Hydraulic apparatus and method for implementing hydraulic valve testing and vibration simulation

Abstract

The application discloses a hydraulic device and method for realizing hydraulic valve testing and vibration simulation, and mainly comprises a hydraulic device, wherein the hydraulic device comprises a hydraulic station, the hydraulic station is connected with a valve testing table pipeline, a proportional reversing valve testing module, a balance valve testing module, an overflow valve testing module, a proportional speed regulating valve testing module, a pressure reducing valve testing module and a vibration simulation control module are installed on the valve testing table and connected through the pipeline, a vibration simulation testing table is connected with the vibration simulation control module through the pipeline, an operation and monitoring upper computer is used for operating and monitoring the whole hydraulic device, and an electrical control cabinet is used for supplying power and controlling the whole hydraulic device. The hydraulic device and method for realizing hydraulic valve testing and vibration simulation can realize quick and effective parameter setting, fault diagnosis and performance testing of various hydraulic valves, can carry out precise simulation of multi-working condition vibration of any frequency spectrum, and improves the efficiency of fault diagnosis, setting maintenance and performance testing of the hydraulic system device.

Description

Technical Field

[0001] This invention relates to hydraulic devices, and more particularly to a hydraulic device and method for testing and simulating vibration of hydraulic valve components. Background Technology

[0002] The Three Gorges Dam ship lift operates 24 / 7, making its operating time and navigation efficiency extremely important. When a hydraulic system component malfunctions, the lift must be stopped for fault diagnosis and replacement, including parameter tuning and performance testing of hydraulic components. This tuning and testing must be conducted on the existing hydraulic system of the Three Gorges Dam ship lift, which is complex and requires adjusting the parameters of many related components. After tuning, the parameters of other related components must be restored, increasing the time and difficulty of tuning and impacting the lift's recovery time. Furthermore, fault diagnosis and performance testing cannot be performed on the existing hydraulic system. Some equipment experiences significantly shorter lifespans than designed due to severe vibration conditions, but the impact of vibration on these components cannot be studied and verified on the existing Three Gorges Dam ship lift mechanism. Therefore, a hydraulic device capable of testing hydraulic valves and simulating vibration is needed. This device should be able to quickly tune hydraulic system components, diagnose faults, and perform performance testing, while also simulating vibration to provide a testing platform for research on the impact of vibration on equipment. Summary of the Invention

[0003] The technical problem to be solved by the present invention is to provide a hydraulic device and method for testing and simulating vibration of hydraulic valve components, which can realize rapid setting, fault diagnosis and performance testing of hydraulic components, and simulate arbitrary vibrations, thereby improving the convenience, reliability and feasibility of hydraulic system maintenance and repair.

[0004] To solve the above-mentioned technical problems, the technical solution adopted by the present invention is as follows: A hydraulic device for testing and simulating vibration of hydraulic valves includes a hydraulic station, with pipeline connections between the hydraulic station and a valve testing bench. The valve testing bench is equipped with and connected via pipelines to a proportional directional valve testing module, a balance valve testing module, a relief valve testing module, a proportional speed control valve testing module, a pressure reducing valve testing module, and a vibration simulation control module. The vibration simulation control module is connected to the vibration simulation testing bench via pipelines. The entire hydraulic device is operated and monitored by a host computer, and powered and controlled by an electrical control cabinet.

[0005] The hydraulic station includes a hydraulic oil tank, and the oil suction port of the motor oil pump assembly is connected to the hydraulic oil tank; the oil outlet of the motor oil pump assembly is connected to the pressure control valve block; the pressure control valve block is connected to the oil pump output flow meter, the oil pump output flow meter is connected to the inlet of the high-pressure oil filter, and the outlet of the high-pressure oil filter is connected to the valve test bench through hydraulic hose five. The pressure control valve block is equipped with an electromagnetic relief valve I, a connecting ball valve, an electromagnetic relief valve II, and a hydraulic station pressure sensor; wherein, the oil outlets of electromagnetic relief valve I and electromagnetic relief valve II are connected to an overflow flow meter through pipelines, the oil outlet of the overflow flow meter is connected to an oil cooling device through pipelines, and the oil outlet of the oil cooling device is connected to a hydraulic oil tank through pipelines. One outlet of the high-pressure oil filter is connected to the transformer and vibration control valve block via a pipeline; a ball valve is installed at the oil inlet of the transformer and vibration control valve block. The oil outlet of ball valve one is connected to the oil inlet of ball valve two, the oil outlet of ball valve two is connected to high pressure filter two, the oil outlet of high pressure filter two is connected to the oil inlet of high frequency servo valve, and the oil outlet of high frequency servo valve is connected to hydraulic hose one and hydraulic hose two. The oil outlet of ball valve one is connected to the oil inlet of throttle valve one; the oil outlet of throttle valve one is connected to throttle valve two, protection relief valve, throttle valve three and accumulator; the oil outlet of throttle valve two is connected to pressure reducing valve one; pressure reducing valve one is connected to valve test bench through hydraulic hose three; the oil outlet of protection relief valve and the oil outlet of throttle valve three are connected to the return oil port of high frequency servo valve. A test bench for connecting four valve components via a hydraulic hose at the oil outlet of a ball valve. The return port of the high-frequency servo valve is connected to the inlet port of the check valve, the outlet port of the check valve is connected to the three inlet ports of the ball valve, and the inlet port of the check valve is connected to the valve test bench through the return hose; the three outlet ports of the ball valve are connected to the return flow meter, and the return flow meter is connected to the hydraulic oil tank through the pipeline; the first outlet of the high-pressure oil filter is connected to the main inlet pressure sensor, and the third outlet of the ball valve is connected to the main return pressure sensor.

[0006] The valve test bench includes a support base, and a main oil inlet pipeline and a main oil return pipeline are installed at the bottom of the support base. The main oil inlet pipeline is connected to a hydraulic hose, and the main oil return pipeline is connected to a return hose. The support base is equipped with oil supply line 1, oil supply line 2, oil supply line 3, and transformer control line in the middle. Oil supply line 1 is connected to hydraulic hose 1, oil supply line 2 is connected to hydraulic hose 4, oil supply line 3 is connected to hydraulic hose 2, and transformer control line is connected to hydraulic hose 3. The top of the support base is equipped with an instrument panel and valve mounting bracket; the instrument panel is equipped with a pressure gauge group and a pressure relay.

[0007] The proportional directional valve test module includes a proportional directional valve test block. An inlet ball valve and a return ball valve are installed on the back of the proportional directional valve test block. The inlet ball valve is connected to the inlet pipeline and the return ball valve is connected to the return pipeline. The proportional directional valve test valve block is equipped with isolation ball valve 1, isolation ball valve 2, isolation ball valve 3, pressure sensor 1, and pressure sensor 2; among them, isolation ball valve 1, isolation ball valve 2, and isolation ball valve 3 are all installed between pressure sensor 1 and pressure sensor 2. The proportional directional valve test valve is installed on the top of the valve block. The proportional directional valve, proportional directional valve sealing plate one, and proportional directional valve sealing plate two are installed. The oil inlet ball valve is connected to the oil inlet of the proportional directional valve, the oil inlet of the proportional directional valve sealing plate 1, and the oil inlet of the proportional directional valve sealing plate 2. The return ball valve is connected to the return port of the proportional directional valve, the return port of the proportional directional valve sealing plate 1, and the return port of the proportional directional valve sealing plate 2. Pressure sensor 1 and pressure sensor 2 are located at the two outlet ports of the proportional directional valve, respectively.

[0008] The balance valve test module includes a balance valve test block. The back of the balance valve test block 401 is equipped with an inlet ball valve 2 and a return ball valve 2. The inlet ball valve 2 is connected to the inlet pipeline 2, and the return ball valve 2 is connected to the return pipeline 2. The balance valve test valve block is equipped with a throttle valve, pressure sensor, and pressure sensor. The top surface of the test valve block for the balance valve is equipped with an electromagnetic directional valve, a balance valve, and a balance valve sealing plate. Oil inlet ball valve 2 is connected to the oil inlet of solenoid directional valve 1, and oil return ball valve 2 is connected to the oil return port of solenoid directional valve 1; the oil outlet of solenoid directional valve 1 is connected to throttle valve 4 and the forward oil inlet of balance valve respectively; throttle valve 4 is connected to the reverse oil inlet of balance valve; the control oil port of balance valve is connected to the transformer control pipeline; pressure sensor 3 is installed at the control oil port of balance valve; and pressure sensor 4 is installed at the reverse oil inlet of balance valve.

[0009] The overflow valve test module includes an overflow valve test block. An inlet ball valve three and a return ball valve three are installed on the back of the overflow valve test block. The inlet ball valve three is connected to the inlet pipeline three, and the return ball valve three is connected to the return pipeline three. The oil outlet of the inlet ball valve is connected to the isolation ball valves four, five, six, and seven. The oil outlet of the isolation ball valve four is connected to the relief valve one, the oil outlet of the isolation ball valve five is connected to the relief valve two, the oil outlet of the isolation ball valve six is ​​connected to the relief valve sealing plate one, the oil outlet of the isolation ball valve seven is connected to the relief valve sealing plate two, and the oil outlets of the relief valve one, relief valve two, relief valve sealing plate one, and relief valve sealing plate two are all connected to the return ball valve three.

[0010] The proportional speed control valve test module includes a proportional speed control valve test block. An inlet ball valve four and a return ball valve four are installed on the back of the proportional speed control valve test block. The inlet ball valve four is connected to the inlet pipeline four, and the return ball valve four is connected to the return pipeline four. A proportional speed control valve one is installed between the inlet ball valve four and the return ball valve four. The vibration simulation control module includes a vibration simulation control valve block. The vibration simulation control valve block is equipped with ball valve 4, oil supply line 4, oil supply line 5, and return line 6. The side of the vibration simulation control valve block is equipped with oil supply line 6, ball valve 5, ball valve 6, ball valve 7, ball valve 8, solenoid directional valve 2, oil outlet line 1, and oil outlet line 2. A proportional speed control valve 2 is installed on the top surface of the vibration simulation control valve block; Oil supply line 6 is connected to oil supply line 2 at one end, oil supply line 6 is connected to ball valve 4 at one end, oil supply line 4 is connected to oil supply line 3 at one end, oil supply line 4 is connected to ball valve 5 at one end, oil supply line 5 is connected to oil supply line 1 at one end, oil supply line 5 is connected to ball valve 6 at one end, ball valve 5 is connected to oil outlet line 2, ball valve 6 is connected to oil outlet line 1, ball valve 4 is connected to proportional speed control valve 2, proportional speed control valve 2 is connected to the oil inlet of solenoid directional valve 2, the oil outlet of solenoid directional valve 2 is connected to ball valve 7 and ball valve 8 respectively, ball valve 7 is connected to oil outlet line 1, and ball valve 8 is connected to oil outlet line 2. The vibration simulation test bench includes a support, a pressure gauge group 2 is installed in the middle of the support, a servo cylinder is installed on the top of the support, and oil supply valve block 1 and oil supply valve block 2 are installed at both ends of the servo cylinder. Oil supply valve block 1 and oil supply valve block 2 are connected and fixed by a double-headed screw assembly. A single-piston double-piston rod assembly is installed inside the servo cylinder. Displacement sensors and overflow collection pipelines are installed on the sides of oil supply valve block 1 and oil supply valve block 2. Oil supply valve block 1 is connected to oil outlet pipeline 1, and oil supply valve block 2 is connected to oil outlet pipeline 2. The single-piston double-piston rod assembly is connected to a displacement detection rod through a bracket. The displacement sensor is slidably installed with the displacement detection rod. An acceleration sensor is installed at the end of the single-piston double-piston rod assembly.

[0011] The pressure reducing valve test module includes a pressure reducing valve test block. The back of the pressure reducing valve test block is equipped with an inlet ball valve five, a return ball valve five, and a pressure relief pipeline. The inlet ball valve five is connected to the inlet pipeline five, and the return ball valve five is connected to the return pipeline five. The oil inlet ball valve 5 is connected to the oil inlet of the pressure reducing valve 2, the oil outlet of the pressure reducing valve 2 is connected to the throttle valve 5, a pressure sensor 5 is installed between the pressure reducing valve 2 and the throttle valve 5, the oil drain port of the pressure reducing valve 2 is connected to the pressure relief pipeline, and the throttle valve 5 is connected to the return ball valve 5.

[0012] A method for fault diagnosis and performance testing of a proportional directional valve includes the following steps: Step 1) Before performing fault diagnosis and performance testing of the proportional directional valve, install the proportional directional valve to be tested on the proportional directional valve test block. Seal the other mounting holes on the proportional directional valve test block with proportional directional valve sealing plate one and proportional directional valve sealing plate two. Step 2) Open inlet ball valve 1 and return ball valve 1. According to the diameter specification of the proportional directional valve being tested, select to open isolation ball valve 1, isolation ball valve 2, or isolation ball valve 3. Keep all other ball valves of the hydraulic device closed. Step 3) Start the motor oil pump assembly and oil cooling device through the operation control system and PLC controller, operate the solenoid relief valve 1 to be energized, keep the proportional directional valve opening input value at 0%, adjust the solenoid relief valve 1 to the given working pressure value X, observe the value of the return oil flow meter and the change of its flow parameter curve in the data monitoring system, which can test the zero position characteristics of the proportional directional valve and diagnose the internal leakage fault characteristics of the proportional directional valve in the zero position state. Step 4) By operating the control system and PLC controller, the proportional directional valve opening input value is -100%, and the oil pump flow rate of the motor oil pump assembly is increased from M to N. The changes in the values ​​of the main inlet oil pressure sensor, pressure sensor 2, and oil pump output flow meter are observed on the data monitoring system. The data monitoring system will display the pressure difference curve between the main inlet oil pressure sensor and pressure sensor 2 and the parameter change curve of the oil pump output flow meter. The no-load flow characteristics of the B channel of the proportional directional valve in the -100% opening state can be tested. Step 5) By operating the control system and PLC controller, the proportional directional valve opening input value is set to 100%, and the oil pump flow rate of the motor oil pump assembly is increased from M to N. The changes in the values ​​of the main inlet oil pressure sensor, pressure sensor 1, and oil pump output flow meter are observed on the data monitoring system. The data monitoring system will display the pressure difference curve between the main inlet oil pressure sensor and pressure sensor 1 and the parameter change curve of the oil pump output flow meter. The flow characteristics of the A channel of the proportional directional valve at 100% opening can be tested. Step 6) By operating the control system and PLC controller, the opening of the proportional directional valve is changed uniformly from -100% to 100%. The change in the value of the return oil flow meter is observed on the data monitoring system. This can test the linear characteristics of the flow in channels A and B of the proportional directional valve when the opening state changes. A method for diagnosing and testing the performance of a balancing valve includes the following steps: Step 1) Before performing fault diagnosis and performance testing of the balance valve, install the balance valve to be tested on the balance valve test block, and seal the other mounting holes on the balance valve test block with the balance valve sealing plate. Step 2) Open ball valve 1, inlet ball valve 2, and return ball valve 2; adjust throttle valve 1, throttle valve 2, and throttle valve 4 to the fully open position; close throttle valve 3 and all other ball valves of the hydraulic device; adjust the protection relief valve to the maximum value; and adjust the outlet pressure of pressure reducing valve 1 to the minimum value of 0. Step 3) Start the motor oil pump assembly and oil cooling device through the operation control system and PLC controller. Power on the electromagnetic overflow valve 1. First, adjust the pressure of the electromagnetic overflow valve 1 to the test value M. Power on the electromagnetic reversing valve 1 to the left working position through the operation control system and PLC controller. Observe the changes in the values ​​of the oil pump output flow meter, overflow flow meter, and return oil flow meter on the data monitoring system. If the oil pump output flow meter and overflow flow meter count values ​​are equal and the return oil flow meter count value is 0, it can be determined that the reverse pressure holding and switching performance of the tested balance valve is normal. Step 4) Gradually increase the outlet pressure value of pressure reducing valve one, and observe the changes in the values ​​of pressure sensor three and return oil flow meter on the data monitoring system. The data monitoring system displays the opening and closing characteristic curve of the tested balance valve, and the minimum opening pressure of the control port of the tested balance valve when the return oil flow meter is greater than 0 can be obtained. By changing the characteristic parameters of the control port section of the tested balance valve, the opening and closing pressure of the tested balance valve can be quickly adjusted. Step 5) Keep the outlet pressure of pressure reducing valve one at value N, and gradually adjust the oil pump displacement of the motor oil pump assembly from small to large. Observe the changes in the values ​​of pressure sensor four, main return oil pressure sensor, and oil pump output flow meter on the data monitoring system. The data monitoring system displays the reverse pressure / flow characteristic curve of the tested balance valve. Step 6) By operating the control system and PLC controller, the electromagnetic reversing valve is energized from the first to the right working position. The oil pump displacement of the motor oil pump assembly is gradually adjusted from small to large. The changes in the values ​​of the main inlet oil pressure sensor, pressure sensor four, and oil pump output flow meter are observed on the data monitoring system. The data monitoring system displays the positive pressure / flow characteristic curve of the tested balance valve. A method for diagnosing and testing the performance of an overflow valve includes the following steps: Step 1) Before performing fault diagnosis and performance testing of the relief valve, install the relief valve to be tested, namely, on the relief valve test block. Seal the other mounting holes of the relief valve test block with relief valve II, relief valve sealing plate I, and relief valve sealing plate II. Step 2) Open the inlet ball valve 3 and the return ball valve 3. According to the diameter specification of the overflow valve 1 being tested, select and open the isolation ball valve 4. Keep all other ball valves of the hydraulic device closed. Step 3) Start the motor oil pump assembly and oil cooling device through the operation control system and PLC controller, and operate the electromagnetic relief valve 1 to get energized. First, adjust the pressure value of the electromagnetic relief valve 1 to Y. Y is higher than the set value M of the relief valve 1 under test. Adjust the relief valve 1 under test from low to high. Observe the value of the main oil inlet pressure sensor and the pressure curve change on the data monitoring system. When the value of the main oil inlet pressure sensor reaches M, stop adjusting the relief valve 1 under test. At this time, the relief valve 1 under test has completed the rapid parameter setting. Step 4) Continue to increase the pump displacement of the motor oil pump assembly to the maximum design flow rate N of the overflow valve under test. Observe the values ​​and curve changes of the main inlet pressure sensor and overflow flow meter on the data monitoring system. If the value of the main inlet pressure sensor remains at the value M and the overflow flow count value is always 0, it indicates that the overflow valve under test has completed the rapid adjustment and the actual maximum flow rate of the overflow valve under test meets the factory design value. Step 5) Keep the set value M of the overflow valve under test unchanged, adjust the pump displacement of the motor oil pump assembly to the minimum value first, and then gradually increase it to the value H. Observe the value changes of the main oil inlet pressure sensor and the oil pump output flow meter on the data monitoring system. The data monitoring system displays the pressure / flow curve of the overflow valve under test at the set pressure value M. A method for fault diagnosis and performance testing of a proportional speed control valve includes the following steps: Step 1) Before performing fault diagnosis and performance testing of the proportional speed control valve, install the proportional speed control valve to be tested on the proportional speed control valve test valve block, open the inlet ball valve four and the return ball valve four, and keep all other ball valves of the hydraulic device closed. Step 2) Start the motor oil pump assembly and oil cooling device through the operation control system, energize the solenoid relief valve, adjust the pressure of the solenoid relief valve to M, adjust the oil pump displacement of the motor oil pump assembly to N, de-energize the proportional speed control valve, and observe the changes in the values ​​of the oil pump output flow meter, overflow flow meter, and return oil flow meter on the data monitoring system. If the oil pump output flow meter and overflow flow meter count values ​​are equal, and the return oil flow meter count value is 0, it can be determined that the on / off performance of the tested proportional speed control valve is normal at 0% opening. Step 3) Gradually increase the proportional speed control valve from 0% to 100%, observe the value and curve change of the return oil flow meter on the data monitoring system, and judge the linear change characteristic of the flow of the proportional speed control valve being tested. Step 4) Adjust the opening value of the proportional speed control valve to X in the operation control system, and gradually increase the pump displacement of the motor oil pump assembly. Observe the changes in the values ​​of the oil pump output flow meter and the hydraulic station pressure sensor on the data monitoring system. The data monitoring system displays the pressure / flow characteristic curve of the tested proportional speed control valve at the opening value X. Step 5) Install the proportional speed control valve 2 to be tested on the vibration simulation control valve block, open ball valve 1, ball valve 4, ball valve 7, and ball valve 8, and keep all other ball valves of the hydraulic device closed; Step 6) Start the motor oil pump assembly and oil cooling device through the operation control system, energize the electromagnetic overflow valve one, adjust the pressure of the electromagnetic overflow valve one to M, adjust the oil pump displacement of the motor oil pump assembly to N, set the proportional speed control valve two to a certain opening degree through the operation control system, energize the electromagnetic reversing valve two through the operation control system, and the servo cylinder performs extension and retraction actions according to the given control signal. The displacement sensor feeds back the motion parameters of the single piston double piston rod assembly to the electrical control cabinet through the signal cable and Ethernet. The dynamic performance of the proportional speed control valve two can be tested and judged through the oil pump output flow meter, the opening degree of the proportional speed control valve two, and the feedback data of the displacement sensor. A method for diagnosing and testing the performance of a pressure reducing valve includes the following steps: Step 1) Before performing fault diagnosis and performance testing of the pressure reducing valve, install the pressure reducing valve to be tested, the second pressure reducing valve, on the pressure reducing valve test block, open the inlet ball valve, the return ball valve, and keep all other ball valves of the hydraulic device closed. Step 2) Start the motor oil pump assembly and oil cooling device through the operation control system and PLC controller. Power on the solenoid relief valve 1, adjust the pressure of the solenoid relief valve 1 to M, adjust the oil pump displacement of the motor oil pump assembly to N, adjust the opening of the throttle valve 5, and observe the value change of the return oil flow meter on the data monitoring system. When the value of the return oil flow meter is less than XL / min, stop adjusting the throttle valve 5, adjust the pressure reducing valve 2 under test, and observe the value change of the pressure sensor 5 on the data monitoring system. When the value of the pressure sensor 5 is J, stop adjusting the pressure reducing valve 2 under test. At this time, the pressure reducing valve 2 under test has completed the rapid parameter setting. Step 3) Continue to increase the opening of throttle valve five, and observe the changes in the values ​​of the main inlet oil pressure sensor, pressure sensor five, and return oil flow meter on the data monitoring system. The data monitoring system displays the curve of the difference between the main inlet oil pressure sensor and pressure sensor five versus the change in the return oil flow meter, which is the pressure difference / flow characteristic curve of the pressure reducing valve two under test when simulating load changes at this set value state. Step 4) Adjust the opening of throttle valve five to the maximum value, and adjust the oil pump displacement of the motor oil pump assembly from small to large. Observe the value changes of the main inlet oil pressure sensor, pressure sensor five, and oil pump output flow meter on the data monitoring system. The data monitoring system displays the curve of the change of the difference between the main inlet oil pressure sensor and pressure sensor five on the oil pump output flow meter, which is the no-load pressure difference / flow characteristic curve of the pressure reducing valve two under test when the setting parameter is J. A method for simulating vibration conditions includes the following steps: Step 1) Before performing vibration condition simulation, open ball valve 1, ball valve 2, ball valve 3, ball valve 5, and ball valve 6, and keep all other ball valves and throttle valves of the hydraulic device closed; Step 2) Start the motor oil pump assembly and oil cooling device through the operation control system and PLC controller, energize the electromagnetic overflow valve, adjust the pressure of the electromagnetic overflow valve to M, and adjust the oil pump displacement of the motor oil pump assembly to N; output any given vibration waveform spectrum signal to the motion controller through the operation control system and PLC controller, and the motion controller outputs the vibration waveform spectrum signal to the high-frequency servo valve, and the high-frequency servo valve controls the servo cylinder to perform vibration simulation action; Step 3) The motion parameters of the single-piston double-piston rod assembly are fed back to the motion controller via signal cables and Ethernet by the displacement sensor and the acceleration sensor. The motion controller performs PID adjustment based on the target position of the vibration waveform spectrum signal and the feedback data from the displacement sensor and the acceleration sensor to form closed-loop control and achieve accurate simulation of the given vibration waveform spectrum signal. Step 4) The parameters of any given vibration waveform spectrum signal can be modified on the data monitoring system, and then the modified vibration waveform spectrum signal is output to the high-frequency servo valve. The high-frequency servo valve controls the servo cylinder to perform signal simulation action. At the same time, the data monitoring system displays the comparison curve between the servo cylinder vibration simulation displacement waveform spectrum fed back by the displacement sensor and the given vibration waveform spectrum signal. Step 5) When the high-frequency servo valve is replaced with the faulty valve, the data monitoring system displays a comparison curve between the simulated displacement waveform of the servo cylinder vibration fed back by the displacement sensor and the given vibration waveform spectrum signal. The control performance of the tested high-frequency servo valve can be accurately judged based on the comparison curve.

[0013] This invention provides a hydraulic device and method for testing and simulating vibration of hydraulic valve components, which has the following technical advantages: 1) By setting up a hydraulic station with a two-stage linear array installation structure of "centralized pump source and decentralized valve group", and testing modules for proportional directional valves, balance valves, relief valves, proportional speed control valves, and pressure reducing valves, rapid and efficient parameter setting, performance testing, and fault diagnosis of various hydraulic valves are achieved. Each valve testing module has an independent test circuit with good anti-interference performance. The two-stage linear array installation structure improves the testing and setting efficiency of valves and enhances the scalability of the entire hydraulic system.

[0014] 2) By setting up a hydraulic station, vibration simulation control module and vibration simulation test bench, an independent servo control loop is provided for vibration simulation, which reduces the interference of the given vibration waveform spectrum signal during vibration simulation. It can realize the simulation of arbitrary vibration waveform characteristics. At the same time, the motion controller performs PID adjustment through the displacement and acceleration feedback parameters of the servo cylinder to form closed-loop control, thereby improving the simulation accuracy of the given vibration waveform spectrum signal.

[0015] 3) By setting up a hydraulic station, the power source for the entire hydraulic device is provided centrally. The two sets of motor oil pump components serve as backups for each other, and can also be used simultaneously by changing the on / off state of the ball valve. This greatly increases the adjustment range of the system flow and pressure of the entire hydraulic device, providing a safe and controllable power source for the entire hydraulic device with multiple flow and pressure variations. It also provides the control pressure circuit required for valve testing, and the pressure of the control circuit is precisely adjustable.

[0016] 4) By setting up a hydraulic station, the system accurately distinguishes and detects the effective flow rate entering various valve testing modules, the ineffective flow rate directly overflowing back to the oil tank, and the return flow rate after passing through various valve testing modules. The system also sets up main inlet and main return pressure detection, enabling the detection and analysis of all flow and pressure used in the hydraulic device testing. This improves the detection utilization rate of flow meters and pressure sensors, reduces the modeling difficulty for the host computer when performing data detection and generating valve characteristic curves, and significantly increases the system's operating time under various loads during various valve testing and vibration simulation through the oil cooling device, thus meeting the time requirements for various valve testing and vibration simulation.

[0017] 5) Through the design of the proportional directional valve test module and hydraulic circuit, the testing of proportional directional valves of various specifications can be realized. The zero-position on / off performance test of the proportional directional valve, as well as the flow and pressure characteristics of port A and port B can be completed.

[0018] 6) Through the design of the balance valve test module and hydraulic circuit, the testing of balance valves of various specifications can be realized. It can complete the reverse on / off performance test and the forward flow and pressure characteristics test of the balance valve. By adjusting the pressure of the control oil port of the balance valve, the reverse opening and closing characteristics of the balance valve can be quickly detected, and a fast and efficient test method is provided for modifying and optimizing the reverse opening and closing characteristics of the balance valve.

[0019] 7) Through the design of the relief valve test module and hydraulic circuit, the testing of relief valves of various specifications can be realized. The parameter setting of the relief valve can be completed quickly, and the opening and closing performance test and the performance test of the positive flow and pressure characteristics of the relief valve can be completed. At the same time, through the set return oil flow meter, the pressure holding and sealing performance of the relief valve in the non-open state can be accurately detected, which can quickly assist in the fault diagnosis of hydraulic components and greatly improve the efficiency of parameter setting and fault diagnosis of relief valve components.

[0020] 8) Through the set proportional speed control valve test module and hydraulic circuit design, the performance tests such as flow and pressure characteristics of the proportional speed control valve can be completed quickly and efficiently. At the same time, the pressure holding and sealing performance of the proportional speed control valve in the non-open state can be accurately detected, which can quickly assist in the fault diagnosis of the proportional speed control valve.

[0021] 9) Through the design of the pressure reducing valve test module and hydraulic circuit, the pressure of the pressure reducing valve can be quickly and efficiently adjusted. The load can also be simulated by adjusting the throttle valve, and the performance of the pressure reducing valve such as flow and pressure characteristics can be tested under different load conditions. This can quickly assist in the parameter setting, performance testing and fault diagnosis of the pressure reducing valve.

[0022] 10) By setting up a hydraulic station, vibration simulation control module, and vibration simulation test bench, the displacement detection of the actual movement of the servo cylinder can be compared with the given control signal to quickly determine the performance of the high-frequency servo valve or proportional speed control valve, thereby improving the fault diagnosis efficiency of this type of hydraulic valve. The "parallel double cylinder structure" installation method realizes the extension and retraction of the servo cylinder and the detection of the external sliding displacement sensor, which facilitates the installation of the acceleration sensor on the shaft end of the single piston double piston rod assembly, effectively increasing the number of detection sensors that can be installed on the servo cylinder and reducing the design and installation difficulty of the hydraulic device.

[0023] 11) Through the set operation and monitoring host computer, a complete instruction operation interface and data monitoring interface are independently provided. At the same time, single analog quantity data and curves are designed for pressure, flow, displacement, acceleration, etc. Correlation analysis curves such as pressure difference, flow difference, and displacement difference are also modeled and displayed. In vibration simulation, a comparison curve between the given vibration waveform spectrum signal and the actual detection data of the displacement sensor is also given. The diversified data processing and display functions are powerful.

[0024] 12) The device has a sophisticated overall structure, complete configuration, rich functions, and strong practicality. It is suitable for use in hydraulic valves and for conducting vibration simulation tests and experiments.

[0025] 13) The device is equipped with an operation and monitoring host computer and an electrical control cabinet. The entire hydraulic device can automatically run, test and stop after issuing a command to perform various valve tests and vibration simulations. It has rich control functions and a high degree of automation. Attached Figure Description

[0026] The present invention will be further described below with reference to the accompanying drawings and embodiments: Figure 1 This is a schematic diagram of the overall layout of the present invention.

[0027] Figure 2 This is a schematic diagram of the hydraulic station structure in this invention (first perspective).

[0028] Figure 3 for Figure 2 A magnified view of a portion of point A in the middle.

[0029] Figure 4 for Figure 2 A magnified view of a portion of point B in the middle.

[0030] Figure 5 This is a schematic diagram of the hydraulic station structure in this invention (second perspective).

[0031] Figure 6 This is a schematic diagram of the valve testing platform in this invention.

[0032] Figure 7 This is a schematic diagram (first-person view) of the structure of the valve testing module and the vibration simulation control module in this invention.

[0033] Figure 8 This is a schematic diagram (second perspective) of the structure of the valve testing module and vibration simulation control module in this invention.

[0034] Figure 9 This is a schematic diagram of the vibration simulation test bench in this invention.

[0035] Figure 10 This is a schematic diagram of the control principle of the hydraulic device for testing and simulating vibration of hydraulic valves in this invention.

[0036] Figure 11 This is a hydraulic schematic diagram of the hydraulic device in this invention.

[0037] Figure 12 for Figure 11 Hydraulic schematic diagram of the medium hydraulic power unit.

[0038] Figure 13 for Figure 11 Hydraulic schematic diagram of the valve component test bench.

[0039] Figure 14 for Figure 11 Hydraulic schematic diagram of the medium proportional directional valve test module.

[0040] Figure 15 for Figure 11 Hydraulic schematic diagram of the balance valve test module.

[0041] Figure 16 for Figure 11 Hydraulic schematic diagram of the overflow valve test module.

[0042] Figure 17 for Figure 11 Hydraulic schematic diagrams of the medium-proportional speed control valve test module and the pressure reducing valve test module.

[0043] Figure 18 for Figure 11 Hydraulic schematic diagram of the vibration simulation control module and vibration simulation test bench. Detailed Implementation

[0044] like Figure 1 , Figure 11 As shown, a hydraulic device for testing hydraulic valve components and simulating vibration includes a hydraulic station 1, a valve testing bench 2, a proportional directional valve testing module 3, a balance valve testing module 4, a relief valve testing module 5, a proportional speed control valve testing module 6, a pressure reducing valve testing module 7, a vibration simulation control module 8, a vibration simulation testing bench 9, an operation and monitoring host computer 10, and an electrical control cabinet 11.

[0045] The hydraulic station 1 is connected to the valve test bench 2 via pipelines. The valve test bench 2 is equipped with and connected to the following test modules via pipelines: proportional directional valve test module 3, balance valve test module 4, relief valve test module 5, proportional speed control valve test module 6, pressure reducing valve test module 7, and vibration simulation control module 8. The vibration simulation control module 8 is connected to the vibration simulation test bench 9 via pipelines. The entire hydraulic device is operated and monitored by the host computer 10, and powered and controlled by the electrical control cabinet 11.

[0046] like Figure 2-5 , Figure 12 As shown, the hydraulic station 1 includes an oil tank base 101, a motor-driven oil pump assembly 102, a motor-driven oil pump assembly 2 103, a hydraulic oil tank 104, a pressure control valve block 105, a solenoid relief valve 106, a connecting ball valve 107, a solenoid relief valve 2 108, a hydraulic station pressure sensor 109, an oil pump output flow meter 110, a high-pressure oil filter 111, a hydraulic hose 5 112, an overflow flow meter 113, an oil cooling device 114, a return oil filter 115, a pressure and vibration control valve block 116, and a ball valve. 117. Ball valve 2; 118. High-pressure oil filter 2; 119. High-frequency servo valve; 120. Hydraulic hose 1; 121. Hydraulic hose 2; 122. Throttle valve 1; 123. Throttle valve 2; 124. Protective relief valve; 125. Throttle valve 3; 126. Accumulator; 127. Pressure reducing valve 1; 128. Hydraulic hose 3; 129. Hydraulic hose 4; 130. Check valve; 131. Ball valve 3; 132. Return oil hose; 133. Return oil flow meter; 134. Main inlet oil pressure sensor; 135. Main return oil pressure sensor; 136.

[0047] like Figure 2-5 , Figure 12As shown, a motor-driven oil pump assembly 102 and a motor-driven oil pump assembly 103 are installed at the bottom of the oil tank base 101, and a hydraulic oil tank 104 is installed at the top of the oil tank base 101. The oil inlet of both motor-driven oil pump assembly 102 and motor-driven oil pump assembly 103 are connected to the hydraulic oil tank 104 via hydraulic hoses. The oil outlets of motor-driven oil pump assembly 102 and motor-driven oil pump assembly 103 are connected to the pressure control valve block 105 via stainless steel pipes. The pressure control valve block 105 is equipped with a solenoid relief valve 106, a connecting ball valve 107, a solenoid relief valve 108, and a hydraulic station pressure sensor 109. The two sets of motor-driven oil pump assemblies serve as backups for each other and can also be used simultaneously, significantly increasing the system flow and pressure adjustment range of the entire hydraulic device, providing a safe and controllable power source for various flow and pressure changes throughout the hydraulic system.

[0048] like Figure 2-5 , Figure 12 As shown, the pressure control valve block 105 is connected to the oil pump output flow meter 110, which is connected to the inlet of the high-pressure oil filter 111. The outlet of the high-pressure oil filter 111 is connected to the valve test bench 2 via hydraulic hose 112. The outlets of the electromagnetic relief valve 106 and the electromagnetic relief valve 108 are connected to the relief flow meter 113 via pipelines. The outlet of the relief flow meter 113 is connected to the oil cooling device 114 via pipelines. The outlet of the oil cooling device 114 is connected to the return oil filter 115 on the hydraulic oil tank 104 via pipelines. This allows for accurate differentiation and detection of the effective flow rate entering various valve test modules in the valve test bench 2 and the ineffective flow rate directly overflowing back to the oil tank. It provides an independent control loop for each valve test module and significantly increases the system's operating time under various loads during valve testing and vibration simulation through the oil cooling device 114, meeting the time requirements for various valve testing and vibration simulation.

[0049] like Figure 2-5 , Figure 12As shown, the outlet of the high-pressure oil filter 111 is connected to the transformer and vibration control valve block 116 via a pipeline. A ball valve 117 is installed at the inlet of the transformer and vibration control valve block 116. The outlet of ball valve 117 is connected to the inlet of ball valve 118. The outlet of ball valve 118 is connected to the high-pressure oil filter 119. The outlet of high-pressure oil filter 119 is connected to the inlet of high-frequency servo valve 120. The outlet of high-frequency servo valve 120 is connected to hydraulic hoses 121 and 122. The outlet of ball valve 117 is connected to the inlet of throttle valve 123. The outlet of throttle valve 123 is connected to throttle valve 124, protective relief valve 125, throttle valve 126, and accumulator 127. The outlet of throttle valve 124 is connected to pressure reducing valve 128. Pressure reducing valve 128 is connected to valve test bench 2 via hydraulic hose 129. The oil outlets of the overflow valve 125 and throttle valve 126 are connected to the return port of the high-frequency servo valve 120, and the oil outlet of ball valve 117 is connected to the valve test bench 2 via hydraulic hose 130. This provides an independent servo control loop for vibration simulation, reducing interference to the given vibration waveform spectrum signal during simulation, ensuring simulation accuracy, providing an independent dynamic performance test control loop for the proportional speed control valve, and also providing the control pressure loop required for valve testing. The pressure of the control loop is precisely adjustable.

[0050] like Figure 2-5 , Figure 12 As shown, the outlet of ball valve 132 is connected to return flow meter 134, which is connected to hydraulic oil tank 104 via a pipeline. The outlet of high-pressure oil filter 111 is connected to main inlet pressure sensor 135, and the outlet of ball valve 132 is connected to main return pressure sensor 136. Through the circuit design of the pressure-changing and vibration control valve block 116, all oil entering various valve component test modules and vibration simulation of the entire hydraulic device passes through return flow meter 134 to hydraulic oil tank 104, realizing the detectable and calculable flow rate used for all tests of the hydraulic device. At the same time, the inlet and return pressures of all oil entering valve component test modules and vibration simulation tests are accurately detected.

[0051] like Figure 6 , Figure 13 As shown, the valve test bench 2 includes a support base 201, a main oil inlet pipeline 202, a main oil return pipeline 203, an oil supply pipeline 1 204, an oil supply pipeline 205, an oil supply pipeline 3 206, a pressure control pipeline 207, an instrument panel 208, a valve mounting bracket 209, a pressure gauge group 1 210, and a pressure relay 211.

[0052] like Figure 6 , Figure 13As shown, the main oil inlet pipe 202 and the main oil return pipe 203 are installed at the bottom of the support base 201. Oil supply pipe 1 204, oil supply pipe 205, oil supply pipe 3 206, and a transformer control pipe 207 are installed in the middle of the support base 201. An instrument panel 208 and a valve mounting bracket 209 are installed on the top of the support base 201. Pressure gauge group 1 210 and a pressure relay 211 are installed on the instrument panel 208. The main oil inlet pipe 202 is connected to hydraulic hose 5 112. Oil line 203 is connected to return oil hose 133, oil supply line 1 204 is connected to hydraulic hose 121, oil supply line 2 205 is connected to hydraulic hose 4 130, oil supply line 3 206 is connected to hydraulic hose 2 122, and pressure control line 207 is connected to hydraulic hose 3 129. Through the linear array method of "centralized pipelines and decentralized valve groups", independent control loops are provided for various valve testing modules and vibration simulation control modules, while improving the scalability of the entire hydraulic device.

[0053] like Figure 7-8 , Figure 14 As shown, the proportional directional valve test module 3 includes a proportional directional valve test valve block 301, an inlet ball valve 302, a return ball valve 303, an inlet pipeline 304, a return pipeline 305, an isolation ball valve 306, an isolation ball valve 2 307, an isolation ball valve 308, a pressure sensor 1 309, a pressure sensor 2 310, a proportional directional valve 311, a proportional directional valve sealing plate 1 312, and a proportional directional valve sealing plate 2 313.

[0054] like Figure 7-8 , Figure 14As shown, the back of the proportional directional valve test block 301 is equipped with an inlet ball valve 302 and a return ball valve 303. The inlet ball valve 302 is connected to the inlet pipeline 304, and the return ball valve 303 is connected to the return pipeline 305. The side of the proportional directional valve test block 301 is equipped with a first isolation ball valve 306, a second isolation ball valve 307, a third isolation ball valve 308, a first pressure sensor 309, and a second pressure sensor 310. The first isolation ball valve 306, the second isolation ball valve 307, and the third isolation ball valve 308 are all installed between the first pressure sensor 309 and the second pressure sensor 310. The top of the proportional directional valve test block 301 is equipped with a proportional directional valve 311, a first proportional directional valve sealing plate 312, and a second proportional directional valve sealing plate 313. Inlet ball valve 302 is connected to the inlet of proportional directional valve 311, the inlet of proportional directional valve sealing plate 312, and the inlet of proportional directional valve sealing plate 313. Return ball valve 303 is connected to the return port of proportional directional valve 311, the return port of proportional directional valve sealing plate 312, and the return port of proportional directional valve sealing plate 313. Pressure sensor 309 and pressure sensor 310 are located at the two outlet ports of proportional directional valve 311, respectively. This hydraulic circuit design enables testing of proportional directional valves of various specifications, including zero-position on / off performance testing and flow and pressure characteristics testing at ports A and B.

[0055] like Figure 7-8 , Figure 15 As shown, the balance valve test module 4 includes a balance valve test valve block 401, an inlet ball valve 2 402, a return ball valve 2 403, an inlet pipeline 2 404, a return pipeline 2 405, a throttle valve 406, a pressure sensor 3 407, a pressure sensor 408, a solenoid directional valve 1 409, a balance valve 410, and a balance valve sealing plate 411.

[0056] like Figure 7-8 , Figure 15As shown, the back of the balance valve test block 401 is equipped with an inlet ball valve 402 and a return ball valve 403. The inlet ball valve 402 is connected to the inlet pipeline 404, and the return ball valve 403 is connected to the return pipeline 405. The side of the balance valve test block 401 is equipped with a throttle valve 406, a pressure sensor 407, and a pressure sensor 408. The top surface of the balance valve test block 401 is equipped with a solenoid directional valve 409, a balance valve 410, and a balance valve sealing plate 411. The inlet ball valve 402 is connected to the inlet of the solenoid directional valve 409, and the return ball valve 403 is connected to the return port of the solenoid directional valve 409. The outlet of the solenoid directional valve 409 is connected to the throttle valve 406. The balance valve 410 is connected to the forward inlet of valve 6, and the throttle valve 406 is connected to the reverse inlet of valve 410. The control port of balance valve 410 is connected to the transformer control line 207. Pressure sensor 407 is installed at the control port of balance valve 410, and pressure sensor 408 is installed at the reverse inlet of balance valve 410. This hydraulic circuit design enables the testing of balance valves of various specifications. It can perform performance tests such as reverse on / off performance test and forward flow and pressure characteristics test. By adjusting the pressure of the control port of balance valve 410, the reverse opening and closing characteristics of balance valve 410 can be quickly detected. It also provides a fast and efficient testing method for modifying and optimizing the reverse opening and closing characteristics of balance valve 410.

[0057] like Figure 7-8 , Figure 16 As shown, the overflow valve test module 5 includes an overflow valve test block 501, an inlet ball valve 3 502, a return ball valve 3 503, an inlet pipeline 3 504, a return pipeline 3 505, an isolation ball valve 4 506, an isolation ball valve 507, an isolation ball valve 6 508, an isolation ball valve 7 509, an overflow valve 1 510, an overflow valve 2 511, an overflow valve sealing plate 1 512, and an overflow valve sealing plate 2 513.

[0058] like Figure 7-8 , Figure 16As shown, the back of the overflow valve test valve block 501 is equipped with an inlet ball valve 3 502 and a return ball valve 3 503. The inlet ball valve 3 502 is connected to the inlet pipeline 3 504, and the return ball valve 3 503 is connected to the return pipeline 3 505. The outlet of the inlet ball valve 3 502 is connected to the isolation ball valve 4 506, the isolation ball valve 507, the isolation ball valve 6 508, and the isolation ball valve 7 509. The outlet of the isolation ball valve 4 506... The oil port connects to relief valve 1 (510), the oil outlet of isolation ball valve 5 (507) connects to relief valve 2 (511), the oil outlet of isolation ball valve 6 (508) connects to relief valve sealing plate 1 (512), and the oil outlet of isolation ball valve 7 (509) connects to relief valve sealing plate 2 (513). The oil outlets of relief valve 1 (510), relief valve 2 (511), relief valve sealing plate 1 (512), and relief valve sealing plate 2 (513) are connected to return ball valve 3 (503). This hydraulic circuit design enables testing of relief valves of various specifications, allowing for rapid parameter tuning, opening and closing performance testing, and positive flow and pressure characteristic testing. Furthermore, the included return flow meter 134 accurately detects the pressure-holding and sealing performance of the relief valve in its non-open state, quickly assisting in the fault diagnosis of hydraulic components and significantly improving the efficiency of parameter tuning and fault diagnosis for relief valve components.

[0059] like Figure 7-8 , Figure 17 As shown, the proportional speed control valve test module 6 includes a proportional speed control valve test valve block 601, an inlet ball valve 602, a return ball valve 603, an inlet pipeline 604, a return pipeline 605, and a proportional speed control valve 606.

[0060] like Figure 7-8 , Figure 17 As shown, the proportional speed control valve test valve block 601 has an inlet ball valve 602 and a return ball valve 603 mounted on its back. The inlet ball valve 602 is connected to the inlet pipeline 604, and the return ball valve 603 is connected to the return pipeline 605. A proportional speed control valve 606 is installed between the inlet ball valve 602 and the return ball valve 603. This hydraulic circuit design allows for rapid and efficient testing of the proportional speed control valve's flow and pressure characteristics, as well as precise detection of its pressure-holding and sealing performance in the non-open state, thus quickly assisting in the fault diagnosis of the proportional speed control valve.

[0061] like Figure 7-8 , Figure 17 As shown, the pressure reducing valve test module 7 includes a pressure reducing valve test valve block 701, an inlet ball valve 702, a return ball valve 703, a pressure relief pipeline 704, an inlet pipeline 705, a return pipeline 706, a pressure reducing valve 707, a throttle valve 708, and a pressure sensor 709.

[0062] like Figure 7-8 , Figure 17As shown, the back of the pressure reducing valve test block 701 is equipped with an inlet ball valve 702, a return ball valve 703, and a pressure relief line 704. The inlet ball valve 702 is connected to the inlet line 705, and the return ball valve 703 is connected to the return line 706. The inlet ball valve 702 is connected to the inlet of the pressure reducing valve 707, and the outlet of the pressure reducing valve 707 is connected to the throttle valve 708. A pressure sensor 709 is installed between the pressure reducing valve 707 and the throttle valve 708. The drain port of the pressure reducing valve 707 is connected to the pressure relief line 704, and the throttle valve 708 is connected to the return ball valve 703. This hydraulic circuit design allows for rapid and efficient pressure setting of the pressure reducing valve. It also allows for simulating changes in load by adjusting the throttle valve 708, enabling performance tests such as flow and pressure characteristics of the pressure reducing valve under different load conditions. This design quickly assists in parameter setting, performance testing, and fault diagnosis of the pressure reducing valve.

[0063] like Figure 7-8 , Figure 18 As shown, the vibration simulation control module 8 includes a vibration simulation control valve block 801, ball valve four 802, oil supply line four 803, oil supply line five 804, return oil line 805, oil supply line six 806, ball valve five 807, ball valve six 808, ball valve seven 809, ball valve eight 810, solenoid directional valve two 811, oil outlet line one 812, oil outlet line two 813, and proportional speed control valve two 814.

[0064] like Figure 7-8 , Figure 18 As shown, the vibration simulation control valve block 801 has a ball valve 802, an oil supply line 803, an oil supply line 804, and a return line 805 mounted on its back. The vibration simulation control valve block 801 has an oil supply line 806, a ball valve 807, a ball valve 808, a ball valve 809, a ball valve 810, a solenoid directional valve 811, an oil outlet line 812, and an oil outlet line 813 mounted on its side. A proportional speed control valve 814 is mounted on the top surface of the vibration simulation control valve block 801. One end of the oil supply line 806 is connected to the oil supply line 805, and another end is connected to the ball valve 802. One end of the oil supply line 803 is connected to the oil supply line 805. Connect to line 3 206. One end of oil supply line 4 803 is connected to ball valve 5 807. One end of oil supply line 5 804 is connected to oil supply line 1 204. One end of oil supply line 5 804 is connected to ball valve 6 808. Ball valve 5 807 is connected to oil outlet line 2 813. Ball valve 6 808 is connected to oil outlet line 1 812. Ball valve 4 802 is connected to proportional speed control valve 2 814. Proportional speed control valve 2 814 is connected to the oil inlet of solenoid directional valve 2 811. The oil outlet of solenoid directional valve 2 811 is connected to ball valve 7 809 and ball valve 8 810 respectively. Ball valve 7 809 is connected to oil outlet line 1 812. Ball valve 8 810 is connected to oil outlet line 2 813.

[0065] Together with the high-frequency servo valve 120, it forms an independent hydraulic circuit capable of vibration simulation, enabling the simulation of arbitrary vibration waveforms. It also provides an independent hydraulic circuit for dynamic performance testing of the proportional speed control valve 814, ensuring the independence and integrity of the two hydraulic circuits under the same load.

[0066] like Figure 9 , Figure 18 As shown, the vibration simulation test bench 9 further includes a support 901, a pressure gauge assembly 902, a servo cylinder 903, an oil supply valve block 904, an oil supply valve block 905, a double-headed screw assembly 906, a single-piston and double-piston rod assembly 907, a displacement sensor 908, an overflow oil collection pipeline 909, a displacement detection rod 910, and an acceleration sensor 911.

[0067] like Figure 9 , Figure 18 As shown, a pressure gauge assembly 902 is installed in the middle of the support 901, and a servo cylinder 903 is installed on the top of the support 901. A first oil supply valve block 904 and a second oil supply valve block 905 are installed at both ends of the servo cylinder 903. The first oil supply valve block 904 and the second oil supply valve block 905 are connected and fixed by a double-headed screw assembly 906. A single-piston double-piston rod assembly 907 is installed inside the servo cylinder 903. A displacement sensor 908 and an overflow collection pipe 909 are installed on the sides of the first oil supply valve block 904 and the second oil supply valve block 905. The first oil supply valve block 904 is connected to an oil outlet pipe 812, and the second oil supply valve block 905 is connected to an oil outlet pipe 813. The single-piston double-piston rod assembly 907 is connected to a displacement detection rod 910 via a bracket. The displacement sensor 908 is slidably fitted with the displacement detection rod 910. An acceleration sensor 911 is installed at the end of the single-piston double-piston rod assembly 907.

[0068] By accurately detecting the displacement and acceleration motion parameters of the actual movement of the servo cylinder, feedback is sent to the motion controller and the high-frequency servo valve 120 to form a closed-loop control, making the vibration simulation of the servo cylinder more accurate. At the same time, by comparing the displacement detection of the actual movement of the servo cylinder with the given control signal, the performance of the high-frequency servo valve 120 or the proportional speed control valve 814 can be quickly determined, improving the fault diagnosis efficiency of this type of hydraulic valve. The extension and retraction of the servo cylinder 903 and the detection of the external sliding displacement sensor 908 are realized through the "parallel double cylinder structure" installation form, which facilitates the installation of the acceleration sensor 911 on the shaft end of the single piston double piston rod assembly 907.

[0069] like Figure 1 , Figure 8As shown, the operation and monitoring host computer 10 includes an operation console, an operation control system, and a data monitoring system. It independently provides a complete instruction operation interface and a data monitoring interface. At the same time, it designs single analog quantity data and curves for pressure, flow, displacement, acceleration, etc. It also models and displays the correlation analysis curves of pressure difference, flow difference, displacement difference, etc. In vibration simulation, it also provides a comparison curve between the given vibration waveform spectrum signal and the actual detection data of displacement sensor 908. It has powerful and diverse data processing and display functions.

[0070] like Figure 1 , Figure 8 As shown, the electrical control cabinet 11 includes a cabinet, a PLC controller, and a motion controller. Matching, independent, and parallel control units are set according to the testing purpose. The independent PLC controller controls the operation of the entire hydraulic device and tests various valve components, while the independent motion controller controls vibration simulation.

[0071] A method for using a hydraulic device to perform hydraulic valve testing and vibration simulation includes the following steps: Step 1: Before performing fault diagnosis and performance testing of the proportional directional valve, install the proportional directional valve 311 to be tested on the proportional directional valve test block 301. Seal the other mounting holes on the proportional directional valve test block 301 with proportional directional valve sealing plates 1 (312) and 2 (313). Open the inlet ball valve 1 (302) and return ball valve 1 (303). Depending on the bore specification of the proportional directional valve 311 under test, select to open the isolation ball valve 1 (306), isolation ball valve 2 (307), or isolation ball valve 3 (308). Keep all other ball valves in the hydraulic system closed. Start the motor oil pump assembly 1 through the operation control system and PLC controller. 102. With the oil cooling device 114 energized, the solenoid relief valve 106 is operated, maintaining the proportional directional valve 311 opening input value at 0%. The solenoid relief valve 106 is adjusted to the given working pressure value X. The value of the return oil flow meter 134 and the changes in its flow parameter curve are observed in the data monitoring system. This can test the zero-position characteristic of the proportional directional valve 311 and diagnose the internal leakage fault characteristics of the proportional directional valve 311 in the zero-position state. By operating the control system and PLC controller, the opening input value of the proportional directional valve 311 is adjusted to -100%, increasing the oil pump flow rate of the motor oil pump assembly 102 from M to N. The data monitoring system... The system monitors the changes in values ​​from the main inlet pressure sensor 135, pressure sensor 310, and oil pump output flow meter 110. The data monitoring system displays the pressure difference curve between the main inlet pressure sensor 135 and pressure sensor 310 and the parameter change curve of the oil pump output flow meter 110. It can also test the no-load flow characteristics of channel B of the proportional directional valve 311 at -100% opening. By operating the control system and PLC controller to set the proportional directional valve 311 opening input value to 100%, the oil pump flow rate of the motor oil pump assembly 102 is increased from M to N. The main inlet pressure sensor 135 is then observed on the data monitoring system. The data monitoring system displays the pressure difference curve between the main inlet pressure sensor 135 and the pressure sensor 309 and the parameter change curve of the oil pump output flow meter 110, based on the changes in the values ​​of the pressure sensor 309 and the oil pump output flow meter 110. This allows testing the flow characteristics of the A channel of the proportional directional valve 311 at 100% opening. By operating the control system and PLC controller to uniformly change the opening of the proportional directional valve 311 from -100% to 100%, the data monitoring system observes the value change of the return flow meter 134, allowing testing of the linear flow characteristics of the A and B channels of the proportional directional valve 311 when the opening changes.

[0072] Step Two: Before performing fault diagnosis and performance testing of the balance valve, install the balance valve 410 to be tested on the balance valve test block 401. Seal the other mounting holes of various sizes on the balance valve test block 401 with the balance valve sealing plate 411. Open ball valve 117, inlet ball valve 2 402, and return ball valve 2 403. Adjust throttle valve 123, throttle valve 2 124, and throttle valve 406 to the fully open state. Close throttle valve 3 126 and all other ball valves of the hydraulic device. Adjust the protection relief valve 125 to the maximum value and adjust the outlet pressure of pressure reducing valve 128 to the minimum value of 0. Start the operation through the control system and PLC controller. The motor-driven oil pump assembly 102 and oil cooling device 114 are powered. The solenoid relief valve 106 is energized. First, the pressure of the solenoid relief valve 106 is adjusted to the test value M. Then, the solenoid directional valve 409 is energized to the left working position via the operation control system and PLC controller. The changes in the values ​​of the oil pump output flow meter 110, overflow flow meter 113, and return flow meter 134 are observed on the data monitoring system. If the values ​​of the oil pump output flow meter 110 and overflow flow meter 113 are equal, and the value of the return flow meter 134 is 0, it can be determined that the reverse pressure holding and switching performance of the tested balance valve 410 is normal. Gradually increase the pressure reducing valve 12... The outlet pressure value of 8 is monitored on the data monitoring system by observing the changes in the values ​​of pressure sensor 407 and return oil flow meter 134. The data monitoring system displays the opening and closing characteristic curve of the tested balance valve 410, from which the minimum opening pressure of the control port of the tested balance valve 410 when the return oil flow meter 134 is greater than 0 can be obtained. By changing the characteristic parameters of the control port section of the tested balance valve 410, the opening and closing pressure of the tested balance valve 410 can be quickly adjusted. The outlet pressure value of pressure reducing valve 128 is kept at value N, and the pump displacement of motor oil pump assembly 102 is gradually adjusted from small to large on the data monitoring system. The changes in the values ​​of pressure sensor 408, main return oil pressure sensor 136, and oil pump output flow meter 110 are observed. The data monitoring system displays the reverse pressure / flow characteristic curve of the tested balance valve 410. By operating the control system and PLC controller, the solenoid directional valve 409 is energized to the right working position, and the oil pump displacement of the motor oil pump assembly 102 is gradually adjusted from small to large. The changes in the values ​​of main inlet oil pressure sensor 135, pressure sensor 408, and oil pump output flow meter 110 are observed on the data monitoring system. The data monitoring system displays the forward pressure / flow characteristic curve of the tested balance valve 410.

[0073] Step 3: Before performing fault diagnosis and performance testing of the relief valve, install the relief valve to be tested, 510, on the relief valve test block 501. Seal the other mounting holes on the relief valve test block 501 with relief valve 2, 511, relief valve sealing plate 1, 512, and relief valve sealing plate 2, 513. Open the inlet ball valve 3, 502, and the return ball valve 3, 503. Based on the nominal diameter of the relief valve to be tested, open the isolation ball valve 4, 506. Keep all other ball valves in the hydraulic system closed. Through operation... The control system and PLC controller start the motor oil pump assembly 102 and the oil cooling device 114, energizing the solenoid relief valve 106. First, adjust the pressure value of the solenoid relief valve 106 to Y, which is higher than the set value M of the relief valve 510 under test. Adjust the relief valve 510 under test from low to high, and observe the value and pressure curve changes of the main inlet oil pressure sensor 135 on the data monitoring system. When the value of the main inlet oil pressure sensor 135 reaches M, stop adjusting the relief valve under test. At step 510, the tested relief valve 510 has completed rapid parameter tuning. Continue increasing the pump displacement of the motor oil pump assembly 102 to the maximum design flow rate N of the tested relief valve 510. Observe the values ​​and curve changes of the main inlet pressure sensor 135 and the relief flow meter 113 on the data monitoring system. If the value of the main inlet pressure sensor 135 remains at value M, and the value of the relief flow meter 113 remains at 0, it indicates that the tested relief valve 510 has completed rapid tuning. At the same time, the actual maximum flow rate of the tested relief valve-510 was also tested and found to meet the factory design value. Keeping the set value M of the tested relief valve-510 unchanged, the pump displacement of the motor oil pump assembly-102 was first adjusted to the minimum value, and then gradually increased to the value H. The changes in the values ​​of the main inlet oil pressure sensor 135 and the oil pump output flow meter 110 were observed on the data monitoring system. The data monitoring system displayed the pressure / flow curve of the tested relief valve-510 under the set pressure value M.

[0074] Step 4: Before performing fault diagnosis and performance testing of the proportional speed control valve, install the proportional speed control valve to be tested, 606, on the proportional speed control valve test block 601. Open the inlet ball valve 602 and the return ball valve 603, while keeping all other ball valves of the hydraulic system closed. Start the motor-oil pump assembly 102 and the oil cooling device 114 through the operation control system. energize the solenoid relief valve 106, adjust the pressure of the solenoid relief valve 106 to M, adjust the oil pump displacement of the motor-oil pump assembly 102 to N, and de-energize the proportional speed control valve 606. Observe the changes in the values ​​of the oil pump output flow meter 110, the overflow flow meter 113, and the return flow meter 134 on the data monitoring system. If the values ​​of the oil pump output flow meter 110 and the overflow flow meter 113 are different... 3. With the values ​​equal, the return flow meter 134 shows a value of 0, indicating that the on / off performance of the tested proportional speed control valve 606 at 0% opening is normal. The proportional speed control valve 606 is operated from 0% to 100%, and the value and curve change of the return flow meter 134 are observed on the data monitoring system to determine the linear flow change characteristic of the tested proportional speed control valve 606. The proportional speed control valve 606 is operated to an opening value of X in the operating control system, and the pump displacement of the motor oil pump assembly 102 is adjusted from small to large. The changes in the values ​​of the oil pump output flow meter 110 and the hydraulic station pressure sensor 109 are observed on the data monitoring system. The data monitoring system displays the pressure / flow characteristic curve of the tested proportional speed control valve 606 at the opening value X. After installing the proportional speed control valve 814 to be tested on the vibration simulation control valve block 801, open ball valves 117, 402, 709, and 810, while keeping all other ball valves of the hydraulic device closed. Start the motor oil pump assembly 102 and oil cooling device 114 through the operation control system, energize the solenoid relief valve 106, adjust the pressure of the solenoid relief valve 106 to M, adjust the oil pump displacement of the motor oil pump assembly 102 to N, set the proportional speed control valve 814 to a certain opening degree through the operation control system, and energize the solenoid directional valve 811 through the operation control system. The servo cylinder 903 performs extension and retraction actions according to the given control signal. The displacement sensor 908 feeds back the motion parameters of the single-piston double-piston rod assembly 907 to the electrical control cabinet 11 through signal cables and Ethernet. The dynamic performance of the proportional speed control valve 814 can be tested and judged through the oil pump output flow meter 110, the opening degree of the proportional speed control valve 814, and the feedback data of the displacement sensor 908.

[0075] Step 5: Before performing fault diagnosis and performance testing of the pressure reducing valve, install the pressure reducing valve 2 707 to be tested on the pressure reducing valve test valve block 701, open the inlet ball valve 5 702 and the return ball valve 5 703, and keep all other ball valves of the hydraulic device closed; start the motor oil pump assembly 102 and the oil cooling device 114 through the operation control system and PLC controller, energize the solenoid relief valve 106, adjust the pressure of the solenoid relief valve 106 to M, and adjust the motor oil pump assembly 102... 2. Set the oil pump displacement to N, adjust the opening of throttle valve 708, and observe the change in the value of return oil flow meter 134 on the data monitoring system. When the return oil flow meter 134 is less than XL / min, stop adjusting throttle valve 708, adjust the pressure reducing valve 707 under test, and observe the change in the value of pressure sensor 709 on the data monitoring system. When the value of pressure sensor 709 is J, stop adjusting pressure reducing valve 707 under test. At this time, pressure reducing valve 707 under test has completed its operation. For rapid parameter setting; continue to increase the opening of throttle valve 5 708, and observe the changes in the values ​​of main inlet oil pressure sensor 135, pressure sensor 5 709, and return oil flow meter 134 on the data monitoring system. The data monitoring system displays the curve of the difference between the main inlet oil pressure sensor 135 and pressure sensor 5 709 versus the change in return oil flow meter 134, which is the pressure difference / flow characteristic curve of the pressure reducing valve 2 707 under the test when simulating load changes at this setting value; adjust the opening of throttle valve 5 708 to the maximum value, and adjust the oil pump displacement of motor oil pump assembly 102 from small to large. Observe the changes in the values ​​of main inlet oil pressure sensor 135, pressure sensor 5 709, and oil pump output flow meter 110 on the data monitoring system. The data monitoring system displays the curve of the difference between the main inlet oil pressure sensor 135 and pressure sensor 5 709 versus the change in oil pump output flow meter 110, which is the no-load pressure difference / flow characteristic curve of the pressure reducing valve 2 707 under the test when the setting parameter is J.

[0076] Step Six: Before performing vibration simulation, open ball valve 117, ball valve 218, ball valve 3132, ball valve 5807, and ball valve 6808, while keeping all other ball valves and throttle valves in the hydraulic system closed. Start the motor-oil pump assembly 102 and oil cooling device 114 via the operation control system and PLC controller. Power on the solenoid relief valve 106, adjust its pressure to M, and adjust the pump displacement of the motor-oil pump assembly 102 to N. Output any given vibration waveform spectrum signal to the motion controller via the operation control system and PLC controller. The motion controller outputs this vibration waveform spectrum signal to the high-frequency servo valve 120, which controls the servo cylinder 903 to perform vibration simulation actions, measured by the displacement sensor 908 and acceleration sensor 908. Sensor 911 feeds back the motion parameters of the single-piston dual-piston rod assembly 907 to the motion controller via signal cable and Ethernet. The motion controller performs PID adjustment based on the target position of the vibration waveform spectrum signal and the feedback data from displacement sensor 908 and acceleration sensor 911 to form closed-loop control, achieving accurate simulation of the given vibration waveform spectrum signal. The data monitoring system can modify the parameters of any given vibration waveform spectrum signal, and then output the modified vibration waveform spectrum signal to the high-frequency servo valve 120. The high-frequency servo valve 120 controls the servo cylinder 903 to perform signal simulation action. At the same time, the data monitoring system displays a comparison curve between the vibration simulation displacement waveform spectrum of the servo cylinder 903 fed back by displacement sensor 908 and the given vibration waveform spectrum signal.

[0077] When the high-frequency servo valve 120 is replaced with a faulty valve, the data monitoring system displays a comparison curve between the vibration simulation displacement waveform spectrum of the servo cylinder 903 fed back by the displacement sensor 908 and the given vibration waveform spectrum signal. Based on the comparison curve, the control performance of the tested high-frequency servo valve 120 can be accurately determined.

Claims

1. A hydraulic device for testing and simulating vibration of hydraulic valve components, characterized in that: The system includes a hydraulic station (1), a pipeline connection between the hydraulic station (1) and the valve test bench (2), and a proportional directional valve test module (3), a balance valve test module (4), an overflow valve test module (5), a proportional speed control valve test module (6), a pressure reducing valve test module (7), and a vibration simulation control module (8) installed on the valve test bench (2) and connected to it via pipelines. The vibration simulation control module (8) is connected to the vibration simulation test bench (9) via pipelines. The entire hydraulic device is operated and monitored by an operation and monitoring host computer (10) and powered and controlled by an electrical control cabinet (11). The hydraulic station (1) includes a hydraulic oil tank (104), the oil inlet of the motor oil pump assembly is connected to the hydraulic oil tank (104); the oil outlet of the motor oil pump assembly is connected to the pressure control valve block (105); the pressure control valve block (105) is connected to the oil pump output flow meter (110), the oil pump output flow meter (110) is connected to the inlet of the high pressure filter (111), and the outlet of the high pressure filter (111) is connected to the valve test bench (2) through the hydraulic hose (112); The pressure control valve block (105) is equipped with an electromagnetic relief valve one (106), a connecting ball valve (107), an electromagnetic relief valve two (108), and a hydraulic station pressure sensor (109); wherein, the oil outlets of the electromagnetic relief valve one (106) and the electromagnetic relief valve two (108) are connected to the overflow flow meter (113) through pipelines, the oil outlet of the overflow flow meter (113) is connected to the oil cooling device (114) through pipelines, and the oil outlet of the oil cooling device (114) is connected to the hydraulic oil tank (104) through pipelines. The outlet of the high-pressure oil filter (111) is connected to the transformer and vibration control valve block (116) via a pipeline; a ball valve (117) is installed at the oil inlet of the transformer and vibration control valve block (116). The oil outlet of ball valve 1 (117) is connected to the oil inlet of ball valve 2 (118), the oil outlet of ball valve 2 (118) is connected to high pressure filter 2 (119), the outlet of high pressure filter 2 (119) is connected to the oil inlet of high frequency servo valve (120), and the oil outlet of high frequency servo valve (120) is connected to hydraulic hose 1 (121) and hydraulic hose 2 (122). The outlet of ball valve 1 (117) is connected to the inlet of throttle valve 1 (123). The outlet of throttle valve 1 (123) is connected to throttle valve 2 (124), protective relief valve (125), throttle valve 3 (126) and accumulator (127). The outlet of throttle valve 2 (124) is connected to pressure reducing valve 1 (128). Pressure reducing valve 1 (128) is connected to valve test bench (2) through hydraulic hose 3 (129). The outlet of protective relief valve (125) and the outlet of throttle valve 3 (126) are connected to the return port of high frequency servo valve (120). The oil outlet of ball valve 1 (117) is connected to valve test bench (2) via hydraulic hose 4 (130); The return port of the high-frequency servo valve (120) is connected to the inlet of the check valve (131), the outlet of the check valve (131) is connected to the inlet of the ball valve (132), and the inlet of the check valve (131) is connected to the valve test bench (2) through the return hose (133); the outlet of the ball valve (132) is connected to the return flow meter (134), and the return flow meter (134) is connected to the hydraulic oil tank (104) through the pipeline; the outlet of the high pressure filter (111) is connected to the main inlet pressure sensor (135), and the outlet of the ball valve (132) is connected to the main return pressure sensor (136).

2. The hydraulic device for testing and simulating vibration of hydraulic valve components according to claim 1, characterized in that: The valve test bench (2) includes a support base (201), and a main oil inlet pipeline (202) and a main oil return pipeline (203) are installed at the bottom of the support base (201). The main oil inlet pipeline (202) is connected to the hydraulic hose five (112), and the main oil return pipeline (203) is connected to the oil return hose (133). The support base (201) is equipped with oil supply line one (204), oil supply line two (205), oil supply line three (206), and transformer control line (207) in the middle. Oil supply line one (204) is connected to hydraulic hose one (121), oil supply line two (205) is connected to hydraulic hose four (130), oil supply line three (206) is connected to hydraulic hose two (122), and transformer control line (207) is connected to hydraulic hose three (129). The support base (201) is equipped with an instrument panel (208) and a valve mounting bracket (209); the instrument panel (208) is equipped with a pressure gauge group (210) and a pressure relay (211).

3. The hydraulic device for testing and simulating vibration of hydraulic valve components according to claim 1, characterized in that: The proportional directional valve test module (3) includes a proportional directional valve test block (301). The back of the proportional directional valve test block (301) is equipped with an inlet ball valve (302) and a return ball valve (303). The inlet ball valve (302) is connected to the inlet pipeline (304), and the return ball valve (303) is connected to the return pipeline (305). The proportional directional valve test valve block (301) is equipped with isolation ball valve one (306), isolation ball valve two (307), isolation ball valve three (308), pressure sensor one (309), and pressure sensor two (310); among them, isolation ball valve one (306), isolation ball valve two (307), and isolation ball valve three (308) are all installed between pressure sensor one (309) and pressure sensor two (310); The proportional directional valve test valve block (301) is equipped with a proportional directional valve (311), a proportional directional valve sealing plate one (312), and a proportional directional valve sealing plate two (313) on its top. The oil inlet ball valve (302) is connected to the oil inlet of the proportional directional valve (311), the oil inlet of the proportional directional valve sealing plate (312), and the oil inlet of the proportional directional valve sealing plate (313); The return ball valve (303) is connected to the return port of the proportional directional valve (311), the return port of the proportional directional valve sealing plate (312), and the return port of the proportional directional valve sealing plate (313). The pressure sensor (309) and the pressure sensor (310) are located at the two outlet ports of the proportional directional valve (311).

4. The hydraulic device for testing and simulating vibration of hydraulic valve components according to claim 2, characterized in that: The balance valve test module (4) includes a balance valve test block (401). The back of the balance valve test block (401) is equipped with an oil inlet ball valve two (402) and an oil return ball valve two (403). The oil inlet ball valve two (402) is connected to the oil inlet pipeline two (404), and the oil return ball valve two (403) is connected to the oil return pipeline two (405). The side of the balance valve test valve block (401) is equipped with throttle valve four (406), pressure sensor three (407), and pressure sensor four (408). The top surface of the balance valve test valve block (401) is equipped with an electromagnetic reversing valve (409), a balance valve (410), and a balance valve sealing plate (411). The inlet ball valve 2 (402) is connected to the inlet of the solenoid directional valve 1 (409), and the return ball valve 2 (403) is connected to the return port of the solenoid directional valve 1 (409). The outlet of the solenoid directional valve 1 (409) is connected to the forward inlet of the throttle valve 4 (406) and the balance valve (410). The throttle valve 4 (406) is connected to the reverse inlet of the balance valve (410). The control port of the balance valve (410) is connected to the transformer control pipeline (207). The pressure sensor 3 (407) is installed at the control port of the balance valve (410), and the pressure sensor 4 (408) is installed at the reverse inlet of the balance valve (410).

5. A hydraulic device for testing and simulating vibration of hydraulic valve components according to claim 2, characterized in that: The overflow valve test module (5) includes an overflow valve test block (501). An inlet ball valve three (502) and a return ball valve three (503) are installed on the back of the overflow valve test block (501). The inlet ball valve three (502) is connected to the inlet pipeline three (504), and the return ball valve three (503) is connected to the return pipeline three (505). The oil outlet of the inlet ball valve three (502) is connected to the isolation ball valve four (506), isolation ball valve five (507), isolation ball valve six (508), and isolation ball valve seven (509); The oil outlet of the isolation ball valve four (506) is connected to the overflow valve one (510), the oil outlet of the isolation ball valve five (507) is connected to the overflow valve two (511), the oil outlet of the isolation ball valve six (508) is connected to the overflow valve sealing plate one (512), the oil outlet of the isolation ball valve seven (509) is connected to the overflow valve sealing plate two (513), and the oil outlets of the overflow valve one (510), overflow valve two (511), overflow valve sealing plate one (512), and overflow valve sealing plate two (513) are all connected to the return ball valve three (503).

6. The hydraulic device for testing and simulating vibration of hydraulic valve components according to claim 2, characterized in that: The proportional speed control valve test module (6) includes a proportional speed control valve test block (601). An inlet ball valve four (602) and a return ball valve four (603) are installed on the back of the proportional speed control valve test block (601). The inlet ball valve four (602) is connected to the inlet pipeline four (604), and the return ball valve four (603) is connected to the return pipeline four (605). A proportional speed control valve one (606) is installed between the inlet ball valve four (602) and the return ball valve four (603). The vibration simulation control module (8) includes a vibration simulation control valve block (801). The vibration simulation control valve block (801) has a ball valve four (802), an oil supply line four (803), an oil supply line five (804), and a return oil line (805) installed on its back. The vibration simulation control valve block (801) is equipped with oil supply line six (806), ball valve five (807), ball valve six (808), ball valve seven (809), ball valve eight (810), solenoid directional valve two (811), oil outlet line one (812), and oil outlet line two (813). A proportional speed control valve (814) is installed on the top surface of the vibration simulation control valve block (801). One end of oil supply line six (806) is connected to oil supply line two (205), and the other end of oil supply line six (806) is connected to ball valve four (802). One end of oil supply line four (803) is connected to oil supply line three (206), and the other end of oil supply line four (803) is connected to ball valve five (807). One end of oil supply line five (804) is connected to oil supply line one (204), and the other end of oil supply line five (804) is connected to ball valve six (808). Ball valve five (807) is connected to the oil outlet line. Two (813) is connected, ball valve six (808) is connected to oil outlet line one (812), ball valve four (802) is connected to proportional speed control valve two (814), proportional speed control valve two (814) is connected to the oil inlet of solenoid directional valve two (811), the oil outlet of solenoid directional valve two (811) is connected to ball valve seven (809) and ball valve eight (810) respectively, ball valve seven (809) is connected to oil outlet line one (812), and ball valve eight (810) is connected to oil outlet line two (813); The vibration simulation test bench (9) includes a support (901), a pressure gauge group two (902) is installed in the middle of the support (901), a servo cylinder (903) is installed on the top of the support (901), and oil supply valve block one (904) and oil supply valve block two (905) are installed at both ends of the servo cylinder (903). The oil supply valve block one (904) and oil supply valve block two (905) are connected and fixed by a double-headed screw assembly (906). A single-piston double-piston rod assembly (907) is installed inside the servo cylinder (903). The oil supply valve block one (904) and oil supply valve block two (905) are connected and fixed by a double-headed screw assembly (906). 4) A displacement sensor (908) and an overflow collection pipe (909) are installed on the side of the oil supply valve block 2 (905). The oil supply valve block 1 (904) is connected to the oil outlet pipe 1 (812). The oil supply valve block 2 (905) is connected to the oil outlet pipe 2 (813). The single piston double piston rod assembly (907) is connected to the displacement detection rod (910) through a bracket. The displacement sensor (908) and the displacement detection rod (910) are slidably installed. An acceleration sensor (911) is installed at the end of the single piston double piston rod assembly (907).

7. A hydraulic device for testing and simulating vibration of hydraulic valve components according to claim 2, characterized in that: The pressure reducing valve test module (7) includes a pressure reducing valve test block (701). The back of the pressure reducing valve test block (701) is equipped with an inlet ball valve five (702), a return ball valve five (703), and a pressure relief pipeline (704). The inlet ball valve five (702) is connected to the inlet pipeline five (705), and the return ball valve five (703) is connected to the return pipeline five (706). The inlet ball valve five (702) is connected to the inlet of the pressure reducing valve two (707), the outlet of the pressure reducing valve two (707) is connected to the throttle valve five (708), a pressure sensor five (709) is installed between the pressure reducing valve two (707) and the throttle valve five (708), the drain port of the pressure reducing valve two (707) is connected to the pressure relief pipeline (704), and the throttle valve five (708) is connected to the return ball valve five (703).

8. A method for testing and simulating the vibration of hydraulic valve components using a hydraulic device according to claim 3, comprising the following steps: Step 1) Before performing fault diagnosis and performance testing of the proportional directional valve, install the proportional directional valve (311) to be tested on the proportional directional valve test block (301), and seal the other mounting holes on the proportional directional valve test block (301) with proportional directional valve sealing plate one (312) and proportional directional valve sealing plate two (313). Step 2) Open the inlet ball valve 1 (302) and the return ball valve 1 (303). According to the bore specification of the proportional directional valve (311) being tested, select to open the isolation ball valve 1 (306), the isolation ball valve 2 (307), or the isolation ball valve 3 (308). Keep all other ball valves of the hydraulic device closed. Step 3) Start the motor oil pump assembly and oil cooling device (114) through the operation control system and PLC controller, operate the electromagnetic relief valve (106) to be energized, keep the opening input value of the proportional directional valve (311) at 0%, adjust the electromagnetic relief valve (106) to the given working pressure value X, observe the value of the return oil flow meter (134) and the change of its flow parameter curve in the data monitoring system, the zero position characteristics of the proportional directional valve (311) can be tested, and the internal leakage fault characteristics of the proportional directional valve (311) in the zero position state can also be diagnosed. Step 4) By operating the control system and PLC controller, the opening input value of the proportional directional valve (311) is -100%, and the oil pump flow rate of the motor oil pump assembly is increased from M to N. The changes in the values ​​of the main inlet pressure sensor (135), pressure sensor 2 (310), and oil pump output flow meter (110) are observed on the data monitoring system. The data monitoring system will display the pressure difference curve between the main inlet pressure sensor (135) and pressure sensor 2 (310) and the parameter change curve of the oil pump output flow meter (110). The no-load flow characteristics of the B channel of the proportional directional valve (311) in the -100% opening state can be tested. Step 5) By operating the control system and PLC controller, the opening input value of the proportional directional valve (311) is set to 100%, and the oil pump flow rate of the motor oil pump assembly is increased from M to N. The changes in the values ​​of the main inlet pressure sensor (135), pressure sensor one (309), and oil pump output flow meter (110) are observed on the data monitoring system. The data monitoring system will display the pressure difference curve between the main inlet pressure sensor (135) and pressure sensor one (309) and the parameter change curve of the oil pump output flow meter (110). The flow characteristics of the A channel of the proportional directional valve (311) at 100% opening can be tested. Step 6) By operating the control system and PLC controller, the opening of the proportional directional valve (311) is changed uniformly from -100% to 100%. The change in the value of the return oil flow meter (134) is observed on the data monitoring system. The linear characteristics of the flow of the A and B channels of the proportional directional valve (311) when the opening state changes can be tested.

9. A method for testing and simulating the vibration of hydraulic valve components using a hydraulic device according to claim 4, comprising the following steps: Step 1) Before performing fault diagnosis and performance testing of the balance valve, install the balance valve (410) to be tested on the balance valve test block (401), and seal the other mounting holes on the balance valve test block (401) with the balance valve sealing plate (411). Step 2) Open ball valve 1 (117), inlet ball valve 2 (402), and return ball valve 2 (403), adjust throttle valve 1 (123), throttle valve 2 (124), and throttle valve 4 (406) to the fully open state, close throttle valve 3 (126) and all other ball valves of the hydraulic device, adjust the protection relief valve (125) to the maximum value, and adjust the outlet pressure of pressure reducing valve 1 (128) to the minimum value of 0; Step 3) Start the motor oil pump assembly and oil cooling device (114) through the operation control system and PLC controller, and operate the electromagnetic overflow valve (106) to get energized. First, adjust the pressure of the electromagnetic overflow valve (106) to the test value M. Then, operate the electromagnetic reversing valve (409) to the left working position through the operation control system and PLC controller to get energized. Observe the changes in the values ​​of the oil pump output flow meter (110), overflow flow meter (113), and return oil flow meter (134) on the data monitoring system. If the values ​​of the oil pump output flow meter (110) and overflow flow meter (113) are equal, and the value of the return oil flow meter (134) is 0, it can be judged that the reverse pressure holding and switching performance of the tested balance valve (410) is normal. Step 4) Gradually increase the outlet pressure value of pressure reducing valve 1 (128), observe the changes in the values ​​of pressure sensor 3 (407) and return oil flow meter (134) on the data monitoring system. The data monitoring system displays the opening and closing characteristic curve of the tested balance valve (410). The minimum opening pressure of the control port of the tested balance valve (410) when the return oil flow meter (134) is greater than 0 can be obtained. By changing the characteristic parameters of the control port section of the tested balance valve (410), the opening and closing pressure of the tested balance valve (410) can be quickly adjusted. Step 5) Keep the outlet pressure of pressure reducing valve 1 (128) at the value N, gradually adjust the oil pump displacement of the motor oil pump assembly from small to large, observe the value changes of pressure sensor 4 (408), main return oil pressure sensor (136), and oil pump output flow meter (110) on the data monitoring system, and the data monitoring system displays the reverse pressure / flow characteristic curve of the tested balance valve (410). Step 6) Operate the solenoid directional valve 1 (409) to the right working position through the operation control system and PLC controller to gradually adjust the oil pump displacement of the motor oil pump assembly from small to large. Observe the value changes of the main oil inlet pressure sensor (135), pressure sensor 4 (408), and oil pump output flow meter (110) on the data monitoring system. The data monitoring system displays the positive pressure / flow characteristic curve of the tested balance valve (410).

10. A method for testing and simulating the vibration of hydraulic valve components using a hydraulic device according to claim 5, comprising the following steps: Step 1) Before performing fault diagnosis and performance testing of the overflow valve, install the overflow valve to be tested (510) on the overflow valve test block (501), and seal the other mounting holes on the overflow valve test block (501) with overflow valve (511), overflow valve sealing plate (512), and overflow valve sealing plate (513). Step 2) Open the inlet ball valve three (502) and the return ball valve three (503). According to the nominal diameter of the overflow valve one (510) being tested, select to open the isolation ball valve four (506). Keep all other ball valves of the hydraulic device closed. Step 3) Start the motor oil pump assembly and oil cooling device (114) through the operation control system and PLC controller, and power the electromagnetic relief valve (106). First, adjust the pressure value of the electromagnetic relief valve (106) to Y. Y is higher than the set value M of the relief valve (510) under test. Adjust the relief valve (510) under test from low to high. Observe the value of the main oil inlet pressure sensor (135) and the pressure curve change on the data monitoring system. When the value of the main oil inlet pressure sensor (135) reaches M, stop adjusting the relief valve (510) under test. At this time, the relief valve (510) under test has completed the rapid parameter setting. Step 4) Continue to increase the pump displacement of the motor oil pump assembly to the maximum design flow rate N of the tested overflow valve (510). Observe the values ​​and curve changes of the main inlet pressure sensor (135) and overflow flow meter (113) on the data monitoring system. If the value of the main inlet pressure sensor (135) is maintained at the value M and the value of the overflow flow meter (113) is always 0, it indicates that the tested overflow valve (510) has completed the rapid adjustment and also tested the actual maximum flow rate of the tested overflow valve (510) to meet the factory design value. Step 5) Keep the set value M of the tested relief valve (510) unchanged, adjust the pump displacement of the motor oil pump assembly to the minimum value first, and then gradually increase it to the value H. Observe the value changes of the main inlet pressure sensor (135) and the oil pump output flow meter (110) on the data monitoring system. The data monitoring system displays the pressure / flow curve of the tested relief valve (510) under the set pressure value M.

11. A method for testing and simulating the vibration of hydraulic valve components using a hydraulic device according to claim 6, comprising the following steps: Step 1) Before performing fault diagnosis and performance testing of the proportional speed control valve, install the proportional speed control valve to be tested (606) on the proportional speed control valve test valve block (601), open the inlet ball valve (602) and the return ball valve (603), and keep all other ball valves of the hydraulic device closed. Step 2) Start the motor oil pump assembly and oil cooling device (114) through the operation control system, operate the electromagnetic overflow valve (106) to be energized, adjust the pressure of the electromagnetic overflow valve (106) to M, adjust the oil pump displacement of the motor oil pump assembly to N, operate the proportional speed control valve (606) to be de-energized, observe the changes in the values ​​of the oil pump output flow meter (110), overflow flow meter (113), and return oil flow meter (134) on the data monitoring system. If the values ​​of the oil pump output flow meter (110) and overflow flow meter (113) are equal, and the value of the return oil flow meter (134) is 0, it can be determined that the on / off performance of the proportional speed control valve (606) under test at 0% opening is normal. Step 3) Operate the proportional speed control valve (606) from 0% to 100% gradually, observe the value and curve change of the return oil flow meter (134) on the data monitoring system, and judge the linear change characteristic of the flow of the proportional speed control valve (606) under test. Step 4) Operate the proportional speed control valve (606) in the operation control system to the opening value of X, and adjust the oil pump displacement of the motor oil pump assembly from small to large. Observe the value changes of the oil pump output flow meter (110) and hydraulic station pressure sensor (109) on the data monitoring system. The data monitoring system displays the pressure / flow characteristic curve of the tested proportional speed control valve (606) at the opening value X. Step 5) Install the proportional speed control valve 2 (814) to be tested on the vibration simulation control valve block (801), open ball valve 1 (117), ball valve 4 (802), ball valve 7 (809), and ball valve 8 (810), and keep all other ball valves of the hydraulic device closed; Step 6) Start the motor oil pump assembly and oil cooling device (114) through the operation control system, operate the electromagnetic overflow valve (106) to be energized, adjust the pressure of the electromagnetic overflow valve (106) to M, adjust the oil pump displacement of the motor oil pump assembly to N, give the proportional speed control valve (814) to a certain opening degree through the operation control system, operate the electromagnetic reversing valve (811) to be energized through the operation control system, and the servo cylinder (903) performs extension and retraction actions according to the given control signal. The displacement sensor (908) feeds back the motion parameters of the single piston double piston rod assembly (907) to the electrical control cabinet (11) through the signal cable and Ethernet. The dynamic performance of the proportional speed control valve (814) can be tested and judged by the oil pump output flow meter (110), the opening degree of the proportional speed control valve (814), and the feedback data of the displacement sensor (908).

12. A method for testing and simulating the vibration of hydraulic valve components using a hydraulic device according to claim 7, comprising the following steps: Step 1) Before performing fault diagnosis and performance testing of the pressure reducing valve, install the pressure reducing valve 2 (707) to be tested on the pressure reducing valve test valve block (701), open the inlet ball valve 5 (702) and the return ball valve 5 (703), and keep all other ball valves of the hydraulic device closed; Step 2) Start the motor oil pump assembly and oil cooling device (114) through the operation control system and PLC controller, operate the electromagnetic overflow valve (106) to be energized, adjust the pressure of the electromagnetic overflow valve (106) to M, adjust the oil pump displacement of the motor oil pump assembly to N, adjust the opening of the throttle valve (708), observe the value change of the return oil flow meter (134) on the data monitoring system, when the value of the return oil flow meter (134) is less than XL / min, stop adjusting the throttle valve (708), adjust the pressure reducing valve (707) under test, observe the value change of the pressure sensor (709) on the data monitoring system, when the value of the pressure sensor (709) is J, stop adjusting the pressure reducing valve (707) under test, at this time the pressure reducing valve (707) under test has completed the rapid parameter setting; Step 3) Continue to increase the opening of throttle valve five (708), and observe the changes in the values ​​of the main inlet pressure sensor (135), pressure sensor five (709), and return flow meter (134) on the data monitoring system. The data monitoring system displays the curve of the difference between the main inlet pressure sensor (135) and pressure sensor five (709) versus the change in the return flow meter (134), which is the pressure difference / flow characteristic curve of the pressure reducing valve two (707) under the set value state when simulating load change. Step 4) Adjust the opening of throttle valve five (708) to the maximum value, and adjust the oil pump displacement of the motor oil pump assembly from small to large. Observe the value changes of the main inlet oil pressure sensor (135), pressure sensor five (709), and oil pump output flow meter (110) on the data monitoring system. The data monitoring system displays the curve of the difference between the main inlet oil pressure sensor (135) and pressure sensor five (709) and the change of the oil pump output flow meter (110), which is the no-load pressure difference / flow characteristic curve of the pressure reducing valve two (707) under test when the setting parameter is J.

13. A method for testing and simulating the vibration of hydraulic valve components using a hydraulic device according to claim 6, comprising the following steps: Step 1) Before performing vibration simulation, open ball valve 1 (117), ball valve 2 (118), ball valve 3 (132), ball valve 5 (807), and ball valve 6 (808), while keeping all other ball valves and throttle valves of the hydraulic device closed; Step 2) Start the motor oil pump assembly and oil cooling device (114) through the operation control system and PLC controller, operate the electromagnetic overflow valve (106) to be energized, adjust the pressure of the electromagnetic overflow valve (106) to M, and adjust the oil pump displacement of the motor oil pump assembly to N; output any given vibration waveform spectrum signal to the motion controller through the operation control system and PLC controller, and the motion controller outputs the vibration waveform spectrum signal to the high frequency servo valve (120), and the high frequency servo valve (120) controls the servo cylinder (903) to perform vibration simulation action; Step 3) The motion parameters of the single-piston double-piston rod assembly (907) are fed back to the motion controller via signal cable and Ethernet by the displacement sensor (908) and the acceleration sensor (911). The motion controller performs PID adjustment based on the target position of the vibration waveform spectrum signal and the feedback data of the displacement sensor (908) and the acceleration sensor (911) to form closed-loop control and realize accurate simulation of the given vibration waveform spectrum signal. Step 4) The parameters of any given vibration waveform spectrum signal can be modified on the data monitoring system, and then the modified vibration waveform spectrum signal is output to the high-frequency servo valve (120). The high-frequency servo valve (120) controls the servo cylinder (903) to perform signal simulation action. At the same time, the data monitoring system displays the comparison curve between the vibration simulation displacement waveform spectrum of the servo cylinder (903) fed back by the displacement sensor (908) and the given vibration waveform spectrum signal. Step 5) When the high-frequency servo valve (120) is replaced with the faulty valve, the data monitoring system displays a comparison curve between the vibration simulation displacement waveform spectrum of the servo cylinder (903) fed back by the displacement sensor (908) and the given vibration waveform spectrum signal. Based on the comparison curve, the control performance of the tested high-frequency servo valve (120) can be accurately determined.

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