A dynamic simulation test method and system for cycle life of a pressure reducing valve

Abstract

The application provides a dynamic simulation test method and system for the cycle life of a pressure reducing valve, and relates to the technical field of valve performance testing. The method comprises the following steps: installing the measured pressure reducing valve in a test pipeline, opening the inlet side valve and the outlet side pressure relief valve, manually adjusting the inlet pressure regulator to make the inlet pressure of the measured pressure reducing valve reach the maximum rated inlet air pressure, obtaining the measured pressure reducing valve with the set inlet pressure; on the basis of the measured pressure reducing valve with the set inlet pressure, adjusting the measured pressure reducing valve itself to make the outlet pressure reach the maximum rated outlet air pressure, obtaining the measured pressure reducing valve with the rated values of the inlet pressure and the outlet pressure; extracting the fluid-structure coupling geometric topology features and the real-time pressure gradient field of the measured pressure reducing valve with the rated values of the inlet pressure and the outlet pressure, and constructing a three-dimensional space discretization grid model. The application improves the test efficiency and reduces the test equipment investment of enterprises.

Description

Technical Field

[0001] This invention relates to the field of valve performance testing technology, and in particular to a dynamic simulation test method and system for the cycle life of a pressure reducing valve. Background Technology

[0002] Pressure reducing valves are core pressure regulating components in industrial fluid pipelines, gas transmission and distribution, and hydraulic equipment. Their cyclic service life directly determines the operational safety and stability of the entire system. Therefore, cyclic life testing has become an indispensable core process in the research and development, design, quality control, and type testing of pressure reducing valve products. Currently, the industry mostly refers to the relevant national standards for pressure reducing valve performance testing and relies on traditional static pressure holding test benches or semi-automatic cyclic testing devices. These devices mainly focus on static pressure holding and sealing tests and simple opening and closing cycle tests with fixed parameters. They cannot accurately reproduce the dynamic load changes in the actual working conditions of pressure reducing valves and have defects such as insufficient test accuracy, low degree of automation, single working condition simulation, and poor versatility.

[0003] For example, a domestic manufacturer of high-pressure industrial pressure reducing valves used a semi-automated static pressure life test bench, which is common in the industry, to conduct type testing on its mass-produced piston-type high-pressure gas pressure reducing valves. This bench could only manually preset fixed valve opening and closing cycles and conduct pressure holding cycle tests at constant pressure. Throughout the process, manual recording of the static average outlet pressure was required. It could not capture dynamic parameters such as pressure overshoot and flow mutation at the moment of valve core opening and closing, nor could it simulate the actual working conditions of pipeline pressure fluctuations and frequent flow changes. Ultimately, the product was deemed to meet the cycle life standard. However, after the product was put into use, it experienced pressure drift and seal leakage failures after running far fewer cycles than the test standard. This showed a huge deviation from the laboratory conclusion, revealing that the existing technology could not reproduce the alternating load impact and performance degradation process of the pressure reducing valve in actual service, and it was difficult to continuously collect and analyze dynamic parameters in real time. The test results were seriously inconsistent with the actual service life. At the same time, the single pipeline design had poor adaptability, which increased the company's R&D and testing costs. Summary of the Invention

[0004] This invention provides a dynamic simulation test method and system for the cycle life of pressure reducing valves, which improves testing efficiency and reduces the investment in testing equipment for enterprises.

[0005] To solve the above-mentioned technical problems, the technical solution of the present invention is as follows: Firstly, a dynamic simulation test method for the cycle life of a pressure reducing valve, the method comprising: Install the pressure reducing valve under test in the test pipeline, open the inlet valve and the outlet pressure relief valve, manually adjust the inlet pressure regulator to make the inlet pressure of the pressure reducing valve under test reach the maximum rated inlet pressure, and obtain the pressure reducing valve under test with the set inlet pressure. Based on the pressure reducing valve under test with the inlet pressure already set, adjust the pressure reducing valve itself so that the outlet pressure reaches the maximum rated outlet pressure, thus obtaining a pressure reducing valve under test with both inlet and outlet pressures reaching the rated values. Extract the fluid-structure interaction geometric topology features and real-time pressure gradient field of the pressure reducing valve under test, where both inlet and outlet pressures reach the rated values, and construct a three-dimensional spatial discretized mesh model. Based on the spatial topological constraints of the three-dimensional spatial discretized geometric model, multi-parameter inverse calculations are performed on the alternating load transfer trajectory between models, the material micro-fatigue damage evolution boundary, and the nonlinear fluid-structure coupling constitutive response to obtain the final opening and closing phase reference and dynamic pressure compensation coefficient. Substitute the final opening and closing phase reference and the dynamic pressure compensation coefficient into the cyclic working condition mapping matrix to obtain the set automatic cyclic control parameters; according to the automatic cyclic control parameters, automatically control the inlet side valve to open and close repeatedly and the outlet side pressure relief valve to open and close synchronously in reverse, simulate the load cyclic action of the pressure reducing valve under test, record the number of cycles, and obtain real-time cycle number data. When the real-time cycle count data reaches the preset cycle count threshold, the inlet valve is automatically closed and the outlet pressure relief valve is opened to relieve pressure on the test pipeline and the pressure reducing valve under test, thus completing the cycle endurance test.

[0006] Secondly, a dynamic simulation test system for the cycle life of a pressure reducing valve includes: The acquisition module is used to install the pressure reducing valve under test in the test pipeline, open the inlet valve and the outlet pressure relief valve, manually adjust the inlet pressure regulator to make the inlet pressure of the pressure reducing valve under test reach the maximum rated inlet pressure, and obtain the pressure reducing valve under test with the set inlet pressure. The adjustment module is used to adjust the pressure reducing valve under test based on the pre-set inlet pressure, so that the outlet pressure reaches the maximum rated outlet pressure, thus obtaining a pressure reducing valve under test where both the inlet pressure and the outlet pressure reach the rated values. The module is used to extract the fluid-structure interaction geometric topology features and real-time pressure gradient field of the pressure reducing valve under test, where both the inlet and outlet pressures have reached the rated values, and to construct a three-dimensional spatial discretized mesh model. The calculation module is used to perform multi-parameter inverse calculations on the alternating load transfer trajectory between models, the material micro-fatigue damage evolution boundary, and the nonlinear fluid-structure interaction constitutive response based on the spatial topological constraint relationship of the three-dimensional spatial discretized geometric model, so as to obtain the final opening and closing phase reference and dynamic pressure compensation coefficient. The control module is used to substitute the final opening and closing phase reference and the dynamic pressure compensation coefficient into the cyclic working condition mapping matrix to obtain the set automatic cyclic control parameters; according to the automatic cyclic control parameters, the inlet side valve is automatically controlled to open and close repeatedly, and the outlet side pressure relief valve is opened and closed synchronously in reverse to simulate the load cyclic action of the pressure reducing valve under test, record the number of cycles, and obtain real-time cycle number data. The processing module is used to automatically close the inlet valve and open the outlet pressure relief valve when the real-time cycle count data reaches the preset cycle count threshold, so as to relieve pressure on the test pipeline and the pressure reducing valve under test and complete the cycle endurance test.

[0007] Thirdly, a computing device includes: One or more processors; A storage device for storing one or more programs that, when executed by one or more processors, cause the one or more processors to implement the method.

[0008] Fourthly, a computer-readable storage medium storing a program that, when executed by a processor, implements the method.

[0009] The above-described solution of the present invention has at least the following beneficial effects: Because it employs a method that first precisely calibrates the rated pressure at the inlet and outlet of the pressure-reducing valve under test, then extracts the fluid-structure interaction geometric topology features of the valve and real-time pressure gradient field to construct a three-dimensional spatial discretized mesh model, and obtains the opening and closing phase reference and dynamic pressure compensation coefficient adapted to the characteristics of the valve under test through multi-parameter inverse calculation, and then obtains the automatic cyclic control parameters through cyclic operating condition mapping matrix calculation, it ultimately achieves a full-process testing technique that enables synchronous reverse opening and closing cyclic control of the inlet-side valve and the outlet-side pressure relief valve, real-time recording of the number of cycles, and automatic pressure relief shutdown. Therefore, it overcomes the limitations of existing technologies that cannot reproduce the alternating load impact and material fatigue under nonlinear fluid-structure interaction during the actual service process of pressure-reducing valves. The core technical problems of the inability to accurately match valve opening and closing control parameters to the actual working conditions during the wear and performance degradation process, the inability of static pressure holding tests and simple fixed parameter cyclic tests to reproduce real dynamic working conditions, large deviations between test results and actual service life, and insufficient precise control capability of dynamic parameters are addressed. This research achieves high-precision dynamic simulation of real working conditions during the cyclic life test of pressure reducing valves, ensuring a high degree of matching between cyclic control parameters and the actual service conditions of the pressure reducing valve under test. It can accurately capture the dynamic performance changes of the valve during the cycle, improving the accuracy, reliability, and repeatability of the pressure reducing valve cyclic life test results. Simultaneously, it realizes fully automated closed-loop control of the testing process, improving testing efficiency. Attached Figure Description

[0010] Figure 1This is a flowchart illustrating a dynamic simulation test method for the cycle life of a pressure reducing valve provided in an embodiment of the present invention.

[0011] Figure 2 This is a schematic diagram of a dynamic simulation test system for the cycle life of a pressure reducing valve provided in an embodiment of the present invention.

[0012] Figure 3 This is a schematic diagram of the outlet pressure waveform before optimization.

[0013] Figure 4 This is a schematic diagram of the optimized outlet pressure waveform.

[0014] Figure 5 This is a schematic diagram of the stress-time curve for automated cyclic testing.

[0015] Figure 6 This is a schematic diagram of the pressure-time curve during the gradient depressurization process. Detailed Implementation

[0016] Exemplary embodiments of the present disclosure will now be described in more detail with reference to the accompanying drawings. While exemplary embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.

[0017] like Figure 1 As shown, an embodiment of the present invention proposes a dynamic simulation test method for the cycle life of a pressure reducing valve, the method comprising the following steps: Step 1: Install the pressure reducing valve under test in the test pipeline, open the inlet valve and the outlet pressure relief valve, manually adjust the inlet pressure regulator to make the inlet pressure of the pressure reducing valve under test reach the maximum rated inlet pressure, and obtain the pressure reducing valve under test with the set inlet pressure. Step 2: Based on the pressure reducing valve under test with the inlet pressure already set, adjust the pressure reducing valve itself so that the outlet pressure reaches the maximum rated outlet pressure, thus obtaining a pressure reducing valve under test with both inlet and outlet pressures reaching the rated values. Step 3: Extract the fluid-structure interaction geometric topology features and real-time pressure gradient field of the pressure reducing valve under test, where both inlet and outlet pressures have reached the rated values, and construct a three-dimensional spatial discretized mesh model. Step 4: Based on the spatial topological constraint relationship of the three-dimensional spatial discretized geometric model, perform multi-parameter inverse calculation on the alternating load transfer trajectory between models, the material micro-fatigue damage evolution boundary and the nonlinear fluid-structure coupling constitutive response to obtain the final opening and closing phase reference and dynamic pressure compensation coefficient. Step 5: Substitute the final opening and closing phase reference and dynamic pressure compensation coefficient into the cyclic working condition mapping matrix to obtain the set automatic cyclic control parameters; according to the automatic cyclic control parameters, automatically control the inlet side valve to open and close repeatedly and the outlet side pressure relief valve to open and close synchronously in reverse, simulate the load cyclic action of the pressure reducing valve under test, record the number of cycles, and obtain real-time cycle number data. Step 6: When the real-time cycle count data reaches the preset cycle count threshold, the inlet valve is automatically closed and the outlet pressure relief valve is opened to relieve pressure on the test pipeline and the pressure reducing valve under test, thus completing the cycle endurance test.

[0018] In this embodiment of the invention, a standardized calibration of the rated pressure at the inlet and outlet of the pressure-reducing valve under test is first performed. Then, the fluid-structure interaction geometric topology features of the pressure-reducing valve under test are extracted, and a three-dimensional spatial discretized mesh model is constructed using the real-time pressure gradient field. Based on the topological constraints of the model space, multi-parameter inverse calculations are performed on the alternating load transfer trajectory, the material micro-fatigue damage evolution boundary, and the nonlinear fluid-structure interaction constitutive response. This yields an opening and closing phase reference and dynamic pressure compensation coefficient adapted to the characteristics of the valve under test. Customized automatic cyclic control parameters are then obtained through cyclic condition mapping matrix calculation. Finally, a closed-loop test technique is achieved, which simulates the load-bearing cyclic action of synchronous reverse opening and closing of the inlet valve and the outlet pressure relief valve, records the number of cycles in real time, and automatically stops and relieves pressure after reaching a preset threshold. Therefore, this technique overcomes the limitations of existing technologies that can only perform static pressure holding tests with fixed parameters or simple opening and closing cyclic tests, and cannot reproduce the actual operation of the pressure-reducing valve. The alternating load impact and nonlinear fluid-structure interaction during actual service life lead to material fatigue and performance degradation processes. However, the inability to customize cyclic control parameters for the specific characteristics of the valve under test results in a severe disconnect between test conditions and actual service scenarios, resulting in significant discrepancies between test results and the actual service life of the product. Furthermore, the core technical challenges include insufficient dynamic performance capture capabilities and low levels of automated closed-loop control in the testing process. This research addresses these issues by achieving dynamic simulation of cyclic lifespan that is highly compatible with the structural characteristics and actual service conditions of the pressure reducing valve under test. It accurately reproduces the load changes and performance degradation processes during actual valve operation, improving the consistency between lifespan test results and the actual service life of the product. This enables automated closed-loop control of the entire testing process, reducing test errors caused by manual intervention and the workload of operators, thus improving testing efficiency. Ultimately, this provides precise and quantitative data support for the lifespan assessment, performance optimization, and quality control of pressure reducing valves.

[0019] In a preferred embodiment of the present invention, step 1 above may include: Step 11: Rigidly seal the outlet end of the pressure reducing valve under test to the outlet branch pipe of the test pipeline. Based on the connection, construct a complete media flow test pipeline. This includes: completing the pre-installation preparations for the pressure reducing valve under test and the test pipeline; cleaning the sealing surfaces of the inlet and outlet flanges of the pressure reducing valve under test, removing oil, rust, and solid impurities from the sealing surfaces; checking the flatness of the sealing surfaces, and confirming that there are no scratches, pits, or deformation defects that would affect the sealing performance; preparing a metal sealing gasket that perfectly matches the inlet and outlet connection specifications of the pressure reducing valve under test; placing the gasket flat between the flange sealing surface of the outlet end of the pressure reducing valve under test and the flange sealing surface of the outlet branch pipe of the test pipeline; and adjusting the position of the gasket. The center of the valve and the center of the flange flow channel must be completely aligned without radial offset. Following the diagonal tightening procedure, tighten the flange bolts sequentially, maintaining a consistent torque in each tightening cycle. Complete the tightening of all bolts in at least three cycles. The final tightening torque should be set according to the nominal diameter and nominal pressure rating of the flange, ensuring a rigid, leak-free seal between the outlet of the pressure reducing valve and the outlet branch of the test pipeline. After completing the outlet seal, use the same sealing procedure to rigidly seal the inlet of the pressure reducing valve to the inlet branch of the test pipeline, ensuring the pressure reducing valve is fully connected to the main flow path of the test pipeline. After all connections are completed, check the installation status of all associated valves, sensors, and connectors on the test pipeline, confirming that all components are fixed and sealed according to design requirements, with no loosening or misalignment. This constitutes a complete, leak-free media flow test pipeline.

[0020] Step 12: Based on the complete media flow test pipeline, send synchronous opening commands to the actuators of the inlet valve and the outlet pressure relief valve, switching the inlet valve to the fully open conduction state and the outlet pressure relief valve to the fully open venting state, establishing the initial media flow path. Specifically, this includes: after confirming the integrity and sealing of the media flow test pipeline, completing the power-on initialization operation, performing a communication self-test on the actuators of the inlet valve and the outlet pressure relief valve to confirm that the signal transmission link between the actuators is completely normal and there are no communication interruptions or signal abnormalities, and simultaneously confirming that both the inlet valve and the outlet pressure relief valve are in the initial closed state; after the self-test is completed, through the internally preset timing synchronization control logic, send synchronous opening commands to the actuators of the inlet valve and the outlet pressure relief valve simultaneously, with the time difference between the two commands not exceeding 1 millisecond, ensuring that the drive signals of the two valves remain completely synchronized. After receiving the opening command, the actuator of the inlet-side valve drives the valve core to complete its full opening stroke until it is completely disengaged from the valve seat flow channel. This switches the inlet-side valve to the fully open conduction state, where the flow channel area reaches its design maximum value and there is no throttling obstruction. Similarly, after receiving the synchronous opening command, the actuator of the outlet-side pressure relief valve drives the valve core to complete its full opening stroke until it is completely disengaged from the valve seat flow channel. This switches the outlet-side pressure relief valve to the fully open venting state, where the venting flow channel is fully open and there is no throttling obstruction. After both valves have completed their full opening, the signal from the valve's built-in position feedback sensor is collected to confirm that both valves are stably in the fully open state. At this point, a continuous and unobstructed initial medium flow path is formed in the test pipeline from the upstream gas source interface, the inlet-side valve, the pressure reducing valve under test, the outlet-side pressure relief valve, to the downstream vent, completing the establishment of the initial flow path.

[0021] Step 13: Based on the initial medium flow path, gradually rotate the pressure regulating handwheel of the inlet pressure regulator counterclockwise to continuously increase the throttling opening of the upstream gas source medium, and collect the pressure feedback signal of the inlet side pipeline in real time. Specifically, this includes confirming that the initial medium flow path has been stably established, the upstream high-pressure gas source is in normal gas supply condition, and the gas source output pressure is higher than the maximum rated inlet pressure of the pressure reducing valve under test. The operator gradually rotates the pressure regulating handwheel of the inlet pressure regulator counterclockwise according to the preset adjustment direction. Each rotation angle does not exceed 15 degrees. After each rotation operation, the handwheel position is held stable for at least 3 seconds to allow the throttling valve core inside the inlet pressure regulator to complete the position adjustment and the medium pressure in the test pipeline to complete a stable transition. As the operator gradually rotates the pressure regulating handwheel, the throttle valve core inside the inlet pressure regulator undergoes axial displacement synchronously with the handwheel's rotation. This continuously increases the flow area of ​​the throttle valve orifice, allowing the high-pressure medium from the upstream gas source to enter the inlet side pipeline of the test line through the ever-expanding throttle valve orifice, causing the medium pressure within the inlet side pipeline to gradually rise. Throughout the entire pressure regulation process, a high-precision pressure sensor installed on the inlet side pipeline of the pressure reducing valve under test continuously collects real-time values ​​of the medium pressure within the inlet side pipeline at a sampling frequency of no less than 1000 Hz, generating a continuous pressure feedback signal.

[0022] Step 14: Compare the real-time value of the pressure feedback signal with the maximum rated intake pressure using dynamic deviation. When the pressure feedback signal rises to the maximum rated intake pressure and the pressure fluctuation amplitude converges within the preset steady-state tolerance range, stop rotating the pressure adjustment handwheel and lock the current throttling opening. Based on the locked state, obtain the pressure reducing valve with the set inlet pressure. Specifically, this includes: acquiring the real-time value of the inlet-side pipeline pressure corresponding to the pressure feedback signal, and performing a dynamic deviation comparison calculation between this real-time value and the pre-recorded maximum rated intake pressure of the pressure reducing valve under test. During the pressure adjustment process, continuously perform statistical calculations on the continuously collected real-time pressure values, calculate the difference between the maximum and minimum pressure values ​​within the preset sliding time window, and obtain the pressure fluctuation amplitude. The sliding time window is set to 5 seconds. When it is determined that the real-time value of the inlet-side pipeline pressure rises to be completely consistent with the maximum rated intake pressure, and the calculated pressure fluctuation amplitude converges within the preset steady-state tolerance range, issue a prompt signal indicating that the adjustment is complete to the operator through the matching audible and visual prompt device. The preset steady-state tolerance range is set to be no greater than 0.02 MPa. Upon receiving the prompt signal, the operator immediately stops rotating the pressure regulating handwheel of the inlet pressure regulator counterclockwise, keeping the handwheel in its current position. Then, the operator rotates the locking mechanism on the inlet pressure regulator handwheel to rigidly lock it to the regulator valve body, completely fixing the position of the throttling valve core inside the inlet pressure regulator and locking the current throttling opening. This ensures that the flow area of ​​the throttling valve orifice will not shift during subsequent testing. After locking the throttling opening, the operator continuously collects the inlet-side pipeline pressure feedback signal for 30 seconds to confirm that the locked inlet pressure value remains stable and the pressure fluctuation amplitude remains within the preset steady-state tolerance range. This completes the precise setting of the inlet pressure of the pressure reducing valve under test, resulting in the pressure reducing valve with the set inlet pressure.

[0023] In this embodiment of the invention, because a complete medium flow test pipeline is constructed by first rigidly sealing the outlet end of the pressure reducing valve under test with the outlet branch of the test pipeline, and then sending synchronous opening commands to the actuators of the inlet valve and the outlet pressure relief valve, the inlet valve is switched to the fully open conduction state and the outlet pressure relief valve is switched to the fully open venting state to establish an initial medium flow path, the pressure regulating handwheel of the inlet pressure regulator is gradually rotated counterclockwise to control the throttling opening of the upstream gas source medium to continuously increase, and the pressure feedback signal of the inlet pipeline network is collected in real time. Finally, the real-time value of the pressure feedback signal is dynamically compared with the maximum rated inlet pressure. When the pressure feedback signal climbs to the maximum rated inlet pressure and the pressure fluctuation amplitude converges within the preset steady-state tolerance range, the rotation of the pressure regulating handwheel is stopped and the current throttling opening is locked. Therefore, the full-process inlet pressure precise calibration technology is effective. This invention overcomes the technical problems in existing technologies, such as unreliable sealing of the pressure reducing valve under test leading to media leakage, non-standard establishment of the test pipeline flow path, lack of real-time closed-loop feedback during inlet pressure regulation, insufficient pressure calibration accuracy, and instability of the inlet pressure reference due to the lack of convergence control of pressure fluctuation amplitude. These problems lead to distortion of subsequent cycle life test data and poor repeatability and consistency of test results. The invention achieves highly reliable sealing installation of the pressure reducing valve under test and standardized construction of the test pipeline, ensuring the stable establishment of the initial media flow path. It also achieves accurate, stable calibration and reliable locking of the maximum rated inlet pressure of the pressure reducing valve under test, ensuring the accuracy and steady-state of the inlet pressure reference before cycle life testing, eliminating the interference of inlet pressure fluctuations on the subsequent testing process, and improving the consistency of the test reference, the stability of the testing process, and the reliability and repeatability of the test results.

[0024] In a preferred embodiment of the present invention, step 2 above may include: Step 21: Based on the pressure reducing valve under test with the set inlet pressure, keep the current throttling opening of the inlet pressure regulator in a physically locked state, and send a closing command to the actuator of the outlet pressure relief valve to cut off the outlet venting passage, so that the test tube route changes from an open flow condition to a closed pressure condition. Specifically, this includes: completing the pre-state verification. For the pressure reducing valve under test with the set inlet pressure, first check the locking mechanism of the inlet pressure regulator to confirm that the locking mechanism is in a fully locked state, the pressure regulating handwheel of the inlet pressure regulator cannot rotate circumferentially, the position of the throttling valve core inside the inlet pressure regulator is completely fixed, the current throttling opening remains stable, and there is no loosening or displacement. Simultaneously, a high-precision pressure sensor installed on the inlet side pipeline continuously collects real-time pressure values ​​of the inlet side pipeline network for at least 10 seconds to confirm that the collected pressure values ​​remain stable at the maximum rated inlet pressure of the pressure reducing valve under test, with pressure fluctuation amplitude not exceeding 0.02 MPa. This confirms that the current throttling opening of the inlet pressure regulator is in a stable physical locked state. After completing the state verification, a closing command is sent to the actuator of the outlet side pressure relief valve. During the command transmission process, the signal transmission stability is maintained, and the command transmission time does not exceed 2 milliseconds. After receiving the closing command, the actuator of the outlet-side pressure relief valve drives the valve core to complete the full-close stroke until the valve core and the valve seat sealing surface are completely pressed together, cutting off the outlet-side venting passage and ensuring that there is no medium leakage in the venting passage. After the outlet-side pressure relief valve completes the closing action, the signal from the valve's built-in position feedback sensor is collected to confirm that the valve is stably in a fully closed and sealed state. At this time, the downstream venting passage of the test pipeline is completely cut off, and the pipeline smoothly transitions from the previous open flow condition to a closed pressure condition. The medium pressure inside the pipeline is in an adjustable closed pressure environment.

[0025] Step 22: Based on the closed pressure condition, rotate the preload adjusting screw on top of the pressure-reducing valve under test axially. This changes the compression of the internal return spring, thereby driving the valve core to generate axial displacement to reconstruct the initial throttling clearance at the valve seat. Specifically, after confirming that the test pipeline is stably under closed pressure, the operator first checks the anti-loosening positioning mechanism of the preload adjusting screw on top of the pressure-reducing valve under test, confirming that the anti-loosening positioning mechanism is fully loosened and the preload adjusting screw can be freely rotated axially. The operator then rotates the preload adjusting screw clockwise along the axial direction according to the preset adjustment direction. Each rotation angle does not exceed 10 degrees. After each rotation operation, the screw is held in its current position for at least 5 seconds to allow the return spring inside the pressure-reducing valve under test to complete the stable adjustment of its compression, and the valve core to complete the smooth transition of its position. As the operator gradually rotates the preload adjusting screw, the lower end face of the screw remains in continuous contact with the upper support of the return spring. The axial rotation of the screw is converted into a downward axial thrust, causing the compression of the return spring to increase continuously. The elastic preload generated by the return spring is simultaneously and continuously increased. The increased elastic preload is transmitted to the upper end face of the valve core through the lower support of the spring, causing the valve core to move downward along the axial guide structure of the valve body. The relative position between the sealing surface at the lower end of the valve core and the valve seat changes continuously, thereby reconstructing the initial throttling gap at the valve seat. The flow area of ​​the throttling gap changes accordingly with the axial displacement of the valve core, thus controlling the pressure drop of the medium in the pipeline.

[0026] Step 23: Based on the reconstructed initial throttling gap, track the pressure response rise curve of the outlet-side pipeline in real time. Match the real-time slope of the pressure response rise curve with the target pressure approach rate to evaluate the suppression effect of the current throttling gap on the medium pressure drop. Specifically, after the initial throttling gap at the valve seat of the pressure reducing valve under test is reconstructed, a high-precision pressure sensor installed on the outlet-side pipeline of the pressure reducing valve under test continuously collects the real-time values ​​of the medium pressure in the outlet-side pipeline at a sampling frequency of not less than 2000 Hz, generating continuous pressure time-series data. Based on the collected pressure time-series data, plot the pressure response rise curve of the outlet-side pipeline in real time. The horizontal axis of the pressure response rise curve is the sampling time, and the vertical axis is the real-time value of the outlet-side pipeline pressure at the corresponding time. Based on the continuous data of the pressure response rise curve, calculate the real-time slope of the curve in real time. The formula used in the calculation process is: ; in This represents the real-time slope of the pressure response ramp-up curve. This represents the outlet-side pipeline pressure value at the current sampling time. This represents the outlet-side pipeline pressure value at the previous sampling time. This is the time value corresponding to the current sampling moment. The time value corresponding to the previous sampling moment is used as the reference. A target pressure approach rate is preset, which is set to 0.01 MPa per second. During the adjustment process, the real-time slope of the calculated pressure response rise curve is matched and judged in real time with the preset target pressure approach rate. When the real-time slope is greater than the target pressure approach rate, it is determined that the flow area of ​​the current throttling gap is too large, the suppression effect on the medium pressure drop is insufficient, the outlet pressure rise rate is too fast, and pressure overshoot is likely to occur. When the real-time slope is less than the target pressure approach rate, it is determined that the flow area of ​​the current throttling gap is too small, the suppression effect on the medium pressure drop is too strong, the outlet pressure rise rate is too slow, and the adjustment efficiency is insufficient. When the difference between the real-time slope and the target pressure approach rate is within the preset allowable deviation range, it is determined that the suppression effect of the current throttling gap on the medium pressure drop meets the adjustment requirements, and subsequent pressure stabilization adjustment is allowed to continue. The preset allowable deviation range is set to ±0.002 MPa per second.

[0027] Step 24: When the terminal value of the pressure response climb curve stabilizes at the maximum rated outlet pressure, and the pressure feedback signal of the inlet side pipeline network is verified to have no attenuation shift, stop rotating the preload adjusting screw and lock the anti-loosening positioning mechanism. Based on the locked state, confirm that the pressure reducing valve under test has reached the rated values ​​for both inlet and outlet pressures. Specifically, this includes: during the pressure adjustment process, continuously monitoring the terminal value of the pressure response climb curve in real time. The terminal value is the stable value of the outlet side pipeline network pressure at the current moment. At the same time, continuously collecting the pressure feedback signal of the inlet side pipeline network for synchronous verification. When it is determined that the terminal value of the pressure response climb curve climbs to the maximum rated outlet pressure of the pressure reducing valve under test, and the continuous collection time is not less than 30 seconds, the fluctuation amplitude of the outlet side pipeline network pressure does not exceed 0.02 MPa, and the pressure value remains stable at the maximum rated outlet pressure, start the inlet side pressure synchronous verification process. During the inlet side pressure synchronous verification process, collect the pressure feedback signal of the inlet side pipeline network within the same time period, and calculate the attenuation shift of the inlet pressure. The formula used in the calculation process is: ; in, This is the offset of the inlet pressure attenuation. To verify the real-time average pressure of the inlet-side pipeline network over a given period of time, The maximum rated inlet pressure of the pressure reducing valve under test is used. When the calculated inlet pressure attenuation offset is no greater than 0.02 MPa, it is determined that the pressure feedback signal of the inlet side pipeline has not experienced attenuation offset, and the inlet and outlet pressure references both meet the rated requirements. After completing the pressure stability judgment and synchronous verification, an audible and visual prompt signal is sent to the operator indicating that the adjustment is complete. Upon receiving the prompt signal, the operator immediately stops rotating the preload adjusting screw on the top of the pressure reducing valve under test, keeps the current axial position of the screw unchanged, and rotates the anti-loosening positioning mechanism matched with the preload adjusting screw to rigidly lock the preload adjusting screw to the valve body cover of the pressure reducing valve under test, completely restricting the circumferential and axial displacement of the preload adjusting screw, and ensuring that the compression of the return spring, the axial position of the valve core, and the throttling gap at the valve seat do not shift during the test. After the anti-loosening locking is completed, the inlet and outlet pressure data are continuously collected for 60 seconds to confirm that the inlet and outlet pressure values ​​are stable at the corresponding rated values ​​and the pressure fluctuation amplitude is always within the preset allowable range. This completes the dual calibration of the rated pressure of the inlet and outlet of the pressure reducing valve under test, confirming that the pressure reducing valve under test has reached the rated values ​​for both the inlet and outlet pressures.

[0028] In this embodiment of the invention, the physical locking state of the current throttling opening of the inlet pressure regulator is maintained first. A closing command is sent to the actuator of the outlet pressure relief valve to cut off the outlet venting passage, smoothly transitioning the test pipeline from an open flow condition to a closed pressure-bearing condition. Then, the pre-tightening screw at the top of the pressure-reducing valve under test is rotated axially. By changing the compression of the internal reset spring, the valve core is driven to generate axial displacement to reconstruct the initial throttling gap at the valve seat. Based on the reconstructed initial throttling gap, the pressure response rise curve of the outlet pipeline is tracked in real time. The real-time slope of the pressure response rise curve is matched with the target pressure approach rate to evaluate the suppression effect of the current throttling gap on the medium pressure drop. Finally, when the terminal value of the pressure response rise curve stabilizes at the maximum rated outlet pressure and the pressure feedback signal of the inlet pipeline is simultaneously verified to have no attenuation shift, the rotation of the pre-tightening screw is stopped. The technology employs a precise calibration method for the entire process of outlet pressure, including a locking and anti-loosening positioning mechanism. This overcomes the technical problems of existing technologies, such as the lack of dynamic process control during the outlet pressure adjustment of pressure reducing valves, the susceptibility to pressure overshoot or insufficient adjustment accuracy, the mismatch between the two pressure references due to the failure to simultaneously verify the stability of the inlet pressure, the pressure reference drift during testing due to the lack of reliable anti-loosening locking after adjustment, and pipeline pressure shocks and poor consistency of test references caused by improper switching of operating conditions. These issues lead to pressure reference distortion and large deviations between test results and actual performance during cycle life testing. This technology achieves smooth and shock-free switching of test pipeline operating conditions, enabling precise, stable calibration and reliable locking of the maximum rated outlet pressure of the pressure reducing valve under test. It also ensures the stability, consistency, and matching of the rated pressure references at the inlet and outlet, effectively eliminating the interference of pressure overshoot, reference drift, and inlet pressure attenuation on the testing process.

[0029] In a preferred embodiment of the present invention, step 3 above may include: Step 31: Based on the pressure reducing valve under test where both inlet and outlet pressures have reached their rated values, the multi-sensor synchronous sampling interface is called to obtain the contour coordinates of the internal flow channel and the key pressure-bearing wall thickness. Through spatial surface fitting and feature dimensionality reduction, the fluid-structure interaction geometric topology features characterizing the interface between the fluid medium flow path and the solid structure are extracted. Specifically, this includes: completing the pre-condition verification; for the pressure reducing valve under test where both inlet and outlet pressures have reached their rated values, real-time inlet and outlet pressure data are continuously collected for 60 seconds to confirm that the fluctuation amplitude of the inlet and outlet pressures does not exceed 0.02 MPa, the pressure reducing valve under test is in a stable steady-state operating condition, and the distribution of the medium flow field and the stress state of the solid structure inside the valve body remain stable over a long period of time. After verification, an industrial-grade 3D laser scanning device was used to perform a non-contact full-contact scan of the internal flow channels of the pressure reducing valve under test. The point cloud sampling accuracy of the scanning device was set to 0.01 mm, and the scanning step size along the medium flow direction was set to 0.05 mm. The device completely covered the entire inner wall surface of the valve body inlet flow channel, valve core throttling flow channel, valve cavity buffer flow channel, and valve body outlet flow channel, and collected the 3D spatial point cloud data of the inner wall surface of the flow channel, i.e., the contour coordinates of the internal flow channel of the valve body. Simultaneously, a high-precision ultrasonic thickness gauge was used to collect the wall thickness dimensions of the key pressure-bearing parts of the valve body. The key pressure-bearing parts include the valve body inlet flange connection section, the valve cavity pressure-bearing outer wall, the valve core pressure-bearing end face, the valve seat support section, and the valve body outlet flange connection section. At least 10 evenly distributed thickness measurement points were set for each pressure-bearing part. The measurement accuracy of the thickness gauge was set to 0.001 mm. At least 5 repeated measurements were performed for each point, and the arithmetic mean of the multiple measurement results was taken as the key pressure-bearing wall thickness dimension of that point. After completing the measurement of all points, the wall thickness dimension dataset of the key pressure-bearing parts of the pressure-reducing valve under test was obtained.

[0030] After completing the basic data acquisition, the three-dimensional point cloud data of the flow channel contour is imported into the data processing unit. First, the point cloud data is pre-processed to remove discrete noise and redundant data generated during the scanning process. Then, a non-uniform rational B-spline surface fitting method is used to fit the continuous spatial surface of the denoised flow channel inner wall point cloud data to restore the complete continuous wall geometric model of the flow channel inside the valve body. The fitted flow channel wall geometric model and the collected key pressure-bearing wall thickness data set are decoupled to separate the flow channel geometric features of the fluid medium flow and the wall thickness boundary features of the solid pressure-bearing structure. Non-critical geometric features unrelated to the fluid-structure interaction are removed, including the geometric features of the mounting boss and non-pressure-bearing auxiliary structures on the outside of the valve body, to complete the feature dimensionality reduction. Finally, from the dimensionality-reduced feature data, the continuous geometric features of the inner wall of the flow channel that completely represent the flow path of the fluid medium and the pressure-bearing wall boundary features that completely represent the interface between the solid structure and the fluid medium are extracted. The two types of features are integrated to obtain the fluid-structure interaction geometric topology features of the pressure-reducing valve under test.

[0031] Step 32: Utilizing the fluid-structure interaction geometric topology features, under steady-state operation of the test pipeline, piezoresistive pressure sensors are fixedly installed as pressure acquisition nodes at preset measurement points downstream of the valve body inlet flange, in the middle section of the valve core flow channel, and upstream of the outlet flange along the medium flow direction. Transient pressure time series sequences at each measurement point are synchronously acquired using the piezoresistive pressure sensors. Gradient tensor operations and spatial domain smoothing filtering are performed on the acquired transient pressure time series sequences to reconstruct a real-time pressure gradient field reflecting the local pressure drop rate and turbulent pulsation intensity. Specifically, this includes: utilizing the extracted fluid-structure interaction geometric topology features, determining the installation positions of the pressure measurement points on the valve body of the pressure reducing valve under test, and sequentially setting three fixed measurement points along the flow direction of the medium within the valve body. The first measurement point is located downstream of the valve body inlet flange at twice the nominal diameter of the flow channel; the second measurement point is located at the axial midpoint of the valve core flow channel, which is the transition position between the valve core throttling orifice and the valve cavity buffer flow channel; and the third measurement point is located upstream of the valve body outlet flange at twice the nominal diameter of the flow channel. At each preset measuring point, a mounting threaded hole matching the piezoresistive pressure sensor is machined. A pressure-sensing hole, communicating with the internal flow channel of the valve body, is opened at the bottom of the threaded hole. The diameter of the pressure-sensing hole smoothly transitions to the inner wall of the flow channel, without any throttling steps or vortex dead zones. A high-frequency response piezoresistive pressure sensor is fixedly installed in the mounting threaded hole at each measuring point. The sensor's measurement range covers the rated pressure range of the inlet and outlet of the pressure-reducing valve under test, with a measurement accuracy of no less than 0.1 class and a frequency response of no less than 50 kHz. The sensor's pressure-sensing end face is flush with the end of the pressure-sensing hole, ensuring accurate acquisition of the transient pressure of the medium within the flow channel. These three piezoresistive pressure sensors together constitute the pressure acquisition node.

[0032] After the sensor installation is completed, and the pressure reducing valve under test is confirmed to be in a stable steady-state operating condition, a synchronous sampling trigger signal is sent to the three piezoresistive pressure sensors via a synchronous trigger controller. The time synchronization error of the trigger signal does not exceed 1 microsecond, ensuring that the pressure acquisition actions at the three measuring points are completely synchronized. After receiving the synchronous trigger signal, the three piezoresistive pressure sensors synchronously acquire the transient pressure values ​​of the medium at their respective measuring points at a sampling frequency of not less than 20,000 Hz, generating a continuous transient pressure time series. The time series of each measuring point includes the corresponding sampling timestamp and the transient pressure value at the corresponding moment. The continuous acquisition time is not less than 10 complete steady-state cycles of medium flow, ensuring that the acquired time series can completely reflect the steady-state pressure distribution characteristics of the flow field within the valve body.

[0033] After acquiring the transient pressure time series data, the time series data from the three measuring points were preprocessed to remove abnormal jump data caused by electrical interference. Then, gradient tensor operations were performed on the preprocessed transient pressure time series. The formula used in the operation was: ; in, Let be the pressure gradient tensor at the measurement point. , , Transient pressure in a three-dimensional rectangular coordinate system , , Partial derivatives along the three axes, The shaft is positioned along the main flow direction of the medium. shaft and The shafts are respectively set along the radial and circumferential directions of the flow channel cross-section.

[0034] After completing the gradient tensor operation, the obtained pressure gradient tensor data is subjected to spatial domain smoothing filtering. A 5th-order moving average smoothing filtering algorithm is used to smooth and denoise the continuously distributed pressure gradient tensor data in the spatial domain, eliminate high-frequency noise interference caused by turbulent fluctuations, and retain the main distribution characteristics of the pressure gradient field. Finally, based on the spatial coordinates of the three measuring points and the smoothed pressure gradient tensor data, a real-time pressure gradient field that covers the entire flow channel region inside the valve body and accurately reflects the local pressure drop rate and turbulent fluctuation intensity at each position in the flow channel is reconstructed through spatial interpolation.

[0035] Step 33: Register the fluid-structure interaction (FSI) geometric topology features with the real-time pressure gradient field in a spatial coordinate system. Based on the registered composite field data, obtain a three-dimensional spatial discretized mesh model that matches the node topological connection relationship and the distribution density of local stress concentration areas. Specifically, this includes: receiving the extracted FSI geometric topology features and the reconstructed real-time pressure gradient field, and performing a spatial coordinate system registration operation. First, establish a unified global three-dimensional rectangular coordinate system. Set the origin of the coordinate system at the center of the end face of the inlet flange of the pressure reducing valve body under test. The x-axis of the coordinate system points to the outlet flange of the valve body along the mainstream flow direction of the medium. The y-axis and z-axis are set along the horizontal and vertical radial directions of the inlet flange cross-section, respectively, as the reference of the global coordinate system. Transform the flow channel wall geometry model and pressure-bearing wall thickness boundary features corresponding to the FSI geometric topology features to the global coordinate system to complete the coordinate reference unification of the geometry features. Transform the spatial interpolation mesh corresponding to the real-time pressure gradient field and the pressure gradient tensor data at each location to the same global coordinate system to ensure that the spatial position of the pressure gradient field completely corresponds to the spatial position of the FSI geometric topology features. After unifying the coordinate reference, the key feature points of the geometric features and the pressure gradient field are registered and verified. The key feature points include the center of the valve body inlet flange, the midpoint of the valve core flow channel, and the center of the valve body outlet flange. The coordinate deviation of the three key feature points in the geometric features and the pressure gradient field is verified to be no more than 0.01 mm. The registration accuracy is confirmed to meet the requirements, and the composite field data of the fluid-structure interaction geometric features and the pressure gradient field after registration is obtained.

[0036] Based on the registered composite field data, the region division operation before mesh generation is performed. According to the position of the fluid-structure interaction interface in the composite field data, two major computational regions are obtained: the fluid domain and the solid domain. The fluid domain is the flow channel region where the medium flows inside the valve body, and the solid domain is the solid region of the pressure-bearing structure such as the valve body, valve core, and valve seat. Mesh generation is performed separately for the fluid and solid domains. Boundary layer mesh refinement is applied to the near-wall region of the fluid domain, generating at least 10 boundary layer structured meshes along the normal direction of the flow channel wall. The thickness of the first boundary layer mesh is set to 0.02 mm, and the mesh growth rate is set to 1.2 to ensure the boundary layer mesh accurately captures the fluid viscosity effects and pressure gradient changes near the flow channel wall. Based on the pressure gradient distribution and local stress concentration areas in the composite field data, high stress gradient regions in the solid domain are identified. These high stress gradient regions include the contact sealing surface between the valve core and valve seat, the pressure-bearing angle of the valve cavity, the throttling end face of the valve core, and the inlet / outlet flange connection section. Local mesh refinement is performed on these high stress gradient regions, with the mesh size in the refined regions not exceeding 0.1 mm and the base mesh size in the unrefined regions not exceeding 0.5 mm.

[0037] After completing the regional mesh refinement settings, the volume element adaptive meshing algorithm is executed. Tetrahedral unstructured meshes are used to adaptively mesh the overall space of the fluid and solid domains. During the meshing process, the quality parameters of the mesh elements are verified in real time, including the aspect ratio, skewness, and Jacobian matrix determinant value, ensuring that the quality parameters of all mesh elements meet the accuracy requirements of numerical calculations. The aspect ratio of the mesh elements does not exceed 5, the skewness does not exceed 0.8, and the Jacobian matrix determinant value is not lower than 0.3. During the meshing process, the distribution density of mesh nodes is adjusted in real time according to the distribution density of local stress concentration areas in the composite field data. In areas with high local stress concentration density, the number of mesh nodes is increased and the size of the mesh elements is reduced. In areas with uniform stress distribution, the number of mesh nodes is appropriately reduced and the size of the mesh elements is increased. Finally, a three-dimensional spatial discretized mesh model is generated that perfectly matches the topological connection relationship of the mesh nodes with the distribution density of local stress concentration areas.

[0038] In this embodiment of the invention, a pressure-reducing valve is used, based on the assumption that both inlet and outlet pressures reach their rated values. A multi-sensor synchronous sampling interface is invoked to obtain the internal flow channel contour coordinates and key pressure-bearing wall thickness dimensions. After spatial surface fitting and feature reduction processing, fluid-structure interaction (FSI) geometric topological features characterizing the interface between the fluid medium flow path and the solid structure are extracted. Then, based on these FSI geometric topological features, piezoresistive pressure sensors are deployed as pressure acquisition nodes at preset measurement points downstream of the valve body inlet flange, in the middle section of the valve core flow channel, and upstream of the outlet flange, along the medium flow direction during steady-state operation of the test pipeline. Transient pressure time-series sequences at each measurement point are simultaneously acquired, and gradient tensor operations and spatial domain smoothing filtering are performed to reconstruct a real-time pressure gradient field reflecting the local pressure drop rate and turbulent fluctuation intensity. Finally, the FSI geometric topological features and the real-time pressure gradient field are registered in a spatial coordinate system. Based on the registered composite field data, boundary layer mesh refinement and volume element adaptive subdivision algorithms are executed to generate a three-dimensional spatial... The full-process digital modeling technique of the discretized mesh model overcomes the limitations of existing technologies, which cannot accurately characterize the geometric features of the fluid-structure interaction interface inside the pressure reducing valve and the spatial distribution characteristics of the fluid pressure field under actual operating conditions. These technologies struggle to accurately capture local pressure drop changes, turbulent pulsations, and structural stress concentration areas within the valve body. Furthermore, the constructed mesh model has a low degree of matching with the actual structure and flow field of the valve under test, failing to provide a precise and reliable model foundation for subsequent alternating load transfer and fatigue damage evolution analysis. This leads to core technical problems such as the disconnect between cyclic control parameters and actual service conditions, and significant deviations between life test results and actual product performance. The technique achieves the effect of accurately extracting the fluid-structure interaction geometric topology features of the pressure reducing valve under test, reconstructing a real-time pressure gradient field that highly matches the actual steady-state operating state, and generating a high-precision three-dimensional spatial discretized mesh model that highly matches the node topological connection relationships and the distribution density of local stress concentration areas. This fully restores the fluid flow characteristics and solid structure stress characteristics inside the valve under test.

[0039] In a preferred embodiment of the present invention, step 4 above may include: Step 41: Based on the spatial topological constraints of the three-dimensional discretized mesh model, establish a set of nodal force balance equations between mesh elements, inject periodic alternating pressure boundary conditions, simulate the load transmission process from fluid pulsation impact to the solid valve core and spring assembly, and track and output the alternating load transmission trajectory within each cycle. Specifically, this includes: verifying the validity of the three-dimensional discretized mesh model, confirming that the fluid-structure interaction interface nodes between the fluid and solid domains in the mesh model are completely corresponding, the node topological connection relationship conforms to the preset spatial topological constraints, and the mass parameters of all mesh elements meet the numerical calculation requirements, with no mesh distortion or node misalignment. After verification, based on the spatial topological constraints of the mesh model, establish a set of nodal force balance equations for all mesh elements in the solid domain. The equations are established with the force balance of each mesh node as the core, comprehensively considering the fluid pressure load on the node, the elastic stress of the solid structure, the preload of the spring assembly, and the inertial load during the valve core movement. The formula used in the calculation process is... ; in, The global stiffness matrix of the solid domain mesh model. Let be the nodal displacement vector. For the overall damping matrix, For the node velocity vector, For the overall quality matrix, For the nodal acceleration vector, The fluid pressure load vector. This is the preload vector of the spring assembly.

[0040] After establishing the nodal force balance equations, periodic alternating pressure boundary conditions are injected into the inlet boundary of the fluid domain mesh model. The alternating pressure variation period is set to 4 seconds, with a pressure rise phase lasting 2 seconds, during which the pressure linearly increases from 0 MPa to the maximum rated inlet pressure of the pressure reducing valve under test, and a pressure fall phase lasting 2 seconds, during which the pressure linearly decreases from the maximum rated inlet pressure back to 0 MPa, thus fully reproducing the fluid pressure pulsation changes during the valve opening and closing cycle. The injected periodic alternating pressure boundary conditions are used as load input terms and substituted into the nodal force balance equations. Numerical solutions are then performed using a transient dynamics solver to simulate the load transmission process from the pulsating pressure impact in the fluid domain through the fluid-structure interaction interface to the valve core, valve seat, valve body, and spring assembly in the solid domain during the valve opening and closing cycle. The time step of the solution process is set to 0.001 seconds to ensure accurate capture of the load transmission changes at every instant. During the numerical solution process, continuous load tracking nodes are set along the direction of fluid pressure transmission, from the valve body inlet flow channel wall, valve core throttling end face, valve core support structure, return spring assembly to valve body upper cover support structure. The interval between each tracking node does not exceed 0.5 mm. By tracking the changes in the force value and direction of the tracking nodes within each time step, the transmission path and amplitude changes of the fluid load in the solid structure are tracked in real time. After each complete alternating pressure cycle, the complete alternating load transmission trajectory within that cycle is output, including the main path of load transmission, the load peak value of each node, and the time delay characteristics of load transmission.

[0041] Step 42: Receive the alternating load transfer trajectory and, combined with the material cyclic plastic deformation accumulation mechanism, iteratively calculate the micro-slip band propagation rate and crack initiation critical value of the mesh element under alternating stress amplitude. Delineate the material micro-fatigue damage evolution boundary characterizing the critical point of structural service attenuation. Specifically, this includes: receiving the alternating load transfer trajectory within each cycle, extracting the alternating stress time series data of each load tracking node in the trajectory, and pre-entering the material performance parameters corresponding to each pressure-bearing structure of the pressure-reducing valve under test, including the elastic modulus, Poisson's ratio, yield strength, fatigue strength limit, and fracture toughness of the stainless steel materials used in the valve core, valve seat, and valve body, as well as the shear modulus, cyclic hardening coefficient, and fatigue limit parameters of the spring steel used in the return spring. Based on the extracted alternating stress time series data and the entered material performance parameters, combined with the material cyclic plastic deformation accumulation mechanism, establish a material fatigue damage accumulation model. The model uses alternating stress amplitude, number of cycles, and material yield strength as core inputs to characterize the accumulation process of internal plastic deformation of the material under cyclic loading. Based on the established fatigue damage accumulation model, the micro-slip band propagation rate of each mesh element in the solid domain mesh model under continuous alternating stress amplitude is iteratively calculated. The formula used in the calculation process is as follows: ; in, The rate of expansion of the micro-slip band, The extended length of the slip band, For the number of load cycles, and These are the fatigue characteristic constants of the corresponding materials. This represents the amplitude of alternating stress on the mesh element. The iterative calculation process uses a single load cycle as the step size. After each cycle is completed, the slip band extension length and extension rate of each mesh element are updated, and the cumulative amount of plastic deformation of each mesh element is recorded.

[0042] After iterative calculations of the micro-slip band propagation rate, the crack initiation critical value for each grid element is calculated based on the material's fracture toughness parameters and fatigue strength limit. The crack initiation critical value is the limit number of cycles and the limit stress amplitude required for the micro-slip bands within the material to propagate to the critical length and form a macroscopic fatigue crack. The slip band propagation rate, cumulative plastic deformation, and corresponding crack initiation critical value of each grid element are compared in real time. When the slip band propagation length of a grid element reaches 80% of the critical length and the cumulative plastic deformation exceeds the material's uniform plastic deformation limit, the grid element is designated as a fatigue damage critical element. After iterative calculations for at least 1000 load cycles, the spatial distribution of all fatigue damage critical elements is integrated and connected to form a continuous material damage critical interface.

[0043] Step 43: Based on the material micro-fatigue damage evolution boundary, a nonlinear hysteresis response function is introduced to dynamically fit the coupling hysteresis effect between the valve core micro-displacement fluctuation and the sudden change in medium flow rate. The nonlinear fluid-structure interaction constitutive response reflecting the deformation degradation of the sealing surface and the nonlinear attenuation of stiffness is extracted. Specifically, this includes: taking the defined material micro-fatigue damage evolution boundary, extracting the structural stiffness attenuation law and sealing surface deformation degradation characteristic parameters corresponding to the boundary; and simultaneously, based on the alternating load transmission trajectory, extracting the axial micro-displacement time series data of the valve core under alternating load, and the corresponding time series data of the sudden change in medium flow rate in the valve body flow channel. For the coupling hysteresis effect between the valve core micro-displacement fluctuation and the sudden change in medium flow rate, a nonlinear hysteresis response function is introduced to construct a fluid-structure interaction hysteresis dynamic model. The model takes the axial micro-displacement of the valve core as the input term and the change in medium flow rate as the output term. It also introduces a material stiffness nonlinear attenuation term, a sealing surface deformation hysteresis term, and a fluid inertia effect term to fully characterize the nonlinear hysteresis characteristics between the valve core displacement change and the flow rate change. The expression of the nonlinear hysteresis response function is: ; in, for The change in medium flow rate at any given time. for The minute axial displacement of the valve core at any given moment. The linear stiffness coefficient is... For nonlinear stiffness coefficients, The hysteresis effect weighting coefficient is... The hysteresis attenuation coefficient, This is the time variable for integration.

[0044] Based on the constructed nonlinear hysteresis response function, dynamic fitting is performed on the time series data of valve core micro-displacement and the time series data of sudden changes in medium flow. The least squares method is used for parameter identification during the fitting process to obtain the final solutions for the linear stiffness coefficient, nonlinear stiffness coefficient, hysteresis effect weighting coefficient, and hysteresis attenuation coefficient, ensuring that the sum of squared residuals between the fitting results and the measured data does not exceed 0.001. Based on the final parameters obtained from the fitting, combined with the defined material micro-fatigue damage evolution boundary, the deformation degradation of the sealing surface and the nonlinear attenuation law of structural stiffness caused by the accumulation of material fatigue damage under different cycle periods are analyzed. The coupling response characteristics between valve core displacement and medium flow, the variation law of sealing surface contact stress, and the attenuation curve of overall structural stiffness under different damage levels are extracted. By integrating these characteristic parameters and variation laws, a nonlinear fluid-structure coupling constitutive response that fully reflects the deformation degradation of the sealing surface and the nonlinear attenuation law of stiffness under cyclic load is obtained.

[0045] Step 44: Perform multi-parameter inverse calculation of the alternating load transfer trajectory, the material micro-fatigue damage evolution boundary, and the nonlinear fluid-structure interaction constitutive response. Using residual gradient descent and objective function extremum optimization strategies, derive the final opening and closing phase reference to ensure cyclic stability and the dynamic pressure compensation coefficient to suppress pressure transient overshoot. Specifically, this includes: integrating the alternating load transfer trajectory, the defined material micro-fatigue damage evolution boundary, and the extracted nonlinear fluid-structure interaction constitutive response into a multi-parameter input set to establish a multi-parameter inverse calculation model. The model's core objectives are to ensure the stability of the cyclic testing process, suppress pressure transient overshoot, and match the material fatigue damage evolution law. An objective function is set, with the pressure overshoot, valve core alternating load peak value, and structural fatigue damage accumulation rate during the cyclic process as optimization variables. The expression of the objective function is: ; in, The objective function value, This refers to the pressure overshoot during the cyclic process. The maximum rated inlet pressure of the pressure reducing valve under test. This represents the peak value of the alternating load on the valve core. The yield strength of the valve core material. This represents the rate of accumulation of structural fatigue damage. This represents the critical cumulative rate of fatigue damage. , , These are the weighting coefficients for the three optimization variables, set to 0.5, 0.3, and 0.2 respectively.

[0046] After establishing the objective function, the opening / closing phase reference and dynamic pressure compensation coefficient are used as input variables to be optimized. These are substituted into the multi-parameter inverse calculation model, and the residual gradient descent algorithm is used for iterative optimization. During the iteration, the gradient of the objective function value relative to the variable to be optimized is calculated at each iteration step, and the value of the variable to be optimized is updated along the direction of gradient descent. The iteration step size is set to 0.001, and the threshold for determining convergence is set to a change in the objective function value of less than 1. e-6 During the iterative optimization process, the evolution boundary of material micro-fatigue damage and the nonlinear fluid-structure interaction constitutive response are simultaneously combined to perform transient simulation verification on the cyclic process corresponding to each set of variables to be optimized. This ensures that the optimized variables can effectively suppress pressure transient overshoot, reduce the peak value of alternating load on the valve core, and slow down the accumulation rate of structural fatigue damage. When the iterative process reaches the convergence threshold and the simulation verification results meet the cyclic stability requirements, the iterative optimization stops, and the values ​​of the variables to be optimized at this time are output. These values ​​include the final opening and closing phase reference to ensure stable operation of the cyclic test process, and the dynamic pressure compensation coefficient used to suppress pressure transient overshoot during the cyclic process. The unit of the opening and closing phase reference is milliseconds, and the value range of the dynamic pressure compensation coefficient is 0 to 1.

[0047] In this embodiment of the invention, a set of nodal force balance equations between grid elements is established based on the spatial topological constraint relationship of a three-dimensional spatial discretized grid model. Periodic alternating pressure boundary conditions are injected to simulate the load transmission process from fluid pulsation impact to the solid valve core and spring assembly, and the alternating load transmission trajectory within each cycle is tracked and output. Then, combining the alternating load transmission trajectory with the material's cyclic plastic deformation accumulation mechanism, iterative calculations are performed on the micro-slip band propagation rate and crack initiation critical value of the grid elements under alternating stress amplitude to delineate the material properties characterizing the critical point of structural service degradation. Based on the material's micro-fatigue damage evolution boundary, a nonlinear hysteresis response function is introduced to dynamically fit the coupling hysteresis effect between the valve core's micro-displacement fluctuations and sudden changes in medium flow. The nonlinear fluid-structure interaction constitutive response, reflecting the deformation degradation and nonlinear stiffness decay of the sealing surface, is extracted. Finally, the alternating load transfer trajectory, the material's micro-fatigue damage evolution boundary, and the nonlinear fluid-structure interaction constitutive response are solved using multi-parameter inverse calculations. Through residual gradient descent and objective function extremum optimization strategies, the final opening and closing phase reference for ensuring cycle stability is derived in reverse. This technique, employing a full-process multiphysics coupling analysis and control parameter optimization method to suppress pressure transient overshoot, overcomes the core technical problems of existing technologies. These problems include the inability to accurately simulate the load transmission process from fluid pulsation to the solid structure during the cyclic opening and closing of a pressure-reducing valve, the inability to quantify the evolution of microscopic fatigue damage and the hysteresis effect of nonlinear fluid-structure interaction, and the inability to reverse-optimize and adapt cyclic control parameters to the structure and material characteristics of the pressure-reducing valve under test. The current technology relies on fixed general parameters for testing, leading to a severe disconnect between cyclic operating conditions and actual service scenarios, the inability to suppress the impact of pressure transient overshoot on the valve, and the inability of test results to accurately reflect the valve's true fatigue life and performance degradation. This technique achieves the effect of accurately reproducing the alternating load transmission path during the cyclic opening and closing of the pressure-reducing valve, quantifying the evolution boundary of microscopic fatigue damage and the constitutive response characteristics of nonlinear fluid-structure interaction, and reverse-deriving the opening and closing phase reference and dynamic pressure compensation coefficient that are highly adapted to the structure and material characteristics of the pressure-reducing valve under test. This effectively ensures the stability of the cyclic testing process, suppresses the impact damage of pressure transient overshoot on the valve, and achieves precise matching between cyclic control parameters and the actual service conditions of the valve.

[0048] In a preferred embodiment of the present invention, step 5 above may include: Step 51: Based on the final opening / closing phase reference and the dynamic pressure compensation coefficient, input as state variables to the cyclic operating condition mapping matrix. Parameter decoupling is performed through matrix space mapping and phase compensation calculation to obtain automatic cyclic control parameters including valve drive timing, duty cycle setpoint, and dynamic pressure compensation threshold. Specifically, this includes: completing the pre-data validity verification to confirm that the numerical accuracy of the final opening / closing phase reference and the dynamic pressure compensation coefficient meets millisecond-level control requirements, and that the value of the dynamic pressure compensation coefficient is within the valid range of 0 to 1, without data overflow or abnormal deviation. After verification, a cyclic operating condition mapping matrix is ​​pre-constructed. The mapping matrix is ​​a 6x6 non-singular square matrix. The row vectors of the matrix correspond to the mapping relationships of six dimensions: opening / closing phase, pressure compensation amount, drive timing, duty cycle, pressure threshold, and cycle period. The element values ​​of the matrix are pre-calibrated based on the rated pressure, rated flow rate, and structural dynamic response characteristics of the pressure reducing valve under test, ensuring that the rank of the matrix equals the order of the matrix, satisfying the operational requirements of parameter decoupling. Using the final opening / closing phase reference and the dynamic pressure compensation coefficient as state variables, a two-dimensional state input vector is constructed. The formula used in the calculation process is as follows: ; in, For the state input vector, As the final start / stop phase reference, This is the dynamic pressure compensation coefficient.

[0049] The constructed state input vector is input into the cyclic operating condition mapping matrix, and a matrix space mapping operation is performed to map the state input vector from the two-dimensional space of phase compensation to the six-dimensional space of full control parameters, obtaining the initial control parameter vector. A phase compensation operation is then performed on the initial control parameter vector. Based on the time delay characteristics of the opening and closing phase reference, the phase offset of the drive timing is corrected. The corrected phase deviation does not exceed 1 millisecond, eliminating the impact of the valve electromagnetic actuator's action delay on control accuracy. After the phase compensation operation, a parameter decoupling operation is performed on the corrected control parameter vector to eliminate coupling interference between various control parameters, including periodic coupling between the drive timing and duty cycle, and amplitude coupling between the pressure compensation threshold and the opening and closing phase. After the decoupling operation, the coupling degree between each control parameter does not exceed 0.01. Finally, the decoupled automatic cyclic control parameters, including the valve drive timing, duty cycle setpoint, and pressure dynamic compensation threshold, are obtained. The valve drive timing includes four time parameters: valve opening trigger time, opening hold time, closing trigger time, and closing hold time. The duty cycle is set to 50%, the pressure dynamic compensation threshold is set to 1.05% of the maximum rated intake pressure, and the total duration of a single cycle is set to 4 seconds.

[0050] Step 52: Receive the set automatic cycle control parameters and send synchronous drive commands to the electromagnetic actuators of the inlet valve and the outlet pressure relief valve. Control the inlet valve to perform periodic opening and closing operations according to the drive sequence, and control the outlet pressure relief valve to perform synchronous reverse opening and closing operations that are phase-inverse with the inlet valve. Construct an alternating differential pressure load environment in the test pipeline to simulate the load-bearing cyclic action of the pressure-reducing valve under test. Specifically, this includes: receiving the decoupled automatic cycle control parameters, first verifying the communication link with the electromagnetic actuators of the inlet valve and the outlet pressure relief valve, confirming that the signal transmission delay of the communication link does not exceed 0.5 milliseconds, the action response time of the electromagnetic actuator meets the control requirements, and there are no signal packet loss or communication interruptions. After verification, the timing synchronization control unit, based on the valve drive sequence in the automatic cycle control parameters, generates two synchronous drive pulse signals with a phase difference of 180 degrees, forming a phase-inverse drive logic. By using hard-wired synchronous triggering, synchronous drive commands are simultaneously sent to the electromagnetic actuators of both the inlet-side valve and the outlet-side pressure relief valve. The time difference between the two drive commands is no more than 0.1 milliseconds, ensuring complete synchronization of the drive signals. After receiving the drive command, the electromagnetic actuator of the inlet-side valve performs periodic and repeated opening and closing operations according to the set drive timing. At the opening trigger moment, the excitation circuit is activated, driving the valve core to complete the fully open action. During the opening holding time, it remains in the fully open conducting state. At the closing trigger moment, the excitation circuit is deactivated, driving the valve core to complete the fully closed action. During the closing holding time, it remains in the fully closed sealing state, completely replicating the preset opening and closing cycle. After receiving a synchronous drive command, the electromagnetic actuator of the outlet-side pressure relief valve performs a synchronous reverse opening and closing operation that is phase-reversed with that of the inlet-side valve. When the inlet-side valve switches to the fully open conducting state, the outlet-side pressure relief valve synchronously switches to the fully closed sealing state, and vice versa. The synchronization error between the two valves does not exceed 1 millisecond, and there is no situation of premature or delayed action. During the periodic opening and closing of the valve, the pressure value at the inlet side of the pressure reducing valve is collected in real time based on the dynamic pressure compensation threshold. When the inlet pressure exceeds the dynamic pressure compensation threshold, the opening and closing action duration of the inlet-side valve is automatically adjusted to correct the pressure amplitude in the pipeline, suppress transient pressure overshoot, and ensure that the pressure changes in the pipeline meet the preset alternating load requirements. By synchronously and in reverse opening and closing operations of two valves, the working conditions of high pressure conduction and low pressure release are periodically switched in the test pipeline, thus constructing an alternating differential pressure load environment consistent with the actual service conditions of the pressure reducing valve under test. This accurately simulates the pressurized opening and closing cycle of the pressure reducing valve under test during actual use, and fully reproduces the alternating load impact and pressure fluctuation characteristics during the valve opening and closing process.

[0051] Step 53: Based on the valve operation status under alternating differential pressure load environment, use a high-frequency cycle counter to accumulate and count the complete operation cycle of the inlet valve and the outlet pressure relief valve in real time to obtain the real-time cycle count data. Specifically, based on the constructed alternating differential pressure load environment and the synchronous reverse opening and closing operation status of the inlet valve and the outlet pressure relief valve, first complete the initialization setting of the high-frequency cycle counter, set the counter's counting trigger mode to dual-channel synchronous trigger mode, set the trigger threshold to the rising edge of the valve fully open signal, and set the counter's counting frequency to 1 MHz to ensure that the complete operation cycle of the valve can be accurately captured without any omissions or miscounts. After initialization, during each opening and closing action of the valves, the position feedback sensors built into the inlet-side valve and the outlet-side pressure relief valve collect the valve core position signal in real time. When the inlet-side valve completes a fully open action and the outlet-side pressure relief valve simultaneously completes a fully closed action, the position feedback sensor outputs the rising edge of the fully open signal. After receiving the dual-channel synchronous trigger signal, the high-frequency periodic counter determines that a complete valve opening and closing action cycle has been completed and performs a counting accumulation operation with a counting accumulation step size of 1. Throughout the entire cycle test, the high-frequency periodic counter continuously accumulates and counts the complete action cycles of the inlet-side valve and the outlet-side pressure relief valve in real time. After each counting accumulation, the current cumulative count value is transmitted to the storage unit and display unit in real time, and the validity of the cumulative count value is simultaneously verified to eliminate invalid counts caused by incomplete valve action or abnormal trigger signals, ensuring the accuracy of the counting results. The verified cumulative count value is used as the real-time cycle count data, which is updated and displayed in real time. At the same time, it is synchronously stored in the local storage medium. The stored content includes the timestamp corresponding to each count, valve action status parameters, and pipeline pressure values ​​to ensure the traceability of the cycle count data. Finally, continuous, accurate, and complete real-time cycle count data is obtained.

[0052] In this embodiment of the invention, the final opening / closing phase reference and the dynamic pressure compensation coefficient are input as state variables into the cyclic operating condition mapping matrix. Parameter decoupling is achieved through matrix space mapping and phase compensation calculation, resulting in customized automatic cyclic control parameters including valve drive timing, duty cycle setpoint, and dynamic pressure compensation threshold. Then, based on the set automatic cyclic control parameters, synchronous drive commands are sent to the electromagnetic actuators of the inlet valve and the outlet pressure relief valve. This controls the inlet valve to perform periodic repeated opening and closing operations according to the drive timing, while simultaneously controlling the outlet pressure relief valve to perform synchronous reverse opening and closing operations with the phase opposite to that of the inlet valve. An alternating pressure differential load environment is accurately constructed within the test pipeline to simulate the load-bearing cyclic action of the pressure-reducing valve under test. Finally, based on the valve action state under the alternating pressure differential load environment, a high-frequency periodic counter is used to accumulate and statistically analyze the complete action cycles of the inlet valve and the outlet pressure relief valve in real time to obtain real-time cycle count data. This fully automated cyclic control and counting technology overcomes the limitations of existing technologies in cyclic operation. The core technical problems include: low matching degree between control parameters and the structural characteristics and dynamic response characteristics of the pressure reducing valve under test; asynchronous opening and closing sequence of inlet and outlet valves; insufficient phase control accuracy; inability to accurately construct an alternating differential pressure load environment consistent with actual service conditions; low accuracy of cycle count statistics; easy omissions and miscounts; pressure shocks and severe distortion of operating condition simulation caused by fixed parameter cyclic control; and low degree of automation and poor controllability of the testing process. These factors lead to large deviations between cycle life test results and the actual service life of the valve, and insufficient reliability of test data. The solution achieves precise matching between cyclic control parameters and the characteristics of the pressure reducing valve under test, ensuring the synchronicity of the opening and closing actions of the inlet valve and the outlet pressure relief valve, the accuracy of phase control, and the consistency of action execution. It accurately reproduces the alternating differential pressure load environment of the pressure reducing valve in actual service in the test pipeline, realizes high-fidelity dynamic simulation of load cyclic action, and completes high-precision, real-time statistics of cycle count without omissions, thus improving the automation, stability, and controllability of the cycle life test process.

[0053] In a preferred embodiment of the present invention, step 6 above may include: Step 61: Retrieve real-time cycle count data and compare it with a preset cycle count threshold. When the real-time cycle count data is determined to be greater than or equal to the preset cycle count threshold, immediately interrupt the current cycle drive command and obtain a forced pressure relief trigger signal. Specifically, this includes: maintaining real-time data communication with the high-frequency cycle counter throughout the entire cycle test. The sampling refresh frequency of the communication link is set to 1000 Hz, and the real-time cycle count data is retrieved and updated every 1 millisecond to ensure the real-time and continuous nature of the cycle count data, without any data delay or update lag. Before the test begins, a preset cycle count threshold is pre-entered in the parameter setting unit. The preset cycle count threshold is set to 100,000 times, which matches the standard requirements for cycle life testing in the type inspection of pressure reducing valves. After each retrieval of real-time cycle count data, the retrieved real-time cycle count data is immediately compared with the preset cycle count threshold. The formula used in the comparison calculation process is: ; in, The difference in the number of iterations. This is real-time loop count data that is retrieved in real time. This is the preset threshold for the number of iterations.

[0054] During the numerical comparison process, anti-interference verification is performed simultaneously, continuously judging the difference in the number of iterations within three consecutive sampling periods to avoid false triggering caused by interference from a single sampling signal. When the calculation results within three consecutive sampling periods all meet the requirements... When the condition of 0 or greater than or equal to 0 is met, i.e., the real-time cycle count data is greater than or equal to the preset cycle count threshold, the cycle termination operation is immediately executed. Through a hard-wired emergency stop control link, the currently issued periodic cycle drive command is immediately interrupted, the sending of opening and closing drive pulses to the electromagnetic actuators of the inlet-side valve and the outlet-side pressure relief valve is stopped, the output port of the valve drive signal is locked to prevent the issuance of new drive commands, and a level-holding forced pressure relief trigger signal is generated. The output level of the trigger signal is a 24V DC high level, and the signal holding time is not less than the entire duration of the test process termination, ensuring the stable execution of the pressure relief control action and preventing pressure relief interruption due to signal interruption.

[0055] Step 62: Based on the forced pressure relief trigger signal, disconnect the excitation circuit of the inlet-side valve to switch to a closed and sealed state, and simultaneously connect the excitation circuit of the outlet-side pressure relief valve to switch to a fully open and venting state. Establish a low-pressure relief channel at the end of the test pipeline. Specifically, this includes: receiving the generated forced pressure relief trigger signal, verifying the validity of the trigger signal, acquiring the level value of the trigger signal, confirming that the trigger signal is a stable 24V DC high level and the signal duration exceeds 10 milliseconds, eliminating malfunctions caused by interference signals, and immediately executing valve state switching control after successful verification. Through a synchronous trigger circuit, state switching control commands are simultaneously sent to the electromagnetic actuators of the inlet-side valve and the outlet-side pressure relief valve. The time difference between the two control commands is no more than 0.1 milliseconds to ensure that the state switching actions of the two valves maintain strict timing synchronization. Upon receiving the state switching control command, the electromagnetic actuator of the inlet-side valve immediately cuts off the valve's excitation circuit and disconnects the power supply to the valve drive motor. The valve's return spring drives the valve core to perform a fully closed stroke until the valve core and valve seat sealing surface are completely pressed together, switching to a fully closed sealing state. This completely cuts off the medium flow path between the upstream high-pressure gas source and the test pipeline, ensuring that no new high-pressure medium continuously enters the test pipeline during the pressure relief process. Simultaneously with the inlet-side valve's closing action, the electromagnetic actuator of the outlet-side pressure relief valve, upon receiving the synchronous state switching control command, immediately activates the valve's excitation circuit and connects the power supply to the valve drive motor, driving the valve core to perform a fully open stroke until the valve core completely disengages from the valve seat flow channel, switching to a fully open venting state. The flow area of ​​the valve's flow channel reaches its design maximum value, with no throttling or obstruction. After the two valves complete the state switching, the real-time signal of the position feedback sensor built into the valve is collected to confirm that the inlet valve is stably in a completely closed and sealed state and the outlet pressure relief valve is stably in a fully open and venting state. At this time, the upstream high-pressure gas source input path of the test pipeline is completely cut off, and the end of the test pipeline is connected to the downstream venting silencer through the fully open outlet pressure relief valve to form a continuous, unobstructed and unthrottled low-pressure release channel.

[0056] Step 63: Using the low-pressure relief channel, the high-pressure medium retained in the test pipeline and the pressure reducing valve under test is gradually unloaded to the environmental safety pressure range. A zero pressure confirmation signal is collected in the pipeline, and the automated test process is terminated. A cycle endurance test completion command is output to complete the cycle endurance test. Specifically, based on the low-pressure relief channel established at the end of the test pipeline, a gradient unloading operation of the high-pressure medium inside the test pipeline and the pressure reducing valve under test is performed. The gradient unloading process is divided into three continuous pressure control stages to avoid water hammer effect and pressure shock caused by rapid release of high-pressure medium, which could damage the sealing surface of the pressure reducing valve under test, the sensor of the test pipeline, and the connection joint. The first stage is the initial pressure relief stage. The outlet-side pressure relief valve is kept fully open for 2 seconds to unload the high-pressure medium in the test pipeline and the pressure reducing valve under test from the rated working pressure to 50% of the maximum rated inlet pressure. The pipeline pressure change is monitored in real time. When the pressure drops to the target value, the second stage, the buffer pressure relief stage, begins. In this stage, the pressure relief channel is kept open for 3 seconds to unload the medium pressure in the pipeline from 50% of the maximum rated inlet pressure to 10% of the maximum rated inlet pressure, completing the smooth release of most of the pressure. The third stage, the zero-pressure relief stage, begins. The pressure relief channel is kept fully open until the medium pressure in the pipeline drops completely to the environmental safety pressure range. The environmental safety pressure range is set to 0 MPa to 0.05 MPa gauge pressure, a safe pressure range that is basically the same as the ambient atmospheric pressure. Throughout the gradient pressure relief process, a high-precision pressure sensor installed on the outlet-side pipeline of the pressure reducing valve under test continuously collects the real-time value of the medium pressure in the test pipeline at a sampling frequency of 1000 Hz, generating continuous pressure decay time series data, and transmitting the data in real time. The collected real-time pressure values ​​are continuously evaluated, and the formula used in the calculation process is as follows: ; in, This represents the deviation between the pipeline pressure and the ambient atmospheric pressure. To test the real-time pressure of the medium in the pipeline, This represents the current atmospheric pressure value.

[0057] When the pressure deviation value collected within 100 milliseconds is less than or equal to 0.05 MPa, it is determined that the high-pressure medium in the test pipeline and the pressure reducing valve under test has been completely unloaded to the safe environmental pressure range, and a pipeline pressure zeroing confirmation signal is collected. Upon receiving the pipeline pressure zeroing confirmation signal, the automated test process is immediately terminated, locking the control status of all valves, maintaining the closed state of the inlet valve and the fully open state of the outlet pressure relief valve to prevent accidental entry of high-pressure medium due to misoperation, stopping the data acquisition of all sensors, and locking all data collected throughout the entire test process, including the number of cycles, inlet and outlet pressure timing data, valve action status data, and pressure overshoot data, to the local storage unit and the cloud backup storage unit to ensure the traceability and tamper-proofness of the test data. After data storage is completed, the human-machine interface outputs a cycle endurance test completion command, and at the same time, a test completion prompt signal is issued through the audible and visual prompt device, completely ending the entire process of this pressure reducing valve cycle endurance test.

[0058] In this embodiment of the invention, the real-time cycle count is compared with a preset threshold value. When the real-time cycle count is greater than or equal to the preset threshold, the current cycle drive command is immediately interrupted and a forced pressure relief trigger signal is generated. Based on the forced pressure relief trigger signal, the excitation circuit of the inlet valve is simultaneously cut off to switch it to a closed and sealed state, and the excitation circuit of the outlet pressure relief valve is switched to a fully open and venting state. A stable low-pressure relief channel is established at the end of the test pipeline. Finally, the high-pressure medium retained in the test pipeline and the pressure reducing valve under test is unloaded to the environmental safe pressure range through the low-pressure relief channel. After collecting the pipeline pressure zero confirmation signal, the automated test process is terminated and a cycle endurance test completion command is output. This fully automated shutdown and pressure relief control technology overcomes the problems of existing technologies, such as the inability to automatically identify the cycle count target point, the need for full manual intervention, and the easy occurrence of cycle count errors and invalid test data. Existing technologies suffer from several technical problems: asynchronous operation of inlet and outlet valves during shutdown and pressure relief; pressure surges in pipelines caused by rapid release of high-pressure media can easily damage the pressure-reducing valve under test and the testing equipment; lack of gradient control and pressure zeroing confirmation during the pressure relief process leads to non-standard test termination procedures and high safety risks; and the test process cannot achieve fully automated closed-loop control, resulting in low testing efficiency and poor consistency of test results. This new technology achieves precise identification of the cycle number threshold and fully automated shutdown triggering of the test process, ensuring the synchronicity of inlet valve shut-off and outlet pressure relief valve opening, realizing smooth gradient pressure relief of the high-pressure media, effectively avoiding damage to the pressure-reducing valve under test and the testing equipment from pressure surges, eliminating safety hazards during high-pressure pressure relief, and achieving standardized and regulated control of the test termination process through pressure zeroing confirmation. This completes the automated closed-loop control of the entire cyclic endurance test process, improving the safety, efficiency, accuracy, consistency, and repeatability of the test results.

[0059] like Figure 2 As shown, embodiments of the present invention also provide a dynamic simulation test system for the cycle life of a pressure reducing valve, comprising: The acquisition module is used to install the pressure reducing valve under test in the test pipeline, open the inlet valve and the outlet pressure relief valve, manually adjust the inlet pressure regulator to make the inlet pressure of the pressure reducing valve under test reach the maximum rated inlet pressure, and obtain the pressure reducing valve under test with the set inlet pressure. The adjustment module is used to adjust the pressure reducing valve under test based on the pre-set inlet pressure, so that the outlet pressure reaches the maximum rated outlet pressure, thus obtaining a pressure reducing valve under test where both the inlet pressure and the outlet pressure reach the rated values. The module is used to extract the fluid-structure interaction geometric topology features and real-time pressure gradient field of the pressure reducing valve under test, where both the inlet and outlet pressures have reached the rated values, and to construct a three-dimensional spatial discretized mesh model. The calculation module is used to perform multi-parameter inverse calculations on the alternating load transfer trajectory between models, the material micro-fatigue damage evolution boundary, and the nonlinear fluid-structure interaction constitutive response based on the spatial topological constraint relationship of the three-dimensional spatial discretized geometric model, so as to obtain the final opening and closing phase reference and dynamic pressure compensation coefficient. The control module is used to substitute the final opening and closing phase reference and the dynamic pressure compensation coefficient into the cyclic working condition mapping matrix to obtain the set automatic cyclic control parameters; according to the automatic cyclic control parameters, the inlet side valve is automatically controlled to open and close repeatedly, and the outlet side pressure relief valve is opened and closed synchronously in reverse to simulate the load cyclic action of the pressure reducing valve under test, record the number of cycles, and obtain real-time cycle number data. The processing module is used to automatically close the inlet valve and open the outlet pressure relief valve when the real-time cycle count data reaches the preset cycle count threshold, so as to relieve pressure on the test pipeline and the pressure reducing valve under test and complete the cycle endurance test.

[0060] It should be noted that this system is a system corresponding to the above method. All implementation methods in the above method embodiments are applicable to this embodiment and can achieve the same technical effect.

[0061] Embodiments of the present invention also provide a computing device, including: a processor and a memory storing a computer program, wherein the computer program, when executed by the processor, performs the method described above. All implementations in the above method embodiments are applicable to this embodiment and can achieve the same technical effects.

[0062] Embodiments of the present invention also provide a computer-readable storage medium storing instructions that, when executed on a computer, cause the computer to perform the method described above. All implementations in the above method embodiments are applicable to this embodiment and can achieve the same technical effects.

[0063] Experimental example: The pressure reducing valve under test is a piston-type high-pressure nitrogen pressure reducing valve, model JYF-20P, with a nominal diameter of DN20. Its key rated parameters are: maximum rated inlet pressure 10.0MPa, maximum rated outlet pressure 0.8MPa, and design cycle life ≥100,000 cycles.

[0064] Test system platform: Build such as Figure 2 The automated testing system shown includes the following core components: a 15MPa high-pressure nitrogen cylinder group, an inlet-side electric regulating valve, a high-precision inlet manual pressure regulator, a pressure reducing valve under test, an outlet-side fast electromagnetic pressure relief valve, upstream and downstream high-frequency piezoresistive pressure sensors, a 3D laser scanner, an ultrasonic thickness gauge, a central control unit, and a human-machine interface.

[0065] Steps 1 and 2: Manual calibration and locking of inlet and outlet rated pressures: Install the JYF-20P valve under test strictly according to the specifications into the test pipeline. Tighten the flange bolts to the specified value using a torque wrench. Open the inlet valve and outlet pressure relief valve to establish a flow path. Slowly rotate the inlet pressure regulator handwheel counterclockwise, and the control unit will collect the inlet pressure in real time. Maintain a stable inlet pressure, send a command to close the outlet pressure relief valve, and the pipeline will switch to a closed pressure-bearing state. Slowly rotate the preload adjusting screw on the top of the pressure reducing valve, and the valve under test will be in its rated initial state.

[0066] Step 3: Extract fluid-structure interaction features and construct a 3D mesh model: With the pressure reducing valve stabilized at its rated operating conditions, a 3D laser scanner was used to scan its internal flow channels, obtaining over 500,000 point cloud data points with an accuracy of ±0.01 mm. An ultrasonic thickness gauge was used to measure the wall thickness of key areas such as the valve core guide and valve seat support. Software was used for surface fitting and feature dimensionality reduction to extract precise fluid-structure interaction geometric topological features. Transient pressure data was simultaneously collected at three locations: downstream of the valve body inlet, in the middle of the valve core chamber, and upstream of the outlet. After gradient tensor calculation and filtering, the pressure distribution field within the valve was reconstructed. The data showed that the main pressure drop occurred at the annular throttling gap between the valve core and the valve seat, where the pressure drop gradient was most severe. The geometric features were spatially registered with the pressure field. Mesh refinement was performed in the valve seat region, which had a large pressure gradient and complex geometry, ultimately generating a high-precision 3D spatial discretized mesh model containing approximately 850,000 elements.

[0067] Step 4: Obtain the optimal control baseline through multi-parameter inverse calculation: Based on a three-dimensional mesh model, a periodic alternating pressure boundary condition with a frequency of 0.25 Hz and an amplitude of 0-10 MPa was applied at the fluid domain inlet to conduct fluid-structure interaction transient dynamics simulations. The simulations show that within each cycle, the fluid impact load is mainly transmitted to the return spring through the valve core end face, and the maximum alternating stress amplitude Δσ of the spring is... sim With a pressure of approximately 450 MPa, and based on the SN curve of the valve core material, the theoretical fatigue life under the current load spectrum is calculated to be approximately 120,000 cycles. Analysis shows that the valve core displacement lags behind the pressure change by about 15 ms, exhibiting significant nonlinearity. Taking minimizing pressure overshoot and maximizing the theoretical fatigue cycle count as the objective function, the inlet valve opening and closing phase and pressure feedback compensation coefficient are optimized in reverse. After 152 iterations, the objective function converges.

[0068] Step 5, Automated load cycle testing and real-time counting: Substituting the optimized phase reference and compensation coefficients into the cyclic operating condition mapping matrix, the specific automatic cyclic control parameters are calculated. The cycle period T = 4s, the inlet valve opening time is 2s, the pressure relief valve operates in opposite phases, and the pressure overshoot compensation threshold is set to 8.5MPa. Based on these parameters, the inlet valve and outlet pressure relief valve are precisely controlled to perform synchronous and opposite opening and closing actions, generating pressure at both ends of the pressure reducing valve as shown in the figure. Figure 4 The alternating differential pressure load is shown. A high-frequency periodic counter begins to accumulate; during the test, the outlet pressure P... out The pressure fluctuates periodically within the range of 0.75~0.85MPa. The pressure overshoot at the moment of each opening of the inlet valve is suppressed to below 10.5MPa, and the real-time cycle number N is continuously recorded.

[0069] Step 6: Upon reaching the threshold, the system automatically releases pressure and shuts down. When the real-time cycle count N reaches the preset 100,000, the control unit immediately interrupts the drive command, synchronously triggering the inlet valve to close and the outlet pressure relief valve to fully open, establishing a release channel. The system then executes the gradient pressure relief logic, such as... Figure 6 As shown, the pipeline pressure smoothly decreased from high pressure to ambient pressure within approximately 15 seconds, without any pressure surge. Once the pressure reached zero, the process automatically terminated.

[0070] Figure 3 and Figure 4 The simulation waveforms of the outlet pressure within one cycle can be displayed separately before and after optimization. The pressure overshoot peak is significantly reduced after optimization. Figure 3 and Figure 4 Corresponding to step 4, this section visually demonstrates the core optimization process of multi-parameter reverse calculation and its effects. Through iteration, a customized final opening and closing phase reference and dynamic pressure compensation coefficient are obtained.

[0071] Figure 5 The horizontal axis represents time, and the vertical axis represents pressure. The main curve represents the outlet pressure P of the pressure-reducing valve under test. out It fluctuates regularly around the 0.8MPa baseline. The background is shaded with colored blocks to indicate the opening and closing states of the inlet and outlet pressure relief valves, which are strictly out of phase. The pressure overshoot suppression zone can be marked on the diagram. Figure 5 Corresponding to step 5, the core results of automated testing are intuitively displayed, including the reproduction effect of alternating differential pressure load environment and the ability of dynamic pressure compensation to suppress pressure overshoot, reflecting the dynamic simulation characteristics of the test conditions.

[0072] Figure 6 The horizontal axis represents time, and the vertical axis represents the pressure within the test pipeline. The curve shows that after the cycle stops triggering, the pipeline pressure does not drop abruptly, but rather goes through three stages: rapid decrease, buffered decrease, and stable return to zero, eventually stabilizing within the tolerance range of approximately 0 MPa. Figure 6Corresponding to step 6, the automated and safe test termination process is demonstrated, highlighting the closed-loop control capability and safety design of the method, avoiding the damage to valves and pipelines that may be caused by sudden pressure relief in traditional testing.

[0073] The above description represents the preferred embodiments of the present invention. It should be noted that those skilled in the art can make various improvements and modifications without departing from the principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A dynamic simulation test method for the cycle life of a pressure reducing valve, characterized in that, The method includes: Install the pressure reducing valve under test in the test pipeline, open the inlet valve and the outlet pressure relief valve, manually adjust the inlet pressure regulator to make the inlet pressure of the pressure reducing valve under test reach the maximum rated inlet pressure, and obtain the pressure reducing valve under test with the set inlet pressure. Based on the pressure reducing valve under test with the inlet pressure already set, adjust the pressure reducing valve itself so that the outlet pressure reaches the maximum rated outlet pressure, thus obtaining a pressure reducing valve under test with both inlet and outlet pressures reaching the rated values. Extract the fluid-structure interaction geometric topology features and real-time pressure gradient field of the pressure reducing valve under test, where both inlet and outlet pressures reach the rated values, and construct a three-dimensional spatial discretized mesh model. Based on the spatial topological constraints of the three-dimensional spatial discretized geometric model, multi-parameter inverse calculations are performed on the alternating load transfer trajectory between models, the material micro-fatigue damage evolution boundary, and the nonlinear fluid-structure coupling constitutive response to obtain the final opening and closing phase reference and dynamic pressure compensation coefficient. Substitute the final opening and closing phase reference and the dynamic pressure compensation coefficient into the cyclic working condition mapping matrix to obtain the set automatic cyclic control parameters; according to the automatic cyclic control parameters, automatically control the inlet side valve to open and close repeatedly and the outlet side pressure relief valve to open and close synchronously in reverse, simulate the load cyclic action of the pressure reducing valve under test, record the number of cycles, and obtain real-time cycle number data. When the real-time cycle count data reaches the preset cycle count threshold, the inlet valve is automatically closed and the outlet pressure relief valve is opened to relieve pressure on the test pipeline and the pressure reducing valve under test, thus completing the cycle endurance test.

2. The dynamic simulation test method for the cycle life of a pressure reducing valve according to claim 1, characterized in that, Install the pressure reducing valve under test in the test pipeline, open the inlet valve and the outlet pressure relief valve, and manually adjust the inlet pressure regulator to make the inlet pressure of the pressure reducing valve under test reach the maximum rated inlet pressure, thus obtaining the pressure reducing valve under test with the set inlet pressure, including: The outlet end of the pressure reducing valve under test is rigidly sealed and connected to the outlet branch of the test pipeline, and a complete medium flow test pipeline is constructed based on the connection relationship. Based on the complete media flow test pipeline, a synchronous opening command is sent to the actuator of the inlet valve and the outlet pressure relief valve, so that the inlet valve is switched to the fully open conduction condition and the outlet pressure relief valve is switched to the fully open venting condition, thus establishing the initial media flow path. Based on the initial medium flow path, the pressure regulating handwheel of the inlet pressure regulator is gradually rotated counterclockwise to control the throttling opening of the upstream gas source medium to continuously increase, and the pressure feedback signal of the inlet side pipeline is collected in real time. The real-time value of the pressure feedback signal is dynamically compared with the maximum rated intake pressure. When the pressure feedback signal rises to the maximum rated intake pressure and the pressure fluctuation amplitude converges within the preset steady-state tolerance range, the pressure adjustment handwheel is stopped and the current throttling opening is locked. Based on the locked state, the pressure reducing valve with the set inlet pressure is obtained.

3. The dynamic simulation test method for the cycle life of the pressure reducing valve according to claim 2, characterized in that, Based on the pressure reducing valve under test with a pre-set inlet pressure, adjust the valve itself to achieve the maximum rated outlet pressure, resulting in a pressure reducing valve where both inlet and outlet pressures reach their rated values. This includes: Based on the pressure reducing valve under test with the inlet pressure already set, the current throttling opening of the inlet pressure regulator is kept in a physically locked state, and a closing command is sent to the actuator of the outlet pressure relief valve to cut off the outlet venting passage, so that the test tube route changes from an open flow condition to a closed pressure condition. Based on the closed pressure condition, the preload adjusting screw at the top of the pressure reducing valve under test is rotated axially, which causes the compression of the internal reset spring to change, thereby driving the valve core to generate axial displacement to reconstruct the initial throttling gap at the valve seat. Based on the reconstructed initial throttling gap, the pressure response rise curve of the outlet side pipeline is tracked in real time. The real-time slope of the pressure response rise curve is matched with the target pressure approach rate to evaluate the suppression effect of the current throttling gap on the medium pressure drop. When the terminal value of the pressure response climb curve stabilizes at the maximum rated outlet pressure, and the pressure feedback signal of the inlet side pipeline is simultaneously verified to have no attenuation shift, stop rotating the preload adjusting screw and lock the anti-loosening positioning mechanism. Based on the locked state, it is confirmed that the pressure reducing valve under test has reached the rated value for both inlet and outlet pressures.

4. The dynamic simulation test method for the cycle life of the pressure reducing valve according to claim 3, characterized in that, The fluid-structure interaction geometric topology and real-time pressure gradient field of the pressure-reducing valve under test, where both inlet and outlet pressures reach their rated values, are extracted to construct a three-dimensional discretized mesh model, including: Based on the pressure reducing valve under test where both inlet and outlet pressures reach their rated values, the multi-sensor synchronous sampling interface is called to obtain the internal flow channel contour coordinates and key pressure-bearing wall thickness dimensions. Through spatial surface fitting and feature dimensionality reduction, the fluid-structure interaction geometric topology features characterizing the interface between the fluid medium flow path and the solid structure are extracted. Based on the geometric topology characteristics of fluid-structure interaction, under the steady-state operation of the test pipeline, piezoresistive pressure sensors are fixedly installed as pressure acquisition nodes at preset measurement points downstream of the valve body inlet flange, in the middle section of the valve core flow channel, and upstream of the outlet flange along the medium flow direction. The transient pressure time series at each measurement point is synchronously acquired through the piezoresistive pressure sensors. Gradient tensor operation and spatial domain smoothing filtering are performed on the acquired transient pressure time series to reconstruct a real-time pressure gradient field that reflects the local pressure drop rate and turbulence pulsation intensity. The fluid-structure interaction geometric topology features are registered with the real-time pressure gradient field in a spatial coordinate system. Based on the registered composite field data, a three-dimensional spatial discretized mesh model is obtained that matches the node topological connection relationship with the distribution density of local stress concentration areas.

5. The dynamic simulation test method for the cycle life of the pressure reducing valve according to claim 4, characterized in that, Based on the spatial topological constraints of the three-dimensional discretized geometric model, multi-parameter inverse calculations are performed on the alternating load transfer trajectory between models, the material micro-fatigue damage evolution boundary, and the nonlinear fluid-structure interaction constitutive response to obtain the final opening and closing phase reference and dynamic pressure compensation coefficients, including: Based on the spatial topological constraints of the three-dimensional spatial discretized mesh model, a set of nodal force balance equations between mesh elements is established, and periodic alternating pressure boundary conditions are injected to simulate the load transmission process of fluid pulsation impact to solid valve core and spring assembly, and to track and output the alternating load transmission trajectory in each cycle. By taking the alternating load transfer trajectory and combining the material cyclic plastic deformation accumulation mechanism, the micro-slip zone propagation rate and crack initiation critical value of the mesh element under the action of alternating stress amplitude are iteratively calculated, and the material micro-fatigue damage evolution boundary characterizing the critical point of structural service attenuation is delineated. Based on the material micro-fatigue damage evolution boundary, a nonlinear hysteresis response function is introduced to dynamically fit the coupling hysteresis effect between valve core micro-displacement fluctuation and medium flow change, and extract the nonlinear fluid-structure coupling constitutive response that reflects the deformation degradation and stiffness nonlinear decay law of the sealing surface. The alternating load transfer trajectory, the material micro-fatigue damage evolution boundary, and the nonlinear fluid-structure interaction constitutive response are solved by multi-parameter inverse calculation. By using residual gradient descent and objective function extremum optimization strategies, the final on- and off-phase reference to ensure cyclic stability and the dynamic pressure compensation coefficient to suppress pressure transient overshoot are derived in reverse.

6. The dynamic simulation test method for the cycle life of a pressure reducing valve according to claim 5, characterized in that, Substituting the final opening / closing phase reference and dynamic pressure compensation coefficient into the cyclic operating condition mapping matrix, the set automatic cyclic control parameters are obtained. Based on the automatic cyclic control parameters, the inlet-side valve is automatically controlled to repeatedly open and close, and the outlet-side pressure relief valve is synchronously opened and closed in reverse to simulate the load-bearing cyclic action of the pressure-reducing valve under test. The number of cycles is recorded to obtain real-time cycle count data, including: Based on the final opening and closing phase reference and the dynamic pressure compensation coefficient as state variables, the parameters are input to the cyclic operating condition mapping matrix. Through matrix space mapping and phase compensation calculation, the parameters are decoupled to obtain the automatic cyclic control parameters including valve drive timing, duty cycle setting value and pressure dynamic compensation threshold. Based on the set automatic cycle control parameters, synchronous drive commands are sent to the electromagnetic actuators of the inlet valve and the outlet pressure relief valve to control the inlet valve to perform periodic and repeated opening and closing operations according to the drive sequence, and to control the outlet pressure relief valve to perform synchronous reverse opening and closing operations that are phase opposite to those of the inlet valve. An alternating differential pressure load environment is constructed in the test pipeline to simulate the load cycle action of the pressure reducing valve under test. Based on the valve operation status under alternating differential pressure load environment, a high-frequency cycle counter is used to accumulate and statistically analyze the complete operation cycle of the inlet valve and the outlet pressure relief valve in real time to obtain the real-time cycle count data.

7. The dynamic simulation test method for the cycle life of a pressure reducing valve according to claim 6, characterized in that, When the real-time cycle count data reaches the preset cycle count threshold, the inlet valve is automatically closed and the outlet pressure relief valve is opened to depressurize the test pipeline and the pressure reducing valve under test, completing the cycle endurance test, including: The system retrieves real-time loop count data and compares it with a preset loop count threshold. When the real-time loop count data is determined to be greater than or equal to the preset loop count threshold, the current loop drive instruction is immediately interrupted and a forced pressure relief trigger signal is obtained. Based on the forced pressure relief trigger signal, the excitation circuit of the inlet valve is switched to a closed and sealed state, while the excitation circuit of the outlet pressure relief valve is switched to a fully open and venting state, thus establishing a low-pressure relief channel at the end of the test pipeline. Using the low-pressure relief channel, the high-pressure medium retained in the test pipeline and the pressure reducing valve under test is gradually unloaded to the environmental safety pressure range. The pipeline pressure is collected to confirm that it has returned to zero and the automated test process is terminated. The cycle endurance test is completed by outputting the cycle endurance test completion command.

8. A dynamic simulation test system for the cycle life of a pressure reducing valve, the system implementing the method as described in any one of claims 1 to 7, characterized in that, include: The acquisition module is used to install the pressure reducing valve under test in the test pipeline, open the inlet valve and the outlet pressure relief valve, manually adjust the inlet pressure regulator to make the inlet pressure of the pressure reducing valve under test reach the maximum rated inlet pressure, and obtain the pressure reducing valve under test with the set inlet pressure. The adjustment module is used to adjust the pressure reducing valve under test based on the pre-set inlet pressure, so that the outlet pressure reaches the maximum rated outlet pressure, thus obtaining a pressure reducing valve under test where both the inlet pressure and the outlet pressure reach the rated values. The module is used to extract the fluid-structure interaction geometric topology features and real-time pressure gradient field of the pressure reducing valve under test, where both the inlet and outlet pressures have reached the rated values, and to construct a three-dimensional spatial discretized mesh model. The calculation module is used to perform multi-parameter inverse calculations on the alternating load transfer trajectory between models, the material micro-fatigue damage evolution boundary, and the nonlinear fluid-structure interaction constitutive response based on the spatial topological constraint relationship of the three-dimensional spatial discretized geometric model, so as to obtain the final opening and closing phase reference and dynamic pressure compensation coefficient. The control module is used to substitute the final opening and closing phase reference and the dynamic pressure compensation coefficient into the cyclic working condition mapping matrix to obtain the set automatic cyclic control parameters; according to the automatic cyclic control parameters, the inlet side valve is automatically controlled to open and close repeatedly, and the outlet side pressure relief valve is opened and closed synchronously in reverse to simulate the load cyclic action of the pressure reducing valve under test, record the number of cycles, and obtain real-time cycle number data. The processing module is used to automatically close the inlet valve and open the outlet pressure relief valve when the real-time cycle count data reaches the preset cycle count threshold, so as to relieve pressure on the test pipeline and the pressure reducing valve under test and complete the cycle endurance test.

9. A computing device, characterized in that, include: One or more processors; A storage device for storing one or more programs, which, when executed by one or more processors, cause the one or more processors to implement the method as described in any one of claims 1 to 7.

10. A computer-readable storage medium, characterized in that, The computer-readable storage medium stores a program that, when executed by a processor, implements the method as described in any one of claims 1 to 7.

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