A high-oil-pressure digital governor hydraulic system with an independent oil supply energy accumulator oil supply accident pressure regulating valve

Abstract

The utility model provides a kind of high oil pressure digital governor hydraulic system of oil supply accident pressure regulating valve with independent oil supply energy storage device, including first oil supply energy storage device and second oil supply energy storage device being connected with speed regulating system and accident pressure regulating valve system and oil supply for both, further including third oil supply energy storage device being connected with accident pressure regulating valve system and only oil supply for it;First check valve is arranged on the connecting pipeline between first oil supply energy storage device and second oil supply energy storage device and third oil supply energy storage device;Second check valve is arranged on the accident oil supply pipeline between third oil supply energy storage device and accident pressure regulating valve system.The utility model is by being set to the third oil supply energy storage device of independent oil supply accident pressure regulating valve system, still can guarantee the independent oil source supply of accident pressure regulating valve when speed regulating system appears pressure fluctuation or pressure loss fault, can effectively solve the problems, such as poor reliability of existing hydraulic system, oil pressure and oil supply instability, low energy efficiency, maintenance difficulty etc.

Description

Technical Field

[0001] This utility model relates to the technical field of hydraulic systems for governors of hydro-generator sets, and in particular to a high-pressure digital governor hydraulic system with an independent oil supply accumulator and an emergency pressure distribution valve. Background Technology

[0002] Hydropower, as a clean energy source, has stringent requirements for equipment energy efficiency. High-pressure hydraulic systems (16 MPa) reduce energy consumption by over 30% by decreasing pump displacement and reducing pipeline losses, while also avoiding oil-gas mixing pollution. The emergency pressure regulating valve, as the hydraulic actuator of the overspeed limiter, is a crucial mechanical device protecting the unit from runaway. However, traditional hydraulic speed control systems rely on the speed control system's accumulator for oil supply to the emergency pressure regulating valve, employing mechanical or simulated electro-hydraulic control methods. This results in problems such as lag in response and low energy efficiency, facing two main bottlenecks: firstly, insufficient oil supply reliability: loss of pressure in the speed control system cannot guarantee reliable shutdown of the emergency pressure regulating valve; secondly, deficiencies in emergency response: the lack of a rapid pressure replenishment mechanism under sudden operating conditions (such as main pump failure) can lead to speed control failure. These systemic defects severely restrict the reliability of high-pressure hydraulic systems in critical power equipment. Utility Model Content

[0003] This utility model addresses the aforementioned deficiencies in the existing technology by providing a high-pressure digital speed governor hydraulic system with an independent oil supply accumulator and an emergency oil supply pressure regulating valve, thereby solving problems such as poor system reliability, unstable oil pressure and oil supply, low energy efficiency, and difficult maintenance in the existing technology.

[0004] To solve the above-mentioned technical problems, this utility model adopts the following technical solution: A high-pressure digital speed governor hydraulic system with an independent oil supply accumulator and an emergency pressure regulating valve includes a first oil supply accumulator and a second oil supply accumulator connected to and supplying oil to both the speed regulating system and the emergency pressure regulating valve system, and a third oil supply accumulator connected to and supplying oil only to the emergency pressure regulating valve system.

[0005] Preferably, a first check valve is provided on the connecting pipeline between the first oil supply accumulator, the second oil supply accumulator, and the third oil supply accumulator.

[0006] Preferably, a second check valve is provided on the emergency oil supply pipeline between the third oil supply accumulator and the emergency pressure regulating valve system.

[0007] Preferably, the speed control system includes a large-action main hydraulic control valve, an emergency stop valve, and a large-action pilot valve, and a main oil supply valve is provided on the main oil supply pipeline between the system and the first and second oil supply accumulators.

[0008] More preferably, the speed control system further includes a small-acting solenoid valve and a locking valve connected to the main oil supply valve, and both the small-acting solenoid valve and the locking valve are connected to a relay.

[0009] Preferably, the emergency pressure regulating valve system includes an emergency pressure regulating valve pilot valve and a first two-position three-way hydraulic control valve and a second two-position three-way hydraulic control valve, which are controlled by the emergency pressure regulating valve pilot valve in a single chamber.

[0010] Preferably, the first two-position three-way hydraulic control valve and the second two-position three-way hydraulic control valve are connected to the relay via dual one-way throttle valves.

[0011] Preferably, it also includes a return oil tank that is connected to the first oil supply accumulator, the second oil supply accumulator, and the third oil supply accumulator via two sets of oil pumps, an oil filter, and a third check valve, respectively, and a first check valve is provided on the pipeline connecting the return oil tank and the third oil supply accumulator.

[0012] More preferably, it also includes a pressure display controller, an electrical contact pressure gauge, and a pressure gauge arranged in parallel, which are connected to the connection point of the return oil tank and the main oil supply pipeline through pipelines.

[0013] Preferably, the first oil supply accumulator and the second oil supply accumulator are connected to the return oil tank via pipelines through the main unloading valve, and the third oil supply accumulator is connected to the return oil tank via pipelines through the emergency unloading valve.

[0014] The present invention adopts the above technical solution and has the following technical effects compared with the prior art: The high-pressure digital speed governor hydraulic system with an independent oil supply accumulator and emergency pressure regulating valve provided by this utility model, by setting up a third oil supply accumulator to supply oil to the emergency pressure regulating valve system, can still ensure the independent oil source supply to the emergency pressure regulating valve when the speed regulating system experiences pressure fluctuations or pressure loss failures. It has the technical effect of improving the reliability of the emergency stop function and avoiding oil supply interruption. It can effectively solve the problems of poor system reliability, unstable oil pressure and oil supply, low energy efficiency, and difficult maintenance in the prior art. Attached Figure Description

[0015] Figure 1 This is a schematic diagram of the overall frame structure of a high-pressure digital speed governor hydraulic system with an independent oil supply accumulator and an emergency oil supply pressure distribution valve according to the present invention. Figure 2 This is a schematic diagram of the connection structure between the first check valve, the second check valve, and each oil supply accumulator in a high-pressure digital speed governor hydraulic system with an independent oil supply accumulator and an emergency pressure distribution valve. Detailed Implementation

[0016] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present utility model. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments.

[0017] Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this utility model.

[0018] In existing technologies, the hydraulic system of a hydro-generator governor typically adopts an integrated design, with the emergency pressure regulating valve sharing an oil accumulator with the speed regulating system. This design means that the reliability of the emergency pressure regulating valve's oil supply depends on the pressure stability of the speed regulating system. When the speed regulating system's accumulator loses pressure or experiences pressure fluctuations, the emergency pressure regulating valve may fail to perform its emergency shutdown action due to insufficient oil supply. Furthermore, traditional systems lack an independent emergency oil supply mechanism, making it difficult to respond quickly under sudden operating conditions and posing a risk of unit runaway.

[0019] To address the aforementioned issues, a hydraulic system capable of providing an independent oil supply path for the emergency pressure regulating valve needs to be designed. In traditional solutions, the emergency pressure regulating valve shares an accumulator with the speed control system, and its oil supply stability is constrained by the operating status of the main system. Physically isolating the oil supply source of the emergency pressure regulating valve from the speed control system can eliminate the impact of abnormal pressure in the main system on the safety protection function. Based on this, by adding an independent accumulator and constructing a redundant oil supply structure, the emergency pressure regulating valve can still obtain stable oil pressure when the main oil supply fails.

[0020] Therefore, as Figure 1 and Figure 2 As shown, based on the above design concept, this application proposes a high-pressure digital speed governor hydraulic system with an independent oil supply accumulator and an emergency pressure regulating valve. It includes a first oil supply accumulator 1 and a second oil supply accumulator 2 connected to the speed regulating system and the emergency pressure regulating valve system and supplying oil to both. It also includes a third oil supply accumulator 3 connected to the emergency pressure regulating valve system and supplying oil only to it.

[0021] The first and second oil supply accumulators (1 and 2) refer to a dual-accumulator structure that provides basic oil supply to the speed control system and the emergency pressure regulating valve system. Specifically, they can be implemented using high-pressure airbag-type accumulators, arranged in parallel to form redundant oil supply capacity. The third oil supply accumulator (3) is an energy storage device independent of the speed control system and connected only to the emergency pressure regulating valve system. It can be implemented using accumulators of the same specifications, with its oil supply path physically isolated from the speed control system's oil supply path. This structure enables the emergency pressure regulating valve system to simultaneously possess both a main oil supply path and an independent emergency oil supply path.

[0022] Specifically, under normal operating conditions, the first oil supply accumulator 1 and the second oil supply accumulator 2 can simultaneously supply oil to the speed control system and the emergency pressure regulating valve system through the main oil supply pipeline. When the speed control system experiences pressure fluctuations or loss of pressure, the third oil supply accumulator 3 continuously provides oil pressure to the emergency pressure regulating valve system through an independent oil supply path. Since the third oil supply accumulator 3 is only connected to the emergency pressure regulating valve system, its oil pressure status is not affected by the operation of the speed control system, thus ensuring the emergency operation requirements of the emergency pressure regulating valve are still met in the event of a speed control system failure.

[0023] Compared to existing technologies, traditional solutions share an energy storage device with the emergency pressure regulating valve and the speed control system, resulting in safety protection functions being constrained by the main system. This solution adds an independent third energy storage device 3, enabling the emergency pressure regulating valve system to have independent oil supply capabilities, maintaining emergency response capabilities even when the main oil supply path fails. Simultaneously, the redundant oil supply structure reduces the impact of a single energy storage device failure on the overall system.

[0024] Through the above technical solution, this application achieves physical isolation of the oil supply path of the emergency pressure regulating valve, avoiding the failure of safety protection functions due to abnormal pressure in the speed regulation system. The setting of the independent third energy storage device 3 ensures that the emergency pressure regulating valve can still obtain stable oil pressure when the speed regulation system is completely depressurized, ensuring the reliable execution of emergency shutdown actions, thereby improving the safety of the hydro-generator unit operation.

[0025] In some of these embodiments, such as Figure 1 and Figure 2 As shown, this application further proposes to install a first check valve 6 on the connecting pipeline between the first oil supply accumulator 1, the second oil supply accumulator 2, and the third oil supply accumulator 3. The connecting pipeline refers to the hydraulic passage connecting the first oil supply accumulator 1, the second oil supply accumulator 2, and the third oil supply accumulator 3, used to establish the oil transmission path and withstand system pressure. The first check valve 6 is a mechanical check device that only allows oil to flow from the main oil supply accumulator side to the third oil supply accumulator 3. It adopts a tubular check valve, but prohibits oil from flowing from the third oil supply accumulator 3 side to the first oil supply accumulator 1 and the second oil supply accumulator 2 side. Unidirectional flow control is achieved through the opening and closing action of the valve core under pressure differential.

[0026] Specifically, the main oil supply accumulator, consisting of the first oil supply accumulator 1 and the second oil supply accumulator 2, is connected to the emergency pressure regulating valve accumulator, consisting of the third oil supply accumulator 3, via a pipeline. A first check valve 6 is integrated into this pipeline. When the pressure in the main oil supply accumulator is higher than that in the emergency pressure regulating valve accumulator, the first check valve 6 automatically opens, replenishing the emergency pressure regulating valve accumulator with oil. When the main oil supply accumulator loses pressure due to a fault, the first check valve 6 automatically closes under the reverse pressure differential, preventing backflow of oil into the emergency pressure regulating valve accumulator. This process achieves pressure isolation through a purely mechanical structure, requiring no external control signals or power source.

[0027] Compared to existing technologies, traditional systems do not have a pressure isolation device between the main oil supply system and the emergency oil supply system. When the main oil supply system loses pressure, the oil in the emergency pressure regulating valve accumulator may flow backward through the shared pipeline. This solution uses the first one-way valve 6 for physical isolation, maintaining normal pressure replenishment while completely cutting off the reverse flow path, ensuring the pressure integrity of the emergency pressure regulating valve accumulator.

[0028] Through the above technical solution, this application solves the problem of oil backflow between the main oil supply system and the emergency pressure regulating valve system. It achieves pressure replenishment during normal operation of the main oil supply system and maintains independent pressure reserves for the emergency oil supply system under abnormal conditions, effectively avoiding the risk of protection function failure due to pressure fluctuations or pressure loss in the main system. The mechanical structure of the first check valve 6 avoids the introduction of complex control loops, simplifying system complexity while achieving its function.

[0029] In some of these embodiments, such as Figure 1 and Figure 2 As shown, this application further proposes installing a second check valve 7 on the emergency oil supply line between the third oil supply accumulator 3 and the emergency pressure regulating valve system. The emergency oil supply line refers to a dedicated oil passage connecting the third oil supply accumulator 3 and the emergency pressure regulating valve system, used to supply hydraulic oil to the emergency pressure regulating valve in emergency situations. The second check valve 7 is a hydraulic valve that only allows oil to flow unidirectionally from the third oil supply accumulator to the emergency pressure regulating valve system. Its opening pressure setting is lower than the minimum oil supply pressure required for the emergency pressure regulating valve to operate, ensuring that forward flow resistance does not affect the emergency response speed.

[0030] Specifically, when the emergency pressure regulating valve system performs an emergency shutdown, the high-pressure oil in the third oil supply accumulator 3 flows through the emergency oil supply line and the second check valve 7 to supply oil to the pilot valve 5 of the emergency pressure regulating valve. At this time, the forward conduction characteristic of the second check valve 7 ensures that the oil flows to the actuator without obstruction. If abnormal pressure fluctuations or reverse oil flow occur on the emergency pressure regulating valve side due to load failure (such as pipeline rupture or actuator jamming), the reverse shut-off function of the second check valve 7 will immediately block the oil backflow path, preventing reverse pressure shock from being transmitted to the inside of the third oil supply accumulator 3.

[0031] The design of the second one-way valve 7 effectively prevents the abnormal pressure on the emergency pressure distribution valve system side from being transmitted back to the third oil supply accumulator 3 during emergency shutdown, avoiding internal oil pressure instability and damage to the sealing structure of the third oil supply accumulator 3, ensuring the reliability of oil supply in the third oil supply accumulator 3 during multiple consecutive emergency actions, and simplifying the system maintenance process, eliminating the need for additional pressure monitoring or active control devices to achieve fault isolation.

[0032] In some of these embodiments, such as Figure 1As shown, this application further proposes a speed control system including a large-action main hydraulic control valve 4, an emergency stop valve 8, and a large-action pilot valve 9, with a main oil supply valve 17 installed on the main oil supply pipeline between the main hydraulic control valve 4 and the first oil supply accumulator 1 and the second oil supply accumulator 2. The large-action main hydraulic control valve 4 is a dynamic response mechanism that achieves sudden load changes by regulating the high-flow oil pressure. Its function is to quickly distribute oil to the relay 12 to meet the pressure demands under large-action conditions. The emergency stop valve 8 is an independent control unit, specifically a normally closed two-position two-way valve. Its function is to directly cut off the main oil supply pipeline in case of system failure, forming a shutdown protection path without intermediate links. The large-action pilot valve 9 is a low-flow signal control mechanism, specifically a servo valve or a high-frequency response proportional valve. Its function is to reduce the main valve's action lag by precisely adjusting the valve core displacement of the main hydraulic control valve. The main oil supply valve 17 refers to the centralized oil source distribution unit, which is used to balance the oil supply pressure fluctuations of the dual energy storage devices and prevent the oil supply of the speed control system from being interrupted due to the pressure loss of a single energy storage device.

[0033] Specifically, the main oil supply valve 17 is located at the junction of the main oil supply pipeline between the dual accumulators and the speed control system, forming a pressure equalization node. When there is a pressure difference between the first oil supply accumulator 1 and the second oil supply accumulator 2, the main oil supply valve 17 automatically adjusts the mixing ratio of the two oil sources through its internal flow channel to keep the oil pressure entering the speed control system stable. After receiving the control signal from the pilot valve 9, the large-action main hydraulic control valve 4 delivers a large flow of oil to the relay in a fully open state. At this time, the emergency stop valve 8 is normally closed to maintain the oil supply path. When the emergency stop command is triggered, the electromagnet of the emergency stop valve 8 is de-energized, and the valve core cuts off the main oil supply pipeline under the action of the spring. At the same time, the oil control chamber of the large-action main hydraulic control valve 4 is quickly depressurized through the large-action pilot valve 9, realizing a dual shutdown protection mechanism.

[0034] In some of these embodiments, such as Figure 1 As shown, this application further proposes that the speed control system also includes a small-acting solenoid valve 10 and a locking valve 11 connected to the main oil supply valve 17. The small-acting solenoid valve 10 and the locking valve 11 are arranged in parallel, and both the small-acting solenoid valve 10 and the locking valve 11 are connected to the relay 12. The small-acting solenoid valve 10 is a miniature proportional valve with high-frequency opening and closing capability, specifically a two-position three-way solenoid valve with a throttle orifice structure, whose flow rate adjustment range is 5%-20% of the main oil supply valve. This valve achieves micron-level compensation of the relay 12 displacement by receiving digital control signals, solving the problem of insufficient accuracy when the main oil supply valve adjusts a large flow rate. The locking valve 11 is a shut-off valve with a mechanical locking function, specifically a two-position two-way hydraulic control valve with a spring reset mechanism, whose response time can be controlled within 50 milliseconds. This valve prevents relay drift caused by oil pressure fluctuations by cutting off the main oil supply circuit and locking the piston position.

[0035] Specifically, when the main oil supply valve 17 performs large stroke adjustment, the small-action solenoid valve 10, based on the feedback signal from the displacement sensor, performs pulse opening and closing at a frequency of over 200Hz, correcting the positioning error of the servo motor 12 by superimposing a small flow rate. When the system detects abnormal vibration or a shutdown command, the spring mechanism of the locking valve 11 automatically switches to the locked position in the de-energized state, blocking the main oil supply line while fixing the piston rod of the servo motor 12 through a mechanical slot.

[0036] In some of these embodiments, such as Figure 1 As shown, this application further proposes an emergency pressure regulating valve system including an emergency pressure regulating valve pilot valve 5 and a first two-position three-way hydraulic control valve 13 and a second two-position three-way hydraulic control valve 14, both controlled by the pilot valve in a single chamber. That is, the emergency pressure regulating valve uses a combination of two two-position three-way hydraulic control valves, controlled by the pilot valve in a single chamber, resulting in a simple structure. The two-position three-way hydraulic control valve refers to a hydraulic directional valve with two fixed working positions and three oil circuit interfaces. Its working position is switched by the valve core driven by pilot pressure oil. Single-chamber control means that the control chambers of the two hydraulic control valves are connected to the pilot valve 5 through the same oil circuit, ensuring that both valves receive the exact same control pressure signal and guaranteeing synchronous operation. The emergency pressure regulating valve pilot valve 5 acts as a pressure signal source, and its output oil circuit directly acts on the control chambers of the two hydraulic control valves, eliminating the need for additional branch flow control devices.

[0037] Specifically, this solution integrates a first check valve 6, a first two-position three-way hydraulic control valve 13, a second two-position three-way hydraulic control valve 14, and an emergency pressure regulating valve pilot valve 5 into an emergency pressure regulating valve system. This system is simple in structure, easy to maintain, and extremely reliable. When the emergency pressure regulating valve pilot valve 5 receives a shutdown signal, its output pressure oil simultaneously enters the control chambers of the first two-position three-way hydraulic control valve 13 and the second two-position three-way hydraulic control valve 14. Under pressure, the valve cores of both valves move synchronously to the working position, connecting the main oil circuit with the shut-off chamber of the servo motor 12, and simultaneously opening the return oil passage. Because the two hydraulic control valves are arranged in parallel oil circuits, a normal operation of either valve is sufficient to complete the shutdown operation, forming a redundant protection mechanism.

[0038] In some of these embodiments, such as Figure 1 As shown, this application further proposes a first two-position three-way hydraulic control valve 13 and a second two-position three-way hydraulic control valve 14 connected to a relay 12 via a double one-way throttle valve 15. The double one-way throttle valve 15 refers to a bidirectional flow control element formed by combining two parallel one-way valves with a throttle valve. During forward flow, the one-way valve is open to achieve rapid oil supply; during reverse flow, the oil is forced through the throttle orifice, creating flow resistance.

[0039] When the emergency pressure distribution valve system is activated, the first two-position three-way hydraulic control valve 13 and the second two-position three-way hydraulic control valve 14 switch the oil circuit direction under single-chamber control. The pressurized oil enters the working chamber of the servo motor 12 through the double one-way throttle valve 15. When moving in the opening direction, the forward oil flow quickly builds pressure through the one-way valve to drive the piston to move, while the return oil in the closing direction is forced to flow through the throttle valve to generate damping, effectively suppressing hydraulic shock.

[0040] In some of these embodiments, such as Figure 1 As shown, this application further proposes a return oil tank 16 connected to the first oil supply accumulator 1, the second oil supply accumulator 2, and the third oil supply accumulator 3 via two sets of oil pumps, an oil filter 22, and a third check valve 21, respectively. A first check valve 6 is installed on the pipeline connecting the return oil tank 16 and the third oil supply accumulator 3. The two sets of oil pumps refer to a main pump and a standby pump arranged in parallel. In the event of a failure of the main pump, the standby pump can automatically switch and start, ensuring that at least one set of oil pumps continuously replenishes pressurized oil to the accumulators. The oil filter 22 is a filtration device used to intercept solid particles in the oil. Specifically, it can be implemented using a metal mesh or paper filter element structure, and is installed at the oil pump outlet to prevent contaminants from entering the accumulators and hydraulic valve groups.

[0041] The third check valve 21 is a check valve that allows hydraulic fluid to flow from the oil pump to the third oil supply accumulator 3 but prevents reverse flow. It can be implemented using a cone valve structure or a ball valve core to prevent high-pressure hydraulic fluid in the accumulator from flowing back and impacting the oil pump when the machine stops. The return oil tank 16 is a container that stores hydraulic oil and facilitates oil circulation, providing a stable oil source for the oil pump and accommodating system return oil. The first check valve 6 is a check valve installed on the inlet pipe of the third oil supply accumulator 3. It can be implemented using the same structure as the third check valve 21, and is used to isolate the oil circuit of the third accumulator 3 from other accumulators to prevent pressure fluctuations or reverse backflow.

[0042] In operation, the two sets of oil pumps draw oil from the return oil tank 16. The oil is then filtered by the oil filter 22 to remove impurities before being supplied to the three accumulators via the third check valve 21. If the main pump fails, the standby pump immediately starts to maintain the oil supply pressure, preventing pressure loss in the accumulators due to the failure of a single pump. The oil filter 22 continuously filters particulate matter and contaminants from the oil, ensuring the cleanliness of the oil entering the accumulators and reducing the risk of valve jamming. The third check valve 21 prevents high-pressure oil in the accumulators from flowing back into the oil pumps when the system shuts down, protecting the pumps from impact. The first check valve 6 forms a one-way channel at the inlet of the third accumulator 3, allowing the accumulator to receive clean oil from the oil pumps while preventing oil from the third accumulator 3 from being transferred back to the main oil supply line.

[0043] In some of these embodiments, such as Figure 1As shown, this application further proposes a pressure display controller 18, an electrical contact pressure gauge 19, and a pressure gauge 20 arranged in parallel, which are connected to the connection point of the return oil tank 16 and the main oil supply line via pipelines. The pressure display controller 18 is a device capable of displaying oil pressure data in real time and performing automatic adjustment; it can be implemented using a conventionally known hydraulic controller with proportional adjustment function to maintain the system pressure within a set range. The electrical contact pressure gauge 19 is an instrument with preset high and low pressure contacts; it can be implemented using a structure combining mechanical contacts and electronic signal output, automatically triggering an alarm or protection action when the pressure exceeds a safety threshold. The pressure gauge 20 is a mechanical pointer display device; it can be implemented using a Bourdon tube pressure gauge to provide intuitive oil pressure readings during manual inspection. The connection point between the main oil supply line and the return oil tank 16 is the intersection of the main oil circuit of the hydraulic system and the return oil path of the tank; it can be implemented using a tee connector to achieve parallel connection of multiple branches, and this location reflects the overall pressure status of the system.

[0044] Specifically, the pressure display and controller 18 continuously collects the oil pressure signal at the connection point between the main oil supply line and the return oil tank through internal sensors, and transmits the data to the control system for closed-loop regulation. When the system pressure deviates from the set value, the pressure display and controller 18 automatically adjusts the hydraulic pump output or opens the unloading valve to restore pressure balance. The high and low pressure contacts of the electrical contact pressure gauge 19 are preset to the upper and lower limits allowed by the system. When the oil pressure exceeds the upper limit or falls below the lower limit, the contacts close and send an electrical signal to the protection circuit, triggering a shutdown or starting the backup oil pump. The mechanical pressure gauge is installed independently at the same connection point, and the pressure status can still be judged by manually observing the pointer position when the electronic monitoring device fails.

[0045] In some of these embodiments, such as Figure 1 As shown, this application further proposes that the first oil supply accumulator 1 and the second oil supply accumulator 2 are connected to the return oil tank 16 via pipelines through the main unloading valve 23, and the third oil supply accumulator 3 is connected to the return oil tank 16 via pipelines through the emergency unloading valve 24. The main unloading valve 23 is an actuator that controls the opening and closing of the oil circuit between the main oil supply accumulator and the return oil tank 16. Specifically, it can be implemented using a solenoid directional valve or a manual ball valve, and its function is to cut off or open the pressure relief channel of the main oil supply accumulator. The emergency unloading valve 24 is an actuator that independently controls the oil circuit between the third oil supply accumulator 3 and the return oil tank 16. Specifically, it can adopt a valve structure of the same type as the main unloading valve, and its function is to establish a dedicated pressure relief path for the emergency oil supply system. The independent setting of the main unloading valve 23 and the emergency unloading valve 24 forms physical isolation, avoiding cross-interference of oil circuits during operation.

[0046] Specifically, a main unloading valve 23 is installed in the connecting pipeline between the main oil supply accumulator and the return oil tank 16. When the speed control system requires maintenance or pressure release, only the main unloading valve 23 needs to be operated to achieve oil return from the main oil supply accumulator. A separate emergency unloading valve 24 is installed between the emergency oil supply accumulator and the return oil tank 16. During maintenance of the emergency pressure distribution valve system, the pressure relief operation of the third accumulator 3 is completed by operating the emergency unloading valve 24. The oil circuits of the two unloading valves are not interconnected. When the main system is depressurized, the oil pressure of the emergency accumulator remains stable; conversely, the main oil supply pressure is unaffected when the emergency system is operated. During maintenance, operators only need to select the corresponding unloading valve for the target system, without performing complex oil circuit switching or pressure isolation operations.

[0047] Combination Figure 1 and Figure 2 As shown, this high-pressure digital speed governor hydraulic system with an independent oil supply accumulator and emergency pressure regulating valve has the advantages of simple structure, convenient maintenance, and extremely high reliability, mainly reflected in the following aspects: First, the emergency pressure regulating valve system can reliably supply oil from the first oil supply accumulator 1, the second oil supply accumulator 2, or an independent third oil supply accumulator 3, avoiding the risks caused by pressure fluctuations or pressure loss in the first oil supply accumulator 1 and the second oil supply accumulator 2; the oil pump can simultaneously supply oil to the three accumulators, and the oil passes through the third oil supply accumulator... A first check valve 6 is installed in the forward direction. The first and second oil accumulators 1 and 2 can supply oil to the speed control system and the emergency pressure regulating valve system, respectively. However, the third oil accumulator 3, due to the isolation provided by the first check valve 6, can only supply oil to the emergency pressure regulating valve system. Therefore, whether the first and second oil accumulators 1 and 2 are functioning normally or malfunctioning, the independence of the third oil accumulator 3 is not affected. Furthermore, the third oil accumulator 3 has a large margin, fully capable of independently supplying oil to the emergency pressure regulating valve without affecting oil pressure stability. Secondly, a second check valve 7 is also installed on the outlet side of the third oil accumulator 3 to prevent backflow into the third oil accumulator 3 during shutdown if a load failure occurs, causing pressure buildup and enhancing safety and stability. Then, the emergency pressure regulating valve is a combination of two two-position three-way single-chamber hydraulic control valves. The system structure is simple, and the internal structure of the hydraulic control valve has only two positions, without switching intermediate transition positions (note: solenoid valves have switching transition positions), and the reliability is very high. Finally, since only a pipe-type check valve is installed below each oil supply accumulator, no control is required. Opening the maintenance door makes installation, disassembly, and maintenance very convenient, without adding any complexity to the system.

[0048] Finally, the following points should be noted: First, in the description of this application, it should be noted that, unless otherwise specified and limited, the terms "installation", "connection", and "linkage" should be interpreted broadly, and can be mechanical or electrical connections, or internal connections between two components, or direct connections. "Up", "down", "left", "right", etc. are only used to indicate relative positional relationships. When the absolute position of the described object changes, the relative positional relationship may change. Secondly, the accompanying drawings of the embodiments disclosed in this utility model only involve the structures involved in the embodiments disclosed in this utility model. Other structures can refer to the general design. In the absence of conflict, the same embodiment and different embodiments of this utility model can be combined with each other. Finally, the above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A high-pressure digital speed governor hydraulic system with an independent oil supply accumulator and an emergency pressure regulating valve, comprising a first oil supply accumulator (1) and a second oil supply accumulator (2) connected to and supplying oil to both a speed regulating system and an emergency pressure regulating valve system, characterized in that, It also includes a third oil supply accumulator (3) that is connected to the emergency pressure regulating valve system and supplies oil only to it.

2. The high-pressure digital speed governor hydraulic system according to claim 1, characterized in that, A first check valve (6) is provided on the connecting pipeline between the first oil supply accumulator (1), the second oil supply accumulator (2), and the third oil supply accumulator (3).

3. The high-pressure digital speed governor hydraulic system according to claim 1, characterized in that, A second check valve (7) is installed on the emergency oil supply pipeline between the third oil supply accumulator (3) and the emergency pressure regulating valve system.

4. The high-pressure digital speed governor hydraulic system according to claim 1, characterized in that, The speed control system includes a large-action main hydraulic control valve (4), an emergency stop valve (8), and a large-action pilot valve (9), and a main oil supply valve (17) is provided on the main oil supply pipeline between it and the first oil supply accumulator (1) and the second oil supply accumulator (2).

5. The high-pressure digital speed governor hydraulic system according to claim 4, characterized in that, The speed control system also includes a small-acting solenoid valve (10) and a locking valve (11) connected to the main oil supply valve (17), and both the small-acting solenoid valve (10) and the locking valve (11) are connected to the relay (12).

6. The high-pressure digital speed governor hydraulic system according to claim 1, characterized in that, The emergency pressure regulating valve system includes an emergency pressure regulating valve pilot valve (5) and a first two-position three-way hydraulic control valve (13) and a second two-position three-way hydraulic control valve (14) that are controlled by the emergency pressure regulating valve pilot valve (5) in a single chamber.

7. The high-pressure digital speed governor hydraulic system according to claim 6, characterized in that, The first two-position three-way hydraulic control valve (13) and the second two-position three-way hydraulic control valve (14) are connected to the relay (12) through a double one-way throttle valve (15).

8. The high-pressure digital speed governor hydraulic system according to claim 1, characterized in that, It also includes an oil return tank (16) that is connected to the first oil supply accumulator (1), the second oil supply accumulator (2) and the third oil supply accumulator (3) respectively via two sets of oil pumps, oil filter (22) and third check valve (21), and a first check valve (6) is provided on the pipeline connecting the oil return tank (16) and the third oil supply accumulator (3).

9. The high-pressure digital speed governor hydraulic system according to claim 8, characterized in that, It also includes a pressure display controller (18), an electrical contact pressure gauge (19), and a pressure gauge (20) arranged in parallel, which are connected to the connection point of the return oil tank (16) and the main oil supply pipeline via pipelines.

10. The high-pressure digital speed governor hydraulic system according to claim 8, characterized in that, The first oil supply accumulator (1) and the second oil supply accumulator (2) are connected to the return oil tank (16) via pipelines through the main unloading valve (23), and the third oil supply accumulator (3) is connected to the return oil tank (16) via pipelines through the emergency unloading valve (24).

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