas reservoirs, accurate acquisition of key parameters such as downhole formation pressure, temperature, and fluid properties is crucial for reserve assessment, development planning, and production forecasting. With the increasing depletion of shallow conventional oil and gas resources, exploration and development targets have shifted to deep, ultra-deep (e.g., exceeding 10,000 meters), and unconventional oil and gas reservoirs. These reservoirs generally possess extreme environmental characteristics such as ultra-high pressure (reaching over 100 MPa) and high temperature (often exceeding 120°C or even reaching 200°C).

[0003] To accurately guide actual mining operations, it is essential to utilize high-temperature and high-pressure simulation testing equipment in the laboratory to replicate extreme downhole conditions and conduct performance tests on rock and fluid properties, as well as drilling tools. Maintaining precise and dynamic stability of the system pressure is a core prerequisite for ensuring the continuity of the test and the validity of the data in such tests.

[0004] However, most industrial relief valves currently on the market are primarily designed for low to medium pressure applications (typically below 40 MPa), and their materials, sealing structures, and pressure regulating mechanisms are ill-suited for long-term operation under combined ultra-high pressure and high temperature conditions. Existing solutions suffer from the following significant bottlenecks: Performance gap: Currently, there is a lack of dedicated relief valve products that can be stably applied to pressures above 100MPa and temperatures above 120°C. Problems such as easy internal leakage under high pressure and material softening and seal failure due to high temperature are prominent.

[0005] Limitations of safety valves: While safety valves can be installed in the system as an alternative, their function is essentially pressure relief protection. Once the pressure exceeds the limit, the safety valve will instantly open fully to release pressure, forcing the test to be interrupted and the data link to be broken. This not only significantly reduces test efficiency and increases costs, but also fails to meet the requirements of precision tests that require continuous, stepped loading or pressure holding.

[0006] Test risks and costs: Due to the lack of reliable ultra-high pressure and high temperature overflow control methods, the test system faces the risk of pressure runaway, and the stability, repeatability and data integrity of the test are difficult to guarantee.

[0007] Therefore, developing a specialized valve capable of precise, reliable, and adjustable overflow pressure control under ultra-high pressures above 100MPa and high temperatures above 120°C has become an urgent need to break through the technical bottlenecks of deep oil and gas experiments and ensure the safe and efficient conduct of scientific research and engineering simulation experiments.

[0008] Currently, the mainstream overflow valves on the market can be divided into spring type, pilot type and electromagnetic proportional type according to their working principle. Their design benchmarks are mostly for medium and low pressure and normal temperature working conditions in conventional industries. They all have significant defects when dealing with the above-mentioned extreme complex working conditions and cannot meet the requirements of precision, continuous and safe experiments.

[0009] I. Inherent Defects of Spring-Loaded Relief Valves Spring-loaded relief valves rely on the pre-compressed spring force to directly balance the system hydraulic pressure. They have a simple structure, but their disadvantages become prominent under ultra-high pressure and high temperature conditions. 1. Low pressure and flow limits: Achieving ultra-high pressure (such as 100MPa) requires springs with extremely high stiffness and size, resulting in bulky valve bodies, difficult adjustment, and easy to cause severe vibration and noise when opening under high pressure and high flow, as well as poor valve core stability.

[0010] 2. Severe degradation of high-temperature performance: The spring material exhibits a "thermal relaxation" effect, with its elastic modulus decreasing as temperature rises. This causes a significant drift in the set pressure as oil temperature increases, resulting in a complete loss of control accuracy. Simultaneously, the valve core and valve body may experience "thermal jamming" due to their different coefficients of thermal expansion.

[0011] 3. Poor regulation characteristics and stability: Under high pressure, the friction and hydraulic force of the valve core increase, causing its opening pressure to be significantly higher than the set value, and the closing pressure to be significantly lower (i.e., a serious pressure "drop"), resulting in large fluctuations in system pressure around the set point, which cannot meet the requirements of precision experiments.

[0012] 4. Short sealing reliability and lifespan: Ultra-high pressure requires extremely high valve seat contact stress, which exacerbates wear on the sealing surface; high temperature accelerates the aging of the sealing material, both leading to serious internal leakage. Springs are also prone to fatigue fracture under high temperature and high stress.

[0013] Relevant improvement patents and the inherent drawbacks they reflect: CN107420460A (A high-pressure pilot-operated relief valve): It replaces the large-stiffness spring with a combination of "small stiffness spring + area difference piston", which directly proves that relying solely on a large-stiffness spring to achieve high pressure has problems such as difficulty in adjustment and unreasonable structure.

[0014] CN112728029A (A high-temperature and high-pressure pilot-operated relief valve): It has a specially added temperature compensation rod, which directly acknowledges that high temperature will cause changes in spring stiffness and friction, and additional mechanical structures must be added for compensation, which increases the complexity of the system.

[0015] CN211398807U (a high-pressure relief valve): It adopts a multi-layer disc spring assembly to obtain high stiffness, but it is still essentially a "hard resistance" design concept that relies on giant elastic elements. Under ultra-high pressure, it still faces severe challenges of stress concentration and thermal compensation.

[0016] CN106195091A (A relief valve with pressure compensation): The main valve core is designed with a pressure compensation chamber to counteract the hydraulic force, aiming to solve the inherent defects of large pressure fluctuation and poor opening and closing characteristics of spring direct-acting structure under high pressure and high flow.

[0017] II. Limitations of Pilot-Operated Relief Valves Pilot-operated relief valves control the main valve through a small pilot valve, which improves performance to some extent, but still has shortcomings under extreme conditions: 1. Extremely sensitive to oil cleanliness and temperature: The throttling orifice and damping orifice in its pilot control oil circuit are extremely small. Changes in oil viscosity caused by high temperature and particle erosion and wear under ultra-high pressure can easily cause blockage or changes in characteristics of the oil circuit, leading to unstable operation or even failure of the main valve.

[0018] 2. High-temperature pressure drift still exists: The pilot valve itself is usually still a spring-type structure. The thermal relaxation of the pilot spring caused by high temperature will cause the set pressure of the entire valve to drift.

[0019] 3. Slow dynamic response: The main valve action depends on the pressure build-up and release of the pilot oil circuit, which has an inherent hydraulic delay. In simulation processes that require a fast response, this may lead to pressure overshoot and long recovery time.

[0020] 4. Multiple internal leakage paths: The complex structure and numerous mating surfaces amplify internal leakage under ultra-high pressure, and high temperatures further exacerbate sealing failure, affecting pressure holding performance.

[0021] III. Obstacles to the Application of Electromagnetic Proportional Relief Valves While electromagnetic proportional relief valves can achieve precise electronic control, their core electromechanical conversion components are difficult to adapt to extreme environments. 1. Core components are susceptible to high temperatures: The coil insulation material and permanent magnet in proportional electromagnets or torque motors will rapidly degrade or even burn out when exposed to temperatures consistently above 120°C. This is the fundamental obstacle to their application in high-temperature environments.

[0022] 2. Insufficient resistance to ultra-high pressure: Under system pressures above 100MPa, the electromagnetic force required to drive the valve core is enormous, resulting in a surge in the size and power consumption of the electromagnet, making structural design difficult and reducing reliability.

[0023] 3. Poor resistance to contamination and high cost: To achieve high precision, its fitting clearance is extremely precise, and ultra-high pressure fluids can easily cause wear and jamming. In addition, it is expensive to manufacture, has harsh requirements for the operating environment, and has high maintenance costs.

[0024] Example patent: CN116044846A (A two-stage relief valve and control method). This patent aims to solve the pressure regulation instability problem over a wide temperature range by switching the oil circuit using an electronic unit. This solution itself confirms the inherent instability of traditional electro-hydraulic proportional or pilot control when the temperature changes, thus requiring the introduction of a more complex electronic compensation mechanism, which increases the system complexity and potential failure points.

[0025] In summary, existing mainstream overflow valve technologies, due to their respective working principles and structural limitations, all possess inherent defects that are difficult to overcome when dealing with extreme operating conditions combining "ultra-high pressure" (>100MPa) and "high temperature" (>120°C). There is a severe lack in the market of a dedicated overflow control device capable of long-term stable, accurate, and reliable operation under such harsh conditions. This technological gap directly restricts the safety, efficiency, and data reliability of high-pressure simulation experiments in the field of deep and ultra-deep oil and gas resource development. Summary of the Invention

[0026] The purpose of this invention is to address the aforementioned shortcomings in the prior art by providing an automatic control relief valve system and method for high-pressure hydraulic pumps. This solves the problems of traditional spring-operated or pilot-operated relief valves, which rely on springs as the set pressure source and experience uncontrollable pressure drift due to material thermal relaxation at temperatures exceeding 120°C. Furthermore, these valves are bulky and difficult to adjust under high pressure, failing to meet the requirements for high precision and high stability.

[0027] To achieve the above objectives, the technical solution adopted by the present invention is as follows: An automatic control relief valve system for a high-pressure hydraulic pump includes a high-pressure valve body, a piston cone sleeve, a hydraulic control chamber, and a control module. The high-pressure valve body is provided with an upper plug at the top; the piston cone sleeve is an integrated component, which is embedded in the high-pressure valve body. The front end of the piston cone sleeve is a sealing cone surface for sealing, and the rear end is a driving piston that bears the driving pressure; the high-pressure valve body, the rear part of the piston cone sleeve, and the upper plug at the top of the high-pressure valve body enclose and form the hydraulic control cavity, which is filled with high-pressure liquid. The control module is connected to the hydraulic control chamber and is used to collect the pressure and temperature parameters in the hydraulic control chamber in real time, and automatically adjust the control pressure in the control chamber to control the overflow and sealing action of the valve body.

[0028] Furthermore, maintaining a seal within the high-pressure valve body requires satisfying the following force balance relationship: P_control × S1≥ P_system ×S2 In the formula, P_control is the control pressure, P_system is the control valve system pressure; S1 is the effective area of ​​the piston rear end bearing surface on the piston cone sleeve, and S2 is the equivalent area of ​​the front cone surface seal of the piston cone sleeve bearing the control valve system pressure.

[0029] Furthermore, the ratio of the effective area S1 of the piston rear end bearing surface on the piston cone sleeve to the equivalent area S2 of the piston cone sleeve front end cone sealing surface bearing the pressure of the control valve system is 10~20.

[0030] Furthermore, a piston cone sleeve sealing ring is provided in the sealing groove of the piston cone sleeve.

[0031] Furthermore, the upper plug is fastened to the high-pressure valve body by fixing bolts.

[0032] Furthermore, an upper plug sealing ring is provided in the sealing groove of the upper plug.

[0033] Furthermore, the control module includes a control pressure generation unit, which includes a high-pressure liquid pump, an injection high-pressure solenoid valve, and a discharge high-pressure solenoid valve. The outlet of the high-pressure liquid pump is connected to the hydraulic control chamber via the injection high-pressure solenoid valve; the discharge high-pressure solenoid valve is connected to the oil drain passage of the hydraulic control chamber.

[0034] Furthermore, the control module also includes a signal monitoring unit, which includes a pressure sensor for monitoring the pressure of the overflow control valve system and a temperature sensor for monitoring the temperature of the high-pressure liquid.

[0035] Furthermore, the control module also includes an automatic control monitoring unit. The signal input terminal of the automatic control monitoring unit is connected to the pressure sensor and the temperature sensor, and the control output terminal of the automatic control monitoring unit is connected to the high-pressure liquid pump, the injection high-pressure solenoid valve, and the discharge high-pressure solenoid valve.

[0036] An overflow control method for an automatic control overflow control valve system for a high-pressure hydraulic pump includes the following steps: S1. System initialization: High-pressure liquid is filled into the hydraulic control chamber. The automatic control monitoring unit sets the overflow pressure threshold and calculates the initial control pressure based on the area ratio S1 / S2. S2. The automatic control and monitoring unit controls the high-pressure liquid pump and the injection high-pressure solenoid valve to open, injecting high-pressure liquid into the hydraulic control chamber until the pressure sensor detects that the control pressure has reached the initial control pressure, and then closes the injection high-pressure solenoid valve. S3. The signal monitoring unit collects the pressure and temperature signals in the hydraulic control chamber in real time and transmits them to the automatic control monitoring unit. The automatic control monitoring unit dynamically corrects the control pressure setpoint through temperature and pressure coupling compensation. S4. When the system pressure increases, causing the piston cone sleeve to move backward and the cone surface to open for overflow, the automatic control monitoring unit controls the high-pressure liquid pump and the injection high-pressure solenoid valve to supplement high-pressure liquid according to the pressure feedback, thereby increasing the control pressure and pushing the piston cone sleeve to reset and seal. When the system pressure is too high and needs to be unloaded, the automatic control monitoring unit opens the discharge high-pressure solenoid valve to release some high-pressure liquid and reduce the control pressure, thereby achieving overflow pressure relief. S5. After completion, the automatic control and monitoring unit controls the high-pressure liquid pump to stop, opens the high-pressure discharge solenoid valve, and completely releases the high-pressure liquid in the hydraulic control chamber, completing the system unloading.

[0037] The high-pressure hydraulic pump automatic control overflow control valve system provided by this invention has the following beneficial effects: 1. This invention provides a core pressure control device that can operate stably, accurately and reliably for long-term operation in ultra-high pressure and high temperature simulation experiments in fields such as deep oil and gas development, fundamentally ensuring the continuity of experiments, process stability and data integrity.

[0038] 2. Structural Innovation: It is the first to adopt an integrated structure of large-area ratio hydraulic piston drive and metal conical surface seal. The opening and closing is achieved by the hydraulic pressure of the rear control chamber of the piston cone sleeve to drive the front cone surface. The static pressure balance principle replaces the traditional direct action of the spring, eliminating the problem of thermal relaxation and fatigue failure of the spring under ultra-high pressure and high temperature from the root.

[0039] 3. Control Innovation: It integrates an automatic control system based on multi-sensor feedback, which dynamically calculates and precisely adjusts the control oil pressure of the drive piston by monitoring the system pressure and temperature in real time, thereby realizing remote, automatic and adaptive precise control of the overflow set pressure.

[0040] 4. Performance Innovation: Through the synergy of the above-mentioned "large area ratio piston drive" and "automatic closed-loop control", the valve can achieve rapid response, stable overflow and reliable reset under extreme working conditions of 120MPa and 150°C. This effectively avoids pressure runaway and unexpected pressure loss during the test, ensures the continuity of the experiment and the integrity of the data, and fills the technical gap in high-precision pressure control equipment in this field.

[0041] 5. The use of a hydraulic piston-type force transmission structure to replace the traditional mechanical spring completely solves the risk of systemic failure caused by pressure drift (accuracy deviation can reach more than ±15%) due to spring thermal relaxation and spring fatigue fracture.

[0042] 6. Dynamic response optimization: Based on a piston design with an area ratio of 10-20, high-pressure sealing can be achieved with only 1 / 10-1 / 20 of the control pressure; combined with the automatic control system, the valve opening and closing response time is shortened to the millisecond level, the reset speed is improved, and the range of system pressure fluctuations is reduced.

[0043] 7. Adaptive Precision Control: The integrated multi-sensor fusion automatic control system can realize remote digital precision adjustment of the pressure setpoint, and through the real-time temperature-pressure coupling compensation algorithm, it can control the long-term pressure drift within a certain range under 150℃ operating conditions. Attached Figure Description

[0044] Figure 1 This is a schematic diagram of the high-pressure hydraulic pump automatic control overflow control valve system in the embodiment.

[0045] Among them, 1-1, high-pressure valve body; 1-2, piston cone sleeve; 1-3, piston cone sleeve sealing ring; 1-4, high-pressure liquid; 1-5, pressure sensor; 1-6, temperature sensor; 1-7, upper plug; 1-8, upper plug sealing ring; 1-9, fixing bolt; 1-10, drain high-pressure solenoid valve; 1-11, injection high-pressure solenoid valve; 1-12, high-pressure liquid pump; 1-13, automatic control monitoring unit. Detailed Implementation

[0046] The specific embodiments of the present invention are described below to enable those skilled in the art to understand the present invention. However, it should be understood that the present invention is not limited to the scope of the specific embodiments. For those skilled in the art, various changes are obvious as long as they are within the spirit and scope of the present invention as defined and determined by the appended claims. All inventions utilizing the concept of the present invention are protected.

[0047] This embodiment provides an automatic control relief valve system for a high-pressure hydraulic pump. It uses a large-area-ratio hydraulic piston drive instead of a spring as the direct force source and integrates closed-loop control to achieve stable, reliable, and precisely settable relief function under ultra-high pressure and high-temperature conditions. This system can adapt to high-temperature and high-pressure environments, with a maximum operating pressure of 120 MPa and a maximum operating temperature of 150°C. Figure 1 Specifically, it includes: High-pressure valve body 1-1, piston cone sleeve 1-2, hydraulic control chamber and control module; In some embodiments, the upper part of the high-pressure valve body 1-1 is provided with an upper plug 1-7, and the piston cone sleeve 1-2 is an integrated component embedded in the high-pressure valve body 1-1. The front end of the piston cone sleeve 1-2 is a sealing cone surface for sealing, and its rear end is a driving piston that bears the driving pressure. The high-pressure valve body 1-1, the rear part of the piston cone sleeve 1-2, and the upper plug 1-7 at the upper end of the high-pressure valve body 1-1 enclose a hydraulic control chamber, which is filled with high-pressure liquid 1-4. The control module is connected to the hydraulic control chamber and is used to collect the pressure and temperature parameters in the hydraulic control chamber in real time, and automatically adjust the control pressure in the control chamber to control the overflow and sealing action of the valve body.

[0048] In one specific embodiment, the piston cone sleeve 1-2 is an integral component, with its front end being a sealing cone surface for sealing and its rear end being a driving piston that bears the driving pressure. The key ingenuity of this design lies in the fact that the effective area S1 of the piston rear end pressure-bearing surface on the piston cone sleeve 1-2 is designed to be 10 to 20 times the equivalent area S2 of the front cone surface sealing part of the piston cone sleeve 1-2 bearing the pressure of the control valve system.

[0049] According to the principles of fluid statics, when the control valve system pressure (P_system) acts on the front conical surface, in order to maintain a seal, a control pressure (P_control) needs to be applied in the hydraulic control chamber at the rear of the piston, and the following force balance relationship must be satisfied: P_control × S1≥ P_system × S2 Since the area ratio S1 / S2 = 10~20, only a relatively small control pressure (P_control) is needed to balance or overcome extremely high system pressure (P_system). This static pressure amplification effect of "small pressure controlling large pressure" is the physical basis for this valve to achieve reliable control and rapid response under ultra-high pressure.

[0050] When the system pressure increases, causing the left side of the inequality to be less than the right side, the piston cone sleeve 1-2 moves backward, and the cone surface opens to overflow; when the system pressure decreases, the control pressure pushes the piston cone sleeve 1-2 to quickly reset and seal. The valve's opening pressure is directly determined by the control pressure (P_control).

[0051] In one specific embodiment, the high-pressure valve body 1-1 is made of high-strength steel, with a rated working pressure of 120MPa and a maximum withstand temperature of 150℃, providing pressure bearing and installation reference for the main structural components and internal precision components. In one specific embodiment, the piston cone sleeve 1-2 is made of high-strength steel and integrates the front sealing cone surface and the rear driving piston into one unit, which has both metal hard sealing and high thrust driving functions; the piston cone sleeve sealing ring 1-3 is provided in the sealing groove of the piston cone sleeve 1-2. The piston cone sleeve sealing ring 1-3 is made of special materials that are resistant to high temperature and high pressure, and is used to realize dynamic sealing between the piston and the valve body under high pressure difference.

[0052] In one specific embodiment, the hydraulic control chamber is filled with high-pressure liquid 1-4, which is a hydraulic control medium with high fluidity, high bulk modulus and excellent chemical and thermal stability. It has stable performance under operating conditions of -20℃ to 150℃ and 120MPa, and its pressure is precisely controlled to drive the piston cone sleeve 1-2.

[0053] In one specific embodiment, the upper plug 1-7 and the high-pressure valve body 1-1 are fastened together by fixing bolts 1-9, forming a sealed pressure-bearing chamber that accommodates the piston and the high-pressure liquid 1-4. An upper plug sealing ring 1-8, made of a high-temperature and high-pressure resistant elastic material, is installed in the sealing groove of the upper plug 1-7 to achieve a static seal at the interface under operating conditions, preventing leakage of the high-pressure liquid 1-4. The fixing bolts 1-9 reliably fix the upper plug 1-7 to the high-pressure valve body 1-1, bearing the enormous separation force generated by the internal high pressure, ensuring the structural integrity of the entire upper sealing assembly under a working pressure of 120 MPa.

[0054] In some embodiments, the control module includes a control pressure generation unit, a signal monitoring unit, and automatic control monitoring units 1-13.

[0055] In one specific embodiment, the control pressure generation unit includes a high-pressure liquid pump 1-12, an injection high-pressure solenoid valve 1-11, and a discharge high-pressure solenoid valve 1-10; the outlet of the high-pressure liquid pump 1-12 is connected to the hydraulic control chamber via the injection high-pressure solenoid valve 1-11; the discharge high-pressure solenoid valve 1-10 is connected to the oil drain passage of the hydraulic control chamber.

[0056] Among them, the high-pressure solenoid valve 1-10 is connected to the drainage passage of the control chamber as an electrically controlled switching valve. When it is necessary to actively reduce the control pressure or unload the system, it opens upon receiving a signal to discharge high-pressure liquid 1-4.

[0057] The high-pressure solenoid valve 1-11 is connected to the injection passage between the hydraulic pump and the high-pressure valve body 1-1 as an electrically controlled switching valve. When the control pressure needs to be adjusted, it receives a signal to open and injects high-pressure liquid 1-4 into the cavity of the high-pressure valve body 1-1.

[0058] High-pressure liquid pumps 1-12 serve as the power source for the entire relief control system. Their function is to pressurize the hydraulic medium and continuously or as needed supply high-pressure liquid 1-4 to the relief valve to establish and maintain the control pressure required to drive the piston. In one specific embodiment, the signal monitoring unit includes a pressure sensor 1-5 for monitoring the pressure of the overflow control valve system and a temperature sensor 1-6 for monitoring the temperature of the high-pressure liquid 1-4.

[0059] Among them, pressure sensor 1-5 collects the pressure changes of high-pressure liquid 1-4 inside high-pressure valve body 1-1. Temperature sensor 1-6 collects the temperature changes of high-pressure liquid 1-4 inside high-pressure valve body 1-1.

[0060] In one specific embodiment, the signal input terminal of the automatic control monitoring unit 1-13 is connected to the pressure sensor 1-5 and the temperature sensor 1-6, and the control output terminal of the automatic control monitoring unit 1-13 is connected to the high-pressure liquid pump 1-12, the injection high-pressure solenoid valve 1-11, and the discharge high-pressure solenoid valve 1-10. The signal of the automatic control monitoring unit 1-13 can be a controller, such as a PLC, a microcontroller, or other control chip.

[0061] In some embodiments, an overflow control method for an automatic control overflow control valve system for a high-pressure hydraulic pump is provided, comprising the following steps: S1. System initialization: High-pressure liquid 1-4 is filled into the hydraulic control chamber. Automatic control monitoring unit 1-13 sets the overflow pressure threshold and calculates the initial control pressure based on the area ratio S1 / S2. S2. Automatic control and monitoring unit 1-13 controls the high-pressure liquid pump 1-12 and injection high-pressure solenoid valve 1-11 to open, injecting high-pressure liquid 1-4 into the hydraulic control chamber until the pressure sensor 1-5 detects that the control pressure has reached the initial control pressure, and then closes the injection high-pressure solenoid valve 1-11. S3, the signal monitoring unit collects the pressure and temperature signals in the hydraulic control chamber in real time and transmits them to the automatic control monitoring unit 1-13. The automatic control monitoring unit 1-13 dynamically corrects the control pressure setpoint through temperature and pressure coupling compensation. S4. When the system pressure increases, causing the piston cone sleeve 1-2 to move backward and the cone surface to open for overflow, the automatic control monitoring unit 1-13 controls the high-pressure liquid pump 1-12 and the injection high-pressure solenoid valve 1-11 to supplement high-pressure liquid 1-4 according to the pressure feedback, thereby increasing the control pressure and pushing the piston cone sleeve 1-2 to reset and seal. When the system pressure is too high and needs to be unloaded, the automatic control monitoring unit 1-13 opens the discharge high-pressure solenoid valve 1-10 to release part of the high-pressure liquid 1-4 to reduce the control pressure and achieve overflow pressure relief. S5. After completion, the automatic control and monitoring unit 1-13 controls the high-pressure liquid pump 1-12 to stop, opens the high-pressure discharge solenoid valve 1-10, and completely releases the high-pressure liquid 1-4 in the hydraulic control chamber, completing the system unloading.

[0062] This invention pioneered an integrated structure of "large area ratio hydraulic piston drive - metal conical seal", which completely replaces the traditional direct spring action mechanism with hydraulic static balance, fundamentally overcoming the core technical bottleneck of control inaccuracy caused by spring thermal relaxation and fatigue fracture under ultra-high pressure and high temperature.

[0063] Although specific embodiments of the invention have been described in detail with reference to the accompanying drawings, this should not be construed as limiting the scope of protection of this patent. Various modifications and variations that can be made by a person skilled in the art without inventive effort within the scope described in the claims still fall within the scope of protection of this patent.

Claims

1. A high-pressure hydraulic pump automatic control overflow control valve system, characterized in that, Includes a high-pressure valve body, piston cone sleeve, hydraulic control chamber, and control module; The high-pressure valve body is provided with an upper plug at the top; the piston cone sleeve is an integrated component, which is embedded in the high-pressure valve body. The front end of the piston cone sleeve is a sealing cone surface for sealing, and the rear end is a driving piston that bears the driving pressure; the high-pressure valve body, the rear part of the piston cone sleeve, and the upper plug at the top of the high-pressure valve body enclose and form the hydraulic control cavity, which is filled with high-pressure liquid. The control module is connected to the hydraulic control chamber and is used to collect the pressure and temperature parameters in the hydraulic control chamber in real time, and automatically adjust the control pressure in the control chamber to control the overflow and sealing action of the valve body.

2. The high-pressure hydraulic pump automatic control overflow control valve system according to claim 1, characterized in that, To maintain a seal within the high-pressure valve body, the following force balance relationship must be satisfied: P_control × S1 ≥ P_system ×S2 In the formula, P_control is the control pressure, P_system is the control valve system pressure; S1 is the effective area of ​​the piston rear end bearing surface on the piston cone sleeve, and S2 is the equivalent area of ​​the front cone surface seal of the piston cone sleeve bearing the control valve system pressure.

3. The high-pressure hydraulic pump automatic control overflow control valve system according to claim 2, characterized in that, The ratio of the effective area S1 of the piston rear end bearing surface on the piston cone sleeve to the equivalent area S2 of the front cone sealing part of the piston cone sleeve bearing the pressure of the control valve system is 10~20.

4. The high-pressure hydraulic pump automatic control overflow control valve system according to claim 1, characterized in that, The piston cone sleeve is provided with a piston cone sleeve sealing ring in the sealing groove.

5. The high-pressure hydraulic pump automatic control overflow control valve system according to claim 1, characterized in that, The upper plug is fastened to the high-pressure valve body by fixing bolts.

6. The high-pressure hydraulic pump automatic control overflow control valve system according to claim 1, characterized in that, The upper plug is provided with a sealing ring in the sealing groove.

7. The high-pressure hydraulic pump automatic control overflow control valve system according to claim 1, characterized in that, The control module includes a control pressure generation unit, which includes a high-pressure liquid pump, an injection high-pressure solenoid valve, and a discharge high-pressure solenoid valve. The outlet of the high-pressure liquid pump is connected to the hydraulic control chamber via the injection high-pressure solenoid valve; the discharge high-pressure solenoid valve is connected to the oil drain passage of the hydraulic control chamber.

8. The high-pressure hydraulic pump automatic control overflow control valve system according to claim 7, characterized in that, The control module also includes a signal monitoring unit, which includes a pressure sensor for monitoring the pressure of the overflow control valve system and a temperature sensor for monitoring the temperature of the high-pressure liquid.

9. The high-pressure hydraulic pump automatic control overflow control valve system according to claim 8, characterized in that, The control module also includes an automatic control monitoring unit. The signal input terminal of the automatic control monitoring unit is connected to the pressure sensor and the temperature sensor, and the control output terminal of the automatic control monitoring unit is connected to the high-pressure liquid pump, the injection high-pressure solenoid valve, and the discharge high-pressure solenoid valve.

10. An overflow control method for an automatic control overflow control valve system for a high-pressure hydraulic pump according to any one of claims 1 to 9, characterized in that, Includes the following steps: S1. System initialization: High-pressure liquid is filled into the hydraulic control chamber. The automatic control monitoring unit sets the overflow pressure threshold and calculates the initial control pressure based on the area ratio S1 / S2. S2. The automatic control and monitoring unit controls the high-pressure liquid pump and the injection high-pressure solenoid valve to open, injecting high-pressure liquid into the hydraulic control chamber until the pressure sensor detects that the control pressure has reached the initial control pressure, and then closes the injection high-pressure solenoid valve. S3. The signal monitoring unit collects the pressure and temperature signals in the hydraulic control chamber in real time and transmits them to the automatic control monitoring unit. The automatic control monitoring unit dynamically corrects the control pressure setpoint through temperature and pressure coupling compensation. S4. When the system pressure increases, causing the piston cone sleeve to move backward and the cone surface to open for overflow, the automatic control monitoring unit controls the high-pressure liquid pump and the injection high-pressure solenoid valve to supplement high-pressure liquid according to the pressure feedback, thereby increasing the control pressure and pushing the piston cone sleeve to reset and seal. When the system pressure is too high and needs to be unloaded, the automatic control monitoring unit opens the discharge high-pressure solenoid valve to release some high-pressure liquid and reduce the control pressure, thereby achieving overflow pressure relief. S5. After completion, the automatic control and monitoring unit controls the high-pressure liquid pump to stop, opens the high-pressure discharge solenoid valve, and completely releases the high-pressure liquid in the hydraulic control chamber, completing the system unloading.

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