Hydraulic control water pressure proportional overflow valve

Abstract

The invention relates to a hydraulic control water pressure proportional overflow valve, which comprises a water pressure overflow valve, a hydraulic control valve core, a valve sleeve for accommodating the water pressure valve core, a hydraulic control valve core and an overflow port on the valve sleeve, the hydraulic control valve seat is arranged at the top of the water pressure overflow valve; one end of the guide and control piston acts on the water pressure valve element, the other end of the guide and control piston extends into the hydraulic control valve seat, and a closed oil pressure guide and control cavity is defined by the guide and control piston and the hydraulic control valve seat; the electro-hydraulic proportional pressure reducing valve is mounted on the hydraulic control valve seat and is used for receiving pressure oil of a constant-pressure oil source and outputting control oil pressure with a corresponding proportion according to an input electric signal; the control oil way is communicated with an output port of the electro-hydraulic proportional pressure reducing valve and the oil pressure guide and control cavity and is used for guiding the control oil pressure to the oil pressure guide and control cavity; and the oil pressure acting force in the oil pressure guide and control cavity is balanced with the hydraulic force and the reset force borne by the water pressure valve element. The extreme dependence of the water pressure proportional control valve on the part machining precision and the medium cleanliness is reduced, and the contradiction between a compact structure and high-pressure output is solved.

Description

Technical Field

[0001] This invention relates to the field of fluid control technology, and in particular to a hydraulically controlled proportional relief valve. Background Technology

[0002] Water-based hydraulic technology, due to its unique advantages such as environmental friendliness and flame retardancy, is considered an important technological development direction in the industrial field, especially in pressure vessel testing. However, compared with traditional mineral oil hydraulic technology, using water as the working medium also brings significant technical challenges. Water's low viscosity, strong corrosiveness, and high permeability directly lead to problems such as sealing difficulties, easy leakage, and extremely stringent requirements for the corrosion resistance and machining precision of component materials in water-based hydraulic components. Specifically, for pressure control components, existing water pressure proportional relief valves mostly adopt pilot-operated control structures to achieve precise pressure proportional regulation. The performance of this type of structure is highly dependent on the precisely fitted components of the pilot valve, such as the pilot valve core and valve sleeve, which require extremely high manufacturing tolerances and fitting precision. At the same time, the pilot control circuit is extremely sensitive to the cleanliness of the working medium (water); even minor contaminants can cause valve core jamming or performance failure. This makes the entire valve not only expensive to manufacture, but also complex, reliability-challenged, and difficult to maintain. Furthermore, in the existing valve design, there is a strong coupling relationship between the valve body size and the output pressure that can be achieved. In application scenarios that pursue compactness and miniaturization, it is difficult to achieve high pressure output without increasing the structural size, which limits its application potential in space-constrained environments. Summary of the Invention

[0003] Therefore, it is necessary to provide a hydraulically controlled proportional water pressure relief valve that reduces the extreme dependence of the proportional water pressure control valve on the machining accuracy of parts and the cleanliness of the medium, and resolves the contradiction between compact structure and high pressure output, in order to address the above-mentioned technical problems.

[0004] The present invention provides a hydraulically controlled proportional relief valve, comprising: A water pressure relief valve has a water pressure valve core and a valve sleeve that houses the water pressure valve core. The water pressure valve core and the overflow port on the valve sleeve form a sealing fit to control the pressure overflow of the main water circuit. A hydraulically controlled valve seat is disposed on the top of the water pressure relief valve; The pilot piston acts on the hydraulic valve core at one end and extends into the hydraulic control valve seat at the other end, forming a closed hydraulic pilot control cavity together with the hydraulic control valve seat. An electro-hydraulic proportional pressure reducing valve is installed on the hydraulic control valve seat. It is used to receive pressure oil from a constant pressure oil source and output a corresponding proportional control oil pressure according to the input electrical signal. The control oil circuit connects the output port of the electro-hydraulic proportional pressure reducing valve to the oil pressure control chamber, and is used to guide the control oil pressure to the oil pressure control chamber, thereby transmitting the pressure to the water pressure valve core through the control piston. The hydraulic force in the hydraulic control chamber is balanced with the hydraulic force and reset force on the water pressure valve core, so that the opening pressure of the water pressure relief valve is continuously and proportionally adjusted according to the change of the input electrical signal of the electro-hydraulic proportional pressure reducing valve.

[0005] In one embodiment, the end of the pilot piston that acts on the water pressure valve core is provided with a ball head structure, and the corresponding end of the water pressure valve core is provided with a ball socket, and the ball head structure and the ball socket form a spherical contact fit.

[0006] In one embodiment, a two-position two-way solenoid directional valve is provided in the control oil circuit. The inlet of the two-position two-way solenoid directional valve is connected to the output port of the electro-hydraulic proportional pressure reducing valve, and its outlet is connected to the oil pressure control chamber.

[0007] In one embodiment, the two-position two-way solenoid directional valve is a normally closed solenoid valve, which cuts off the oil passage between the output port of the electro-hydraulic proportional pressure reducing valve and the oil pressure control chamber when power is lost, and seals the oil pressure control chamber.

[0008] In one embodiment, an accumulator is connected to the oil line between the output port of the electro-hydraulic proportional pressure reducing valve and the two-position two-way solenoid directional valve.

[0009] In one embodiment, a pressure sensor is also included on the water pressure relief valve. The sensing end of the pressure sensor is connected to the main water pressure channel of the water pressure relief valve and is used to detect the output water pressure value.

[0010] In one embodiment, a compression spring is fitted on the pilot piston, and the compression spring acts between the pilot piston and the hydraulic valve seat to provide an initial preload for the hydraulic valve core.

[0011] In one embodiment, the constant pressure oil source is configured to simultaneously supply pressure oil to two or more of the electro-hydraulic proportional pressure reducing valves.

[0012] In one embodiment, the constant pressure oil source supplies oil to multiple electro-hydraulic proportional pressure reducing valves in parallel through an integrated oil distribution manifold. The oil distribution manifold has a main oil inlet and multiple independent oil outlets. Each oil outlet is connected to the oil inlet of one of the electro-hydraulic proportional pressure reducing valves via an independently adjustable flow or pressure control unit. Pressure sensors installed on each of the electro-hydraulic proportional pressure reducing valves and each water pressure relief valve are respectively connected to a central controller to form multiple independent water pressure closed-loop control loops. The central controller is configured to perform synchronous proportional control of multiple water pressure output pressures or sequential control according to preset logic.

[0013] In one embodiment, the total pressure of the constant pressure oil source, the status of each branch oil circuit, and the stability of each water pressure closed-loop control circuit are monitored in real time by a safety monitoring and fault handling module. When a pressure abnormality or loss of control is detected in a specific branch oil circuit or its associated water pressure control circuit, the central controller is triggered to execute a predetermined fault isolation procedure, including immediately instructing the two-position two-way solenoid directional valve corresponding to the faulty circuit to switch to the closed position to lock its pilot chamber pressure, and / or cutting off or releasing the pressure oil supply of the faulty branch oil circuit through the corresponding flow or pressure control unit on the oil circuit distribution manifold.

[0014] The aforementioned hydraulically controlled proportional water pressure relief valve, by setting an independent and mature hydraulic-electro-hydraulic proportional pressure reducing valve as the pressure control core, realizes pilot hydraulic control of the water pressure relief valve. This transfers the high-precision pressure proportional regulation function from the traditional hydraulic pilot circuit to the more technologically mature hydraulic control circuit, fundamentally reducing the requirements for the machining accuracy and fit tolerances of key moving parts within the water pressure relief valve, such as the water pressure valve core and valve sleeve. Simultaneously, since the high-precision pressure regulation and sensing feedback process mainly takes place in a closed hydraulic circuit, it reduces extreme dependence on the cleanliness of the water medium and improves adaptability to water quality fluctuations. Furthermore, the force transmission structure of the pilot piston achieves isolated drive of the hydraulic control force on the water pressure valve core. While maintaining the overall external dimensions of the valve body, only the force-bearing area of ​​the pilot piston or water pressure valve core needs to be adjusted to effectively regulate the output water pressure setting range, achieving good decoupling and design flexibility between structural compactness and high-pressure output capability. The system systematically solves the problems of high manufacturing cost, high reliability affected by water quality, and difficulty in achieving high pressure output in a compact space caused by the reliance on water medium pilot control in existing water pressure proportional relief valves. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0016] Figure 1 A schematic diagram of the structure of a hydraulically controlled proportional relief valve according to one embodiment; Figure 2 for Figure 1 A magnified view of part A in the middle; Figure 3 A perspective view of a hydraulically controlled proportional relief valve according to one embodiment; Figure 4 for Figure 1 Hydraulic schematic diagram of a medium-pressure proportional relief valve.

[0017] Figure label: 110. Water pressure relief valve; 111. Skeleton sealing ring; 112. Valve sleeve; 113. O-ring seal; 114. Water pressure valve core; 115. Valve sleeve seal; 116. Valve sleeve stop ring; 118. Ball head structure; 120. Hydraulic control valve seat; 122. Control oil circuit; 124. Hydraulic control chamber; 126. Compression spring; 128. Piston sealing ring; 130. Control piston; 140. Electro-hydraulic proportional pressure reducing valve; 150. Pressure sensor; 160. Accumulator; 170. Two-position two-way solenoid directional valve. Detailed Implementation

[0018] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0019] It should be noted that when a component is referred to as being "fixed to" or "set on" another component, it can be directly on the other component or there may be an intermediate component. When a component is considered to be "connected to" another component, it can be directly connected to the other component or there may be an intermediate component present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used in this specification are for illustrative purposes only and do not represent the only possible implementation.

[0020] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0021] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature and the second feature are in indirect contact through an intermediate medium. Furthermore, "above," "over," and "on top" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0022] Unless otherwise defined, all technical and scientific terms used in this specification have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used in this specification includes any and all combinations of one or more of the associated listed items.

[0023] The following is combined with Figures 1-4 The present invention describes a hydraulically controlled proportional overflow valve.

[0024] like Figures 1 to 4 As shown, in one embodiment, a hydraulically controlled proportional relief valve includes a hydraulic relief valve 110, a hydraulically controlled valve seat 120, a pilot piston 130, an electro-hydraulic proportional pressure reducing valve 140, and a control oil circuit 122.

[0025] The water pressure relief valve 110 contains a water pressure valve core 114 and a valve sleeve 112 that houses the water pressure valve core 114. The water pressure valve core 114 and the overflow port on the valve sleeve 112 form a sealing fit to control the pressure overflow of the main water circuit. Inside the water pressure relief valve 110, there is also a valve sleeve seal 115 for separating the high and low pressure sides, and an O-ring seal 113 and a skeleton seal 111 for sealing the valve sleeve stop ring 116. This multi-layer sealing system is specially designed for the low viscosity and easy leakage characteristics of water media. Structurally, it effectively isolates the medium channel between the high-pressure inlet Ph and the low-pressure relief port Th, significantly improving the valve's static sealing performance and long-term reliability in pure water media.

[0026] A hydraulic control valve seat 120 is located on top of the water pressure relief valve 110. One end of the pilot piston 130 acts on the water pressure valve core 114, and the other end extends into the hydraulic control valve seat 120, forming a closed oil pressure pilot control chamber 124 together with the hydraulic control valve seat 120. An electro-hydraulic proportional pressure reducing valve 140 is installed on the hydraulic control valve seat 120 to receive pressure oil from a constant pressure oil source and output a corresponding proportional control oil pressure according to the input electrical signal. The control oil circuit 122 connects the output port of the electro-hydraulic proportional pressure reducing valve 140 to the oil pressure pilot control chamber 124, and guides the control oil pressure to the oil pressure pilot control chamber 124, thereby transmitting the pressure to the water pressure valve core (114) through the pilot piston (130). The hydraulic pressure in the hydraulic control chamber 124 balances the hydraulic force and reset force on the water pressure valve core 114, allowing the opening pressure of the water pressure relief valve 110 to be continuously and proportionally adjusted according to the change in the input electrical signal of the electro-hydraulic proportional pressure reducing valve 140. Specifically, the water pressure relief valve 110 constitutes the main valve, with its inlet and outlet connected to the system water pressure inlet Ph and water pressure relief port Th, respectively. The pilot piston 130 passes through the skeleton sealing ring 111 and other sealing elements located above the valve sleeve 112. Its lower end directly abuts against or acts on the top of the water pressure valve core 114, while its upper end slides within the guide hole of the hydraulic control valve seat 120. The piston sealing ring 128 seals the upper cavity into an independent hydraulic control chamber 124. The electro-hydraulic proportional pressure reducing valve 140 receives constant pressure oil from an independent oil source (inlet P0, pressure relief port T0), and its output port is connected to the oil pressure pilot chamber 124 via a control oil circuit 122 machined within the hydraulic control valve seat 120. During operation, the electro-hydraulic proportional pressure reducing valve 140 outputs corresponding control oil pressure to the oil pressure pilot chamber 124 according to the input electrical signal (such as current). This oil pressure acts on the upper end face of the pilot piston 130, generating downward hydraulic pressure. This force is transmitted through the piston to the water pressure valve core 114, balancing the hydraulic force exerted on the valve core 114 by the water pressure and the spring force that resets it. When the oil pressure in the pilot chamber 124 increases, the system water pressure required to push the valve core 114 to open the overflow port (i.e., the overflow pressure) also increases, and vice versa. This achieves the core objective of indirectly, continuously, and proportionally regulating the water pressure system pressure using mature and precise oil pressure proportional pressure reducing technology. By transferring the high-precision pressure control function from the water pressure pilot circuit, which has extremely high requirements for machining accuracy and media cleanliness, to the technically mature oil pressure control circuit, the requirements for machining accuracy and fit tolerance of key moving parts such as the water pressure valve core 114 and valve sleeve 112 of the water pressure relief valve 110 are greatly reduced, thereby improving the reliability of the valve and reducing manufacturing costs and maintenance difficulty.

[0027] The pilot piston 130 has a ball head structure 118 at one end acting on the hydraulic valve core 114, and a ball socket at the corresponding end of the hydraulic valve core 114. The ball head structure 118 and the ball socket form a spherical contact fit. The lower end of the pilot piston 130 is machined into a ball head structure 118 (or an independent ball head structure 118 is provided to correspond to the ball socket machined at the lower end of the pilot piston 130), forming a spherical pair with the corresponding ball socket at the top of the hydraulic valve core 114. This structure enables the pilot piston 130 to have a slight self-aligning ability when transmitting axial pressure, which can compensate for slight misalignment caused by machining or assembly, effectively reduce lateral forces and the resulting friction and jamming risks, ensure that the force is transmitted smoothly and linearly along the axial direction, and further improve the sensitivity and reliability of the valve core action. After passing through the skeleton sealing ring 111, the pilot piston 130 acts directly on the hydraulic valve core 114. It is precisely fitted with the guide hole of the hydraulic control valve seat 120 and reliably isolates the upper hydraulic pilot control chamber 124 through the piston sealing ring 128. The ball head structure 118 and the ball socket spherical contact fit are located between the lower end of the pilot piston 130 and the top of the hydraulic valve core 114. This not only reduces lateral forces and friction through the spherical pair, ensuring the linearity of force transmission, but also makes the entire force transmission path (from the hydraulic pilot control chamber 124 → pilot piston 130 → ball head / ball socket contact pair → hydraulic valve core 114) compact and rigid. This allows the hydraulic control signal to be quickly and without lag converted into a force on the hydraulic valve core 114, improving the system's pressure response speed and control accuracy.

[0028] A two-position, two-way solenoid directional valve 170 is installed on the control oil circuit 122. The inlet of the two-position, two-way solenoid directional valve 170 is connected to the output port of the electro-hydraulic proportional pressure reducing valve 140, and its outlet is connected to the oil pressure pilot control chamber 124. The two-position, two-way solenoid directional valve 170 is installed on the hydraulic valve seat 120 and is connected in series in the control oil circuit 122 from the output port of the electro-hydraulic proportional pressure reducing valve 140 to the oil pressure pilot control chamber 124. This valve acts as an oil circuit switch, used to connect or disconnect the supply of pilot pressure oil according to control commands. The two-position, two-way solenoid directional valve 170 is a normally closed solenoid valve. When de-energized, it disconnects the oil circuit between the output port of the electro-hydraulic proportional pressure reducing valve 140 and the oil pressure pilot control chamber 124, and closes the oil pressure pilot control chamber 124. The two-position, two-way solenoid directional valve 170 is normally in a de-energized, closed state. When the electromagnet is energized, the valve core reverses direction, the oil circuit is opened, and the control pressure oil output from the proportional pressure reducing valve 140 enters the oil pressure control chamber 124. When the electromagnet is de-energized, the valve core resets under the action of the return spring, not only cutting off the oil supply path but also sealing the oil outlet of the oil pressure control chamber 124, making it a sealed cavity. This allows the pressure state of the control chamber 124 to be locked without continuous power supply. An accumulator 160 is connected in parallel to the oil circuit between the output port of the electro-hydraulic proportional pressure reducing valve 140 and the two-position two-way solenoid directional valve 170. The accumulator 160 is connected in parallel to the oil circuit between the output port of the proportional pressure reducing valve 140 and the inlet of the solenoid directional valve 170. During normal system operation, the accumulator 160 absorbs minute pressure fluctuations in the output pressure of the electro-hydraulic proportional pressure reducing valve 140, providing dynamic pressure stabilization and ensuring stable control pressure, thereby improving the stability of water pressure regulation. In the event of an unexpected power outage or the de-energization and closure of the solenoid directional valve 170, the pressure oil stored in the accumulator 160 replenishes the closed oil pressure control chamber 124, slowing the rate of pressure drop due to internal leakage. This provides a buffer for the system, preventing the water pressure relief valve 110 from suddenly opening due to a sudden drop in control pressure, thus preventing system depressurization and enhancing system safety. The electro-hydraulic proportional pressure reducing valve 140, the two-position two-way solenoid directional valve 170, and the accumulator 160 are all mounted on the hydraulic control valve seat 120. The solenoid directional valve 170 is located in the oil line between the output pressure port of the proportional pressure reducing valve 140 and the oil pressure control chamber 124; the accumulator 160 is located in the oil line between the output pressure port of the proportional pressure reducing valve 140 and the solenoid directional valve 170. This integrated installation and internal oil passage connection design compactly integrates all hydraulic control components into a single module, significantly reducing external connection pipelines. This not only simplifies system assembly and reduces the risk of failure due to leakage or damage to external pipelines, but also shortens the control oil circuit volume, which is beneficial for improving the dynamic response performance of pressure control. The specific position of the accumulator 160 in the oil circuit (after the proportional valve and before the solenoid valve) ensures that it can both absorb pressure pulsations at the proportional valve outlet and effectively compensate and buffer the pressure in the closed hydraulic control chamber 124 after the solenoid valve is closed.

[0029] This embodiment also includes a pressure sensor 150 installed on the water pressure relief valve 110. The sensing end of the pressure sensor 150 is connected to the main water pressure channel of the water pressure relief valve 110 to detect the output water pressure value. The pressure sensor 150 is installed on the side wall of the valve body of the water pressure relief valve 110, and its sensing end is connected to the main water pressure channel (e.g., the high-pressure chamber or inlet Ph) through a small hole processed in the valve body. The sensor detects the actual output water pressure value of the system in real time and converts it into an electrical signal. This electrical signal can be fed back to an external controller (not shown in the figure) and compared with a given target pressure signal, thereby adjusting the electrical signal input to the electro-hydraulic proportional pressure reducing valve 140 to form a closed-loop pressure control system. This enables precise feedback and real-time correction of the water pressure output, eliminating control errors caused by factors such as friction and hydraulic force changes, and significantly improving the pressure control accuracy and stability of the entire valve.

[0030] A compression spring 126 is fitted onto the pilot piston 130. The compression spring 126 acts between the pilot piston 130 and the hydraulic valve seat 120, providing an initial preload to the hydraulic valve core 114. The compression spring 126 is installed between the spring seat at the upper end of the pilot piston 130 and the corresponding mounting surface of the hydraulic valve seat 120. The downward force of the spring is always applied to the hydraulic valve core 114 through the pilot piston 130, providing it with a set initial preload. This ensures that when there is no pressure (or the pressure is extremely low) in the hydraulic pilot chamber 124, the hydraulic valve core 114 can reliably close the main overflow port under the action of the spring force, preventing leakage when the system is not in operation, and setting a minimum opening pressure threshold.

[0031] The constant pressure oil source is configured to simultaneously supply pressure oil to two or more of the electro-hydraulic proportional pressure reducing valves 140. See also... Figure 4 The schematic diagram shows that the constant-pressure hydraulic source (inlet P0) providing control oil pressure to the proportional pressure reducing valve 140 can be designed with sufficient flow and pressure stability to simultaneously drive multiple parallel hydraulically controlled proportional relief valves. Each electro-hydraulic proportional pressure reducing valve 140 receives pressurized oil from the same oil source but can be controlled by independent electrical signals. Using a common, technologically mature hydraulic control power unit, multiple hydraulic circuits can operate independently, each outputting different and precisely adjustable water pressures. This achieves resource sharing and efficient utilization, significantly reducing the complexity and cost of multi-channel independent hydraulic control systems.

[0032] A constant-pressure oil source supplies oil to multiple electro-hydraulic proportional pressure reducing valves 140 in parallel via an integrated oil distribution manifold. This manifold has a main inlet and multiple independent outlets. Each outlet is connected to the inlet of an electro-hydraulic proportional pressure reducing valve 140 via an independently adjustable flow or pressure control unit. Pressure sensors 150 installed on each electro-hydraulic proportional pressure reducing valve 140 and each water pressure relief valve 110 are respectively connected to a central controller to form multiple independent water pressure closed-loop control loops. The central controller is configured to perform synchronous proportional control of multiple water pressure outputs or sequential control according to preset logic. The integrated oil distribution manifold, as a compact structure, has independent flow channels machined internally to branch from the main inlet to each outlet, providing a stable pressure oil source for each branch. The flow or pressure control units (such as throttle valves and pressure compensation valves) on each branch can be used to finely adjust or balance the flow or pressure of each branch, ensuring the stability of the inlet conditions of each downstream electro-hydraulic proportional pressure reducing valve 140 and avoiding mutual interference. The central controller receives feedback signals from all pressure sensors 150 and issues independent control commands to each electro-hydraulic proportional pressure reducing valve 140. This allows multiple hydraulic relief valve units to operate independently, rather than being isolated, and to be integrated into a single intelligent pressure control system. The controller is programmable to perform advanced control functions such as synchronously increasing or decreasing all output pressures (synchronous proportional control) or sequentially reaching different set pressures at different times according to process requirements (sequential control), greatly improving the automation level, control flexibility, and overall performance of the multi-channel hydraulic system.

[0033] The total pressure of the constant pressure oil source, the status of each branch oil circuit, and the stability of each water pressure closed-loop control loop are monitored in real time by a safety monitoring and fault handling module. When an abnormal pressure or loss of control is detected in a specific branch oil circuit or its associated water pressure control loop, the central controller is triggered to execute a predetermined fault isolation procedure: including immediately instructing the two-position two-way solenoid directional valve 170 corresponding to the faulty circuit to switch to the closed position to lock the pressure in its oil pressure control chamber 124, and / or cutting off or releasing the pressure oil supply to the faulty branch oil circuit through the corresponding flow or pressure control unit on the oil circuit distribution manifold. The safety monitoring and fault handling module (which can be a software function of the central controller or an independent hardware unit) continuously monitors the key parameters of the entire multi-valve system, such as whether the total oil source pressure is normal, whether the pressure of each branch oil circuit is within a reasonable range, and whether each water pressure closed-loop circuit stably follows the set value. Once the algorithm determines that a fault has occurred in a certain circuit (such as pressure overshoot, oscillation, uncontrolled pressure relief, etc.), the module will immediately initiate an emergency response. The central controller sends a closing command to the solenoid directional valve 170 of the faulty circuit, de-energizing it to cut off the oil circuit and seal the oil pressure control chamber 124, thereby locking the water pressure output of the faulty circuit at the current or safe state and preventing the fault from escalating. At the same time, the pressure oil supply of the faulty branch can be cut off or released by controlling the adjustable unit (such as a solenoid shut-off valve) of the corresponding branch on the integrated manifold, thus isolating the fault at its source.

[0034] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0035] The above-described embodiments are merely illustrative of several implementations of the present invention, and while the descriptions are specific and detailed, they should not be construed as limiting the scope of the invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these modifications and improvements all fall within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the appended claims.

Claims

1. A hydraulically controlled proportional relief valve, characterized in that, include: A water pressure overflow valve (110) is provided with a water pressure valve core (114) and a valve sleeve (112) for accommodating the water pressure valve core. The water pressure valve core (114) and the overflow port on the valve sleeve (112) form a sealing fit to control the pressure overflow of the main water circuit. A hydraulic valve seat (120) is disposed on top of the water pressure relief valve (110); The pilot piston (130) acts on the hydraulic valve core (114) at one end and extends into the hydraulic control valve seat (120) at the other end, forming a closed hydraulic pilot control cavity (124) together with the hydraulic control valve seat (120). An electro-hydraulic proportional pressure reducing valve (140) is installed on the hydraulic control valve seat (120) to receive pressure oil from a constant pressure oil source and output a corresponding proportional control oil pressure according to the input electrical signal. The control oil circuit (122) connects the output port of the electro-hydraulic proportional pressure reducing valve (140) to the oil pressure control chamber (124) to guide the control oil pressure to the oil pressure control chamber (124), thereby transmitting the pressure to the water pressure valve core (114) through the control piston (130). The hydraulic force in the hydraulic control chamber (124) is balanced with the hydraulic force and reset force on the water pressure valve core (114), so that the opening pressure of the water pressure relief valve (110) is continuously and proportionally adjusted according to the change of the input electrical signal of the electro-hydraulic proportional pressure reducing valve (140).

2. The hydraulically controlled proportional relief valve according to claim 1, characterized in that, The guide piston (130) is provided with a ball head structure (118) at one end of the water pressure valve core (114), and a ball socket is provided at the corresponding end of the water pressure valve core (114). The ball head structure (118) and the ball socket form a spherical contact fit.

3. The hydraulically controlled proportional relief valve according to claim 1, characterized in that, The control oil circuit is provided with a two-position two-way solenoid directional valve (170). The inlet of the two-position two-way solenoid directional valve (170) is connected to the output port of the electro-hydraulic proportional pressure reducing valve (140), and its outlet is connected to the oil pressure control chamber (124).

4. The hydraulically controlled proportional relief valve according to claim 3, characterized in that, The two-position two-way solenoid directional valve (170) is a normally closed solenoid valve. When power is lost, it cuts off the oil passage between the output port of the electro-hydraulic proportional pressure reducing valve (140) and the oil pressure control chamber (124) and closes the oil pressure control chamber (124).

5. The hydraulically controlled proportional relief valve according to claim 4, characterized in that, An accumulator (160) is connected in the oil line between the output port of the electro-hydraulic proportional pressure reducing valve (140) and the two-position two-way solenoid directional valve (170).

6. The hydraulically controlled proportional relief valve according to claim 1, characterized in that, It also includes a pressure sensor (150) installed on the water pressure overflow valve (110), the sensing end of the pressure sensor (150) being connected to the main water pressure channel of the water pressure overflow valve (110) for detecting the output water pressure value.

7. The hydraulically controlled proportional relief valve according to claim 1, characterized in that, A compression spring (126) is fitted on the control piston (130). The compression spring (126) acts between the control piston (130) and the hydraulic valve seat (120) to provide initial preload for the hydraulic valve core (114).

8. The hydraulically controlled proportional relief valve according to any one of claims 1 to 7, characterized in that, The constant pressure oil source is configured to simultaneously supply pressure oil to two or more of the electro-hydraulic proportional pressure reducing valves (140).

9. The hydraulically controlled proportional relief valve according to claim 8, characterized in that, The constant pressure oil source supplies oil to multiple electro-hydraulic proportional pressure reducing valves (140) in parallel through an integrated oil distribution manifold. The oil distribution manifold has a main oil inlet and multiple independent oil outlets. Each oil outlet is connected to the oil inlet of one of the electro-hydraulic proportional pressure reducing valves (140) via an independently adjustable flow or pressure control unit. The pressure sensors (150) installed on each of the electro-hydraulic proportional pressure reducing valves (140) and each water pressure relief valve (110) are respectively connected to a central controller to form multiple independent water pressure closed-loop control loops. The central controller is configured to perform synchronous proportional control of multiple water pressure output pressures or sequential control according to preset logic.

10. The hydraulically controlled proportional relief valve according to claim 9, characterized in that, The total pressure of the constant pressure oil source, the status of each branch oil circuit, and the stability of each water pressure closed-loop control circuit are monitored in real time by a safety monitoring and fault handling module. When a pressure abnormality or loss of control is detected in a specific branch oil circuit or its associated water pressure control circuit, the central controller is triggered to execute a predetermined fault isolation procedure, including immediately instructing the two-position two-way solenoid directional valve (170) corresponding to the fault circuit to switch to the closed position to lock the pressure of its control chamber (124), and / or cutting off or releasing the pressure oil supply of the fault branch oil circuit through the flow or pressure control unit corresponding to the oil circuit distribution manifold.

Images