Wallboard impact test device and method for simulating dampening load

Abstract

The invention provides a wallboard impact test device and test method for simulating a dampening load, and belongs to the field of bearing performance tests. Comprising a dampening wave impact load simulation loading module, a test wall plate is fixed through a test clamp tool module, and in the test impact process, obtained real-time monitoring data are sent to a controller of the dampening wave impact load simulation loading module through a test measurement module so as to complete closed-loop control of dynamic loads when dampening wave impact is simulated; the dampening wave impact load simulation loading module comprises a controller, a hydraulic power unit and a loading unit, and the controller compares experimental data of a dampening wave impact load real experiment with real-time simulation data obtained by the test measurement module, converts an obtained difference value into an electric signal and sends the electric signal to the hydraulic power unit; electric signals are converted into pressure loads through the hydraulic power unit, and actions are executed by the loading unit. According to the invention, the simulation effect of a real dampening wave-colliding service scene can be achieved.

Description

Technical Field

[0001] The present invention belongs to the field of bearing performance tests, and particularly relates to a panel impact test device and a test method for simulating water landing loads. Background Art

[0002] Water surface aircraft can take off and land, taxi, and berth on the water surface. According to the water landing structure form, they can generally be divided into hull-type water surface aircraft and float-type water surface aircraft, and are mainly used in the fields of transportation, patrol, forest fire fighting, water rescue, etc. The operating environment of water surface aircraft is more complex than that of conventional land-based aircraft. It not only requires good flight performance but also certain seaworthiness performance. During the water landing and wave impact movement of water surface aircraft, the floats and the lower fuselage structure of the hull type are often subjected to large impact loads, which pose certain safety challenges to the aircraft structure. Past research has shown that there are significant differences in the load distribution and structural deformation of water surface aircraft when hitting the water surface compared to hitting hard ground. During the process of hitting the water surface, weaker structures such as the skin undergo large deformations, and the water will deform along with the structural deformation, resulting in weaker structures such as the skin and stringers absorbing more energy compared to the case of hitting hard ground, leading to damage. The water landing panel of a water surface aircraft is the main load-bearing structure during the water landing process and needs to bear the impact pressure of water landing and wave impact. Therefore, it is necessary to conduct analysis and research on the structural response of the water landing panel of a water surface aircraft under different water landing and wave impact loads to ensure that the water landing structure meets the design and airworthiness requirements.

[0003] In current research and tests, model tests or actual flight tests are mainly used to measure the wave impact loads of surface vehicles. In model tests, a surface vehicle model of a certain scale is established, and the water entry and wave impact processes of the vehicle are simulated in a pool to obtain relevant load data. In actual flight tests, sensors are used to measure the loads during water entry and the load-bearing conditions of the vehicle's panel structure are observed during the water landing process of the vehicle. However, both of these test methods have certain limitations. Model tests of surface vehicles are usually carried out in a pool of a certain scale, and the actual water surface conditions are simulated by adjusting water flow, waves, etc. However, due to the extremely complex factors such as the type, height, speed of waves, and the attitude and speed of surface vehicles, existing pools are limited by their boundary reflection problems and often difficult to truly reproduce the dynamic process of a surface vehicle during water entry and wave impact. In addition, there is a scale effect in model tests, that is, the size ratios between the model and the actual vehicle are different, which may lead to certain deviations between the experimental results and the actual situation. Although flight tests can obtain more real load data, due to the extremely complex environment faced by the vehicle during the test, flight tests are restricted by various factors such as weather and sea conditions. Moreover, flight tests usually require a long time for preparation, high costs, and it is difficult to conduct comprehensive tests on the water entry loads under different water surface conditions in a short time. In addition, some extreme situations in flight tests may be difficult to replicate through conventional flight operations, resulting in the inability to accurately evaluate the performance of the vehicle in special environments.

[0004] Therefore, the present invention provides a panel impact test device and test method for simulating water entry loads. Summary of the Invention

[0005] Technical Problems to be Solved:

[0006] In order to avoid the deficiencies of the prior art, the present invention provides a panel impact test device and test method for simulating water entry loads. The dynamic water loads on the water entry panel structure of a surface vehicle are simulated and impacted by an impact simulation loading device to achieve the simulation effect of the actual water entry and wave impact service scenario and avoid the uncontrollable factors in pool tests. In addition, a test method for simulating the water entry and wave impact loads of a surface vehicle is formed. Through the effective cooperation of a hydraulic pump, an accumulator, a servo valve, and an actuator, the simulation loading of different load-time history curves can be realized, and the test conditions of the panel water load impact and loading can be changed according to the actual water landing service scenario, ensuring the test repeatability and saving the test cost.

[0007] The technical solution of the present invention is: a panel impact test device for simulating water impact load, including a water impact load simulation loading module for generating and simulating the water impact and wave impact load of the test panel. The test panel is fixed by a test fixture tooling module. During the test impact, the real-time monitoring data obtained by the test measurement module is sent to the controller of the water impact and wave impact load simulation loading module to complete the closed-loop control of the dynamic load imitating water impact and wave impact;

[0008] The water impact and wave impact load simulation loading module includes a controller, a hydraulic power unit and a loading unit. The controller compares the experimental data of the real water impact and wave impact load experiment with the real-time simulation data obtained by the test measurement module, converts the obtained difference into an electrical signal and sends it to the hydraulic power unit, and the hydraulic power unit converts the electrical signal into a pressure load for the loading unit to execute the action.

[0009] A further technical solution of the present invention is: the hydraulic power unit includes an oil source, a distributor, an oil accumulator and an electro-hydraulic servo valve group connected by pipelines; the distributor distributes the hydraulic oil provided by the oil source to the input circuit, return circuit of the oil accumulator or the input circuit, return circuit of the electro-hydraulic servo valve group as required to control the flow rate and pressure of each circuit;

[0010] The oil accumulator is used to store hydraulic oil and provide supplementary pressure or flow rate during the pressure fluctuation of the electro-hydraulic servo valve group or short-term demand peaks; or ensure that the electro-hydraulic servo valve can obtain the required oil pressure in a timely manner under high dynamic or high load conditions;

[0011] The electro-hydraulic servo valve group includes a first electro-hydraulic servo valve, a hydraulic damper and a second electro-hydraulic servo valve connected in series in sequence, and its control circuits are in parallel to ensure the step-by-step adjustment of the hydraulic oil flow rate and pressure and achieve phase synchronization compensation; the first electro-hydraulic servo valve is a two-stage valve with a designed flow rate of 230 L / min for high load peak demands; the second electro-hydraulic servo valve is a two-stage valve with a designed flow rate of 170 L / min for fine adjustment of medium and low load peak demands.

[0012] A further technical solution of the present invention is: the loading unit includes an actuator and a loading punch installed at the loading end through a spherical hinge. The flexible connection between the two and the freedom compensation and dynamic attitude adjustment of the loading punch are realized through the spherical hinge, which can avoid stress concentration or structural damage caused by rigid connection and ensure that the load is accurately transmitted to the panel along the preset direction;

[0013] The loading surface of the loading punch is opposite to the preset impact position of the experimental panel, and a flexible loading pad for protection is arranged between the two; during impact loading, the experimental panel may generate instantaneous angular offset due to deformation or vibration. The attitude of the loading punch is adjusted in real time through the multi-degree-of-freedom characteristics of the spherical hinge to maintain vertical contact with the loading surface of the panel and avoid interference of lateral component forces on the test data.

[0014] A further technical solution of the present invention is that the specific control method of the controller is as follows:

[0015] Load the preset water-impact load-time history curve into the controller and set the target load waveform;

[0016] Select the corresponding control mode according to the change rate of the target waveform; the control modes include M1 mode, M2 mode, M3 mode, and M4 mode; for the M1 mode with a peak load of 80 - 100 kN: the opening ranges of both electro-hydraulic servo valves are 0 - 100%, the synchronization error ≤ 5 ms, the accumulator instantaneously releases flow, and the oil pump replenishes pressure at high flow; for the M2 mode with a peak load of 20 - 80 kN and a high change rate: the opening of the first valve is 0 - 100%, the opening of the second valve is 80 - 100%, and the synchronization error ≤ 5 ms; for the M3 mode with a peak load of 20 - 80 kN and a low change rate: the opening of the first valve is 0 - 100%, and the second valve remains fully open at 100%; for the M4 mode with a peak load of 0 - 20 kN: the first valve remains fully open at 100%, and the opening of the second valve is 0 - 100%.

[0017] Synchronously adjust the opening degrees of the first electro-hydraulic servo valve and the second electro-hydraulic servo valve through the PID control method, and combine the energy of the instantaneous release of flow of the oil accumulator to control the load waveform output by the actuator;

[0018] Real-time monitor the difference between the feedback value of the actuator force sensor and the target value, and limit the error within the allowable range through PID closed-loop control;

[0019] Safely monitor the oil temperature and vibration signals. If the oil temperature > 65 °C lasts for 60 seconds or the vibration > 5 mm / s lasts for 10 seconds, trigger an emergency shutdown.

[0020] A further technical solution of the present invention is that the test fixture tooling module is used to fix the panel, and includes a first base at the bottom and a second base, columns, a cross beam, and a panel support structure installed thereon;

[0021] The second base is installed on the upper surface of the first base through a T-slot and a T-nut, and can adjust the installation position of the panel;

[0022] The cross beam is installed above the second base through two symmetrically arranged columns, is used to fix the fixed end of the actuator, and adjusts the height position of the actuator by adjusting the installation position on the columns vertically;

[0023] The wall panel support structure includes an end clamping component and a vertical support component. Both ends of the wall panel are integrally connected to the potting end housing by potting, and the potting end housings at both ends are respectively fixedly connected to the symmetrically arranged vertical support components on both sides through the clamping components; the vertical support components are installed on the upper surface of the second base through T-shaped grooves and T-shaped nuts.

[0024] A further technical solution of the present invention is that the test measurement module is used to collect impact data, including a strain gauge array, an accelerometer array, a centralized dynamic strain collector, a laser displacement sensor array, a CAN data acquisition module, a CAN analyzer, and a computer.

[0025] The strain gauge array and the accelerometer array are installed on the surface of the wall panel according to the test requirements and are connected to the centralized dynamic strain collector through a collection circuit.

[0026] The centralized dynamic strain collector has multiple data acquisition channels to meet the test data acquisition requirements.

[0027] The laser displacement sensor array is installed below the wall panel, and the laser irradiation site is the position where the displacement change of the wall panel to be monitored is required. The initial value of the laser displacement should be as close as possible to the displacement monitoring upper limit.

[0028] The CAN data acquisition module is responsible for receiving the measurement data from the laser displacement sensor array and converting it into a format suitable for further processing.

[0029] The CAN analyzer, as an analysis tool, is used to monitor and analyze the data stream transmitted through the CAN bus and further convert the data signal transmitted through the CAN bus into a data signal transmitted through a USB cable.

[0030] The computer is connected to the centralized dynamic strain collector through an optical fiber and is used to acquire, record, and store the strain and acceleration signals generated by the test.

[0031] The computer is connected to the CAN analyzer through a USB cable and is used to acquire, record, and store signals such as displacement generated by the test; it is connected to the controller through an optical fiber and is used to control the operation of each electromechanical component of the testing machine to ensure the normal function of the test.

[0032] A method for simulating the water impact test of a wall panel, the specific steps are as follows:

[0033] Install the wall panel and fix it to the test fixture tooling module, and adjust the loading punch to align with the preset impact position of the wall panel.

[0034] Input a preset load-time history curve through the controller, and perform a preloading of 10% of the water impact load simulation data to calibrate the parameters;

[0035] Load in stages proportionally step by step and perform real-time data acquisition; the loading ratios are 20%, 30%, 50%, 75%, 100%, and 150% of the water impact load simulation data respectively;

[0036] Use the hydraulic accumulator to instantaneously supplement high-pressure hydraulic oil to achieve the accurate reproduction of high-amplitude and high-frequency response impact loads;

[0037] Compare the error between the input and output data, and adjust the control parameters until the error is less than 5%;

[0038] After completing the test, save the data and disassemble the test piece.

[0039] A further technical solution of the present invention is: in the staged loading:

[0040] Under the high load peak of 80 - 100 kN, control the flow rates of the first and second electro-hydraulic servo valves simultaneously;

[0041] Under the medium load peak of 20 - 80 kN, the first electro-hydraulic servo valve mainly controls the flow rate, and the second valve assists in adjusting;

[0042] Under the low load peak of 0 - 20 kN, only the second electro-hydraulic servo valve controls the flow rate.

[0043] A further technical solution of the present invention is: the data acquisition includes:

[0044] Monitor the strain distribution on the surface of the panel through the strain gauge array;

[0045] Record the displacement of the skin center point of the panel through the laser displacement sensor array;

[0046] Capture the dynamic response characteristics through the accelerometer array;

[0047] Real-time feedback of the loading data through the force sensor and displacement sensor built in the actuator.

[0048] A further technical solution of the present invention is: the controller adopts PID closed-loop control, with a frequency range of 0.01 - 100 Hz, and supports multi-valve phase synchronization compensation.

[0049] Beneficial effects

[0050] The beneficial effects of the present invention are as follows: through the optimization of the hydraulic system, flexible connection design, intelligent control strategy and modular tooling, the present invention realizes the high-fidelity simulation of the water impact load of the water surface aircraft, and has the advantages of high precision, high reliability and low cost, providing an efficient test platform for the structural safety assessment of the aircraft. The specific advantage analysis is as follows:

[0051] 1. The present invention consists of a large-flow electro-hydraulic servo valve and a small-flow electro-hydraulic servo valve to form an electro-hydraulic servo valve group. The large-flow valve preferentially meets the requirements of high load amplitudes, while the small-flow valve supplements the load amplitude and fine control. Combining the parallel circuit and phase synchronization compensation technology, it realizes the multi-level regulation of hydraulic oil, meets the high-precision flow control requirements of hydraulic actuators under different load amplitudes (0 - 100 kN) and load non-linearity degrees, and breaks through the performance bottleneck of traditional single-valve systems under high amplitude and high frequency response requirements.

[0052] At the same time, a high-pressure hydraulic oil is pre-stored in the accumulator, and high-flow and high-pressure hydraulic oil (≥400 L / min) can be instantaneously released when an impact command is issued, making up for the defect of insufficient pump flow, ensuring the stability of high-dynamic loading, and controlling the error within 5%.

[0053] 2. The actuator cylinder is connected to the loading punch through a ball joint, allowing the loading punch to rotate freely, compensating for installation errors and panel deformations during dynamic impacts, avoiding interference from lateral component forces, ensuring that the load direction is perpendicular to the panel contact, and improving the authenticity of test data. The flexible loading pad (foamed rubber material) evenly distributes the impact load, reduces local stress concentration, and simulates the dynamic response characteristics of real water on the panel. Through the combined action of software and hardware, the present invention takes into account the high amplitude and high frequency response loading requirements of the water impact load time history curve of a surface aircraft, and can achieve high-precision simulation from low-amplitude and low-frequency response wave loads to high-amplitude and high-frequency response water impact loads, achieving a balance between test cost and performance.

[0054] ·3. Through reasonable design of tooling fixtures, and by using components such as actuator cylinders and sealing devices made of high-strength metal materials and wear-resistant coatings, the present invention can ensure that the test device has good structural rigidity and strength and can withstand repeated impact loads. Through designs such as T-bolts and T-slots, parameters such as the test piece to be loaded, the loading area, the loading method, and the loading speed can be adjusted according to different test requirements, with high flexibility and the ability to adapt to different types of test scenarios and load waveforms.

[0055] 4. Through the combination of multiple sensor arrays, the present invention can collect and store key data such as the structural deformation, strain, impact load, acceleration, and displacement of the panel in real time, ensuring the effectiveness and comprehensiveness of test data.

[0056] 5. The present invention calibrates the load control parameters of the testing machine through preloading tests to ensure the simulation accuracy of the water impact load during formal loading.

[0057] 6. The present invention can fully simulate the water impact loads of different intensities through PID closed-loop control and multi-valve phase synchronization compensation (frequency range 0.01 - 100 Hz), combined with preloading calibration (10% ratio), and gradually increasing the load proportionally during the loading process (20%, 30%, 50%, 75%, 100%, 150%), making the test conditions closer to the actual working conditions. This loading method can effectively evaluate the performance of the panel under different load levels.

[0058] 7. In the test, through multiple calibrations and clearings, the error between the input data and the output data is ensured to be controlled within the allowable range, avoiding the influence of systematic errors on the test results. After the test, it is confirmed that there is no abnormality in the test piece and the valid data is saved, further improving the reliability of the test results. Description of the Drawings

[0059] Figure 1 Schematic assembly diagram of the overall structure of a panel impact test device for simulating water impact loads in an embodiment of the present invention;

[0060] Figure 2 Schematic diagram of the two-frame and five-stringer panel structure in an embodiment of the present invention;

[0061] Figure 3 Schematic assembly diagram of the panel and the panel support structure in an embodiment of the present invention;

[0062] Figure 4 Schematic diagram of the oil source structure in an embodiment of the present invention;

[0063] Figure 5 Schematic diagram of the T-slot and T-nut of the first base in an embodiment of the present invention;

[0064] Figure 6 Schematic diagram of the oil accumulator structure in an embodiment of the present invention;

[0065] Figure 7 Schematic diagram of the loading punch structure in an embodiment of the present invention;

[0066] Figure 8 Oil flow diagram of the electro-hydraulic servo valve group in an embodiment of the present invention;

[0067] Figure 9 Comparison diagram of the water impact load loading curves in an embodiment of the present invention;

[0068] Description of reference numerals: 101 - Controller, 102 - Oil source, 103 - Oil distributor, 104 - Oil accumulator, 105 - Electro-hydraulic servo valve group, 106 - Actuator, 107 - Ball joint, 108 - Loading punch, 109 - Loading pad, 201 - First base, 202 - Second base, 203 - First column, 204 - Second column, 205 - Cross beam, 206 - Wall panel, 207 - Wall panel support structure, 301 - Strain gauge array, 302 - Accelerometer array, 303 - Centralized dynamic strain acquisition instrument, 304 - Laser displacement sensor array, 305 - CAN data acquisition module, 306 - CAN analyzer, 307 - Electronic computer, 2061 - Encapsulation end extension, 2062 - Skin, 2063 - Longeron, 2064 - Frame, 2065 - Encapsulation end housing, 2066 - Encapsulation adhesive, 2067 - Encapsulation end extension through hole, 2071 - First end clamping component, 20711 - First end clamping component bottom through hole, 20712 - First end clamping component side through hole, 2072 - Second end clamping component, 2073 - First vertical support component, 2074 - Second vertical support component, 1021 - Oil pump, 1022 - Oil tank, 1023 - Cooling system, 1024 - Oil source housing, 1025 - Control circuit and panel, 1026 - Lifting lug, 2011 - First base T-slot, 2012 - First base T-nut, 1041 - High-pressure oil accumulator, 1081 - Loading punch upper flat plate, 1082 - Loading punch lower flat plate, 1083 - Loading punch stiffener. Detailed implementation manners

[0069] The embodiments described below by referring to the accompanying drawings are exemplary and are intended to explain the present invention, and should not be construed as limiting the present invention.

[0070] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention.

[0071] When designing the impact test device and test method for simulating the impact load of a water surface aircraft during water landing and wave hitting, for some existing technical solutions, their main disadvantages are as follows:

[0072] (1) The verification of the water impact bearing performance of traditional water surface aircraft is carried out through model tests and other methods. Its cost is relatively high, and the pool test method is affected by boundary reflection and cannot correctly reflect the load and dynamic response characteristics of the structure.

[0073] (2) There are two general methods for simulating water loads: the multi-point coupling lever loading technology and the airbag loading technology. The multi-point coupling lever loading technology for the bottom structure of amphibious aircraft can only load the water load on the bottom of the ship through actuators, and can only load static loads, which cannot meet the high loading speed, high impact energy and non-linear loading requirements of impact dynamic load loading. Moreover, the test loading lever system is very complex and the test cost is huge.

[0074] (3) For the airbag loading technology, a closed metal container is needed to restrict the expansion of the airbag outside the load acting area. However, the bonding process between the airbag and the metal container is difficult to accurately control. At the same time, the airbag is prone to problems such as air leakage and poor followability under high loading pressure, and it is difficult to meet the requirements of wall panel water load simulation. At the same time, the out-of-plane airbag loading also cannot meet the high loading speed, high impact energy and non-linear loading requirements of the instantaneous load when the water surface aircraft lands on the water.

[0075] (4) General impact simulation loading devices are divided into electric actuators and electro-hydraulic servo actuators. Electric actuators generally have complex structures and high costs, and are not practical enough in the loading scenarios of large-sized test pieces. The electro-hydraulic servo actuator controlled by a traditional single-stage electro-hydraulic servo valve may have problems such as untimely response and inability to reach the amplitude, and it is difficult to meet the requirements of wall panel water load simulation.

[0076] (5) Although some current dynamic loading devices for simulating sea conditions use accumulators to supply energy for the loading device and can achieve dynamic slamming load loading, the pneumatic impact cylinders they commonly use have inherent problems such as low upper limit of impact force and slow impact response, and cannot meet the impact load loading characteristics of "high amplitude, high frequency response, and highly non-linear" when the water surface aircraft lands on the water; at the same time, the pneumatic system is restricted by the compressibility of gases and is difficult to accurately reproduce the water impact waveform; in addition, the pneumatic impact cylinder has certain shortcomings in environmental adaptability, and its performance is greatly affected by temperature.

[0077] In order to better simulate the impact of the water surface aircraft landing on the water and hitting the waves, a new test device needs to be designed, which can more accurately reproduce the load changes of the water surface aircraft under different waves, different water flows and different impact angles. The test device should have the following key technical requirements:

[0078] (1) The test device needs to be able to simulate the complex wave impact loads encountered by the aircraft during water landing, especially in the case of large wave variations and high aircraft speeds, and be able to provide high-precision load data to ensure that it can truly reflect the extreme conditions encountered by the aircraft in the water environment.

[0079] (2) Since the wave impact load usually has a high instantaneous impact force, the test device must have good structural rigidity and strength, be able to withstand repeated impact loads without malfunction or failure. Especially in the high-load environment when simulating the contact between the aircraft and the water surface, the test device must have strong durability.

[0080] (3) The test device needs to have an accurate control system so that it can accurately simulate the water landing angle, water landing speed, load distribution of the aircraft, and the sea conditions during water entry during the test, ensuring that the implementation of each test has the characteristics of flexibility and repeatability.

[0081] (4) The test device should also be equipped with an advanced data acquisition and analysis system, which can monitor the load-bearing situation of the water surface aircraft's water landing panel structure during the wave impact process in real time, especially the load changes and dynamic response characteristics acting on the key parts of the structure, and evaluate the anti-impact performance and structural safety of the aircraft by analyzing these data.

[0082] Therefore, the present invention proposes a panel impact test device for simulating water landing loads, including a water impact load simulation loading module for generating and simulating the water impact loads of the test panel. The test panel is fixed by a test fixture tooling module. During the test impact process, the real-time monitoring data obtained is sent to the controller of the water impact load simulation loading module through the test measurement module to complete the closed-loop control of imitating the dynamic loads during water impact. The water impact load simulation loading module includes a controller, a hydraulic power unit, and a loading unit. The controller compares the experimental data of the real water impact load experiment with the real-time simulation data obtained by the test measurement module, converts the obtained difference into an electrical signal and sends it to the hydraulic power unit, and the hydraulic power unit converts the electrical signal into a pressure load for the loading unit to execute the action.

[0083] Specifically, the test fixture tooling module includes a first base, a second base, a first column, a second column, a cross beam, a panel, and a panel support structure;

[0084] The first base is installed parallel to the ground, and its vertical projection area on the ground is larger than the sum of the vertical projection areas of the second base, the cross beam, the first column, and the second column on the ground. The material should be cast iron or other alloy materials. Its upper surface and lower surface are both parallel to the ground, and parallel T-shaped grooves are evenly engraved on its upper surface;

[0085] The outer edge at the bottom surface of the second base is fixed to the upper surface of the first base through T-bolts and T-grooves. Its vertical projection area on the ground is larger than that of the wall panel support structure. Its upper surface and lower surface are both parallel to the upper surface of the first base, and its upper surface is evenly engraved with parallel T-grooves.

[0086] The wall panel support structure includes a first end clamping component, a second end clamping component, a first vertical support component, and a second vertical support component.

[0087] The wall panel is composed of a skin, a plurality of stringers, and a plurality of frames. Among them, the skin and the stringers are arranged in parallel, and both ends of the skin and both ends of the stringers are respectively connected to two metal outer frames through potting glue to ensure the stability of the structure. The connection body of the potting glue and the metal outer frame is called the potting end. The frames are located in the middle of the skin and the stringers, connecting the two to form a stable overall framework, and clamping end connection parts are extended at both metal outer frames.

[0088] The first end clamping component and the second end clamping component have high rigidity, are both fixedly connected to the clamping end connection parts at the potting ends of the wall panel, and are respectively fixedly connected to the first vertical support component and the second vertical support component.

[0089] The first vertical support component and the second vertical support component have high rigidity, are fixed to the upper surface of the second base through T-bolts and T-grooves, and finally ensure that the skin of the wall panel is parallel to the upper surface of the second base and is facing the loading punch.

[0090] The bottoms of the first column and the second column are fixedly installed on the second base through mechanical connectors and are located on both sides of the wall panel support structure.

[0091] Both ends of the cross beam are slidably installed between the first and second columns. After installation, the axis is parallel to the wall panel plane, the height is higher than the wall panel, and it is fixed through mechanical connectors.

[0092] Specifically, the water impact and wave load simulation loading module includes a controller, an oil source, an oil distributor, an oil accumulator, an electro-hydraulic servo valve group, an actuator, a spherical hinge, a loading punch, and a loading pad.

[0093] The fixed end of the actuator is fixedly installed at the middle position of the cross beam, with the direction perpendicular to the ground downward, and the loading end is located below the fixed end.

[0094] The actuator consists of a housing, a piston, a piston rod, a force sensor and a displacement sensor, a hydraulic oil pipe, and a sealing device. Among them,

[0095] The outer shell is usually a long cylindrical structure, typically made of high-strength metal materials, mainly used to bear the internal pressure and protect the internal components. The inner surface of the outer shell is coated with a wear-resistant coating to reduce friction and ensure the service life of the actuator cylinder;

[0096] The piston is located inside the actuator cylinder and moves within the inner cavity of the actuator cylinder. It is usually made of metal alloy. One side of the piston pushes the load inside the actuator cylinder through the pressure of hydraulic oil, while the other side is connected to the control circuit of the hydraulic system;

[0097] The piston rod connects the piston to the external structure. When the piston moves inside the actuator cylinder, the piston rod also moves accordingly. The piston rod is usually made of corrosion-resistant and wear-resistant materials;

[0098] The displacement sensor is installed inside the actuator cylinder to monitor the position of the piston rod, thereby providing position feedback to ensure precise control;

[0099] The force sensor is installed at the loading end of the actuator cylinder to monitor the reaction force load at the loading end in real time;

[0100] The hydraulic oil pipe is used to connect the electro-hydraulic servo valve to the hydraulic cavity of the actuator cylinder and provide hydraulic fluid through an oil pump;

[0101] The sealing device is mainly installed between the piston and the actuator cylinder wall to prevent hydraulic oil leakage and prevent external contaminants from entering;

[0102] A spherical hinge is installed at the lower loading end of the actuator cylinder to achieve a flexible connection between the actuator cylinder and other components. It consists of a spherical joint and a corresponding hinge seat and can rotate freely in multiple directions, allowing relative angular changes between the connected components;

[0103] The loading punch is fixedly installed at the lower end of the spherical hinge. The lower surface is a plane, and its area is equal to the area of the preset loading area of the test. The impact position is aligned with the preset impact position of the wall panel;

[0104] A loading pad is arranged between the loading punch and the wall panel. The loading pad is made of a flexible material, and its area is greater than or equal to the area of the preset loading area of the test according to the test requirements;

[0105] The electro-hydraulic servo valve group is installed outside the actuator cylinder and precisely adjusts the working state of the hydraulic system through electrical signals. It is responsible for controlling the flow rate and flow direction of the hydraulic oil entering the actuator cylinder, thereby controlling the movement of the piston;

[0106] The electro-hydraulic servo valve group consists of a first electro-hydraulic servo valve, a second electro-hydraulic servo valve, and a hydraulic damper. Among them,

[0107] The first electro-hydraulic servo valve and the second electro-hydraulic servo valve are both two-stage valves. The designed flow rate of the first electro-hydraulic servo valve is greater than that of the second electro-hydraulic servo valve. The hydraulic oil circuits are in series, and the control circuits are in parallel, ensuring the step-by-step adjustment of the hydraulic oil flow rate and pressure, achieving more precise control and smoother operation to handle the realization of complex load waveforms;

[0108] The first electro-hydraulic servo valve includes a hydraulic amplifier composed of an electro-mechanical converter, a pilot-stage valve, and a power main valve, as well as a feedback mechanism. The electro-mechanical converter converts an electrical signal into an output force signal, which is then converted by an elastic component into a displacement beam that drives the pilot-stage valve to move, positioning and returning the pilot-stage valve to zero. The pilot-stage valve is a nozzle-flapper type pilot-stage valve, which controls the flow rate by changing the opening degree of the liquid flow path, and further controls the output load of the loading system. The power-stage main valve adopts a four-edge spool valve structure and works based on the throttling principle. By means of the relative movement between the spool and the valve body, the throttling port flow area is changed to control the liquid flow rate and pressure above 230 L / min. The feedback mechanism installed inside the valve feeds back the pressure, flow rate, or spool displacement of the pilot valve or the power-stage main valve control port to the input end of the pilot-stage valve or the input end of the proportional amplifier, realizing the comparison between the input and output, solving the positioning problem of the power-stage main valve, and obtaining the required servo valve pressure-flow performance. The oil inlet of the first electro-hydraulic servo valve is directly connected to the output end of the oil accumulator. The working oil port of the first electro-hydraulic servo valve is connected in series to the oil inlet of the second electro-hydraulic servo valve through a hydraulic damper. The oil return port of the first electro-hydraulic servo valve and the oil return port of the second electro-hydraulic servo valve are connected in parallel to the oil source;

[0109] The second electro-hydraulic servo valve includes a hydraulic amplifier composed of an electro-mechanical converter, a pilot-stage valve, and a power main valve, as well as a feedback mechanism. The electro-mechanical converter converts an electrical signal into an output force signal, which is then converted by an elastic component into a displacement beam that drives the pilot-stage valve to move, positioning and returning the pilot-stage valve to zero. The pilot-stage valve is a nozzle-flapper type pilot-stage valve, which controls the flow rate by changing the opening degree of the liquid flow path, and further controls the output load of the loading system. The power-stage main valve adopts a cone valve structure, and the conical surface seal realizes the fine control of the 170 L / min flow rate. The axial displacement of the spool is accurately adjusted by the differential pressure output by the pilot stage. The feedback mechanism installed inside the valve feeds back the pressure, flow rate, or spool displacement of the pilot valve or the power-stage main valve control port to the input end of the pilot-stage valve or the input end of the proportional amplifier, realizing the comparison between the input and output, solving the positioning problem of the power-stage main valve, and obtaining the required servo valve pressure-flow performance. The oil inlet of the second electro-hydraulic servo valve is connected in series to the working oil port of the first electro-hydraulic servo valve. The working oil port of the second electro-hydraulic servo valve is directly connected to the inlet / return oil cavity of the actuator. The oil return port of the second electro-hydraulic servo valve and the oil return port of the first electro-hydraulic servo valve share a pipeline to connect to the oil source;

[0110] The hydraulic damper is placed between the first electro-hydraulic servo valve and the second electro-hydraulic servo valve, and is connected in series in the high-pressure pipeline between the working oil port of the first electro-hydraulic servo valve and the oil inlet of the second electro-hydraulic servo valve, and is used to absorb the pressure oscillation caused by the sudden change of flow rate;

[0111] The hydraulic damper is a cylindrical pulsation damper, and its specific structure includes: an outer cylinder body, an elastic damping element and a pressure balance valve. The outer cylinder body is forged from 316L stainless steel, and hemispherical heads are welded at both ends. The overall pressure resistance level is greater than or equal to 35 MPa. The elastic damping element is placed in the inner cavity of the outer cylinder body and is composed of a baffle and a spring element. The baffle divides the inner cavity of the outer cylinder body into an oil chamber communicating with the system oil circuit and a nitrogen chamber filled with nitrogen. The pre-charged pressure in the nitrogen chamber is 10 MPa. The pressure balance valve is arranged at the end of the nitrogen chamber and is used to regularly supplement nitrogen or release overpressure gas;

[0112] The hydraulic damper can ensure the reduction of the amplitude of the oil circuit pressure fluctuation during the load pulse process within the peak frequency of 5 Hz of the pulse curve loaded by the electro-hydraulic servo valve group, and improve the smoothness of the inlet pressure of the second electro-hydraulic servo valve. The main working principle is: during the process of the increase of the oil chamber pressure, the gas in the nitrogen chamber is compressed and stored for energy, regulating the pressure rising rate; during the process of the decrease of the oil chamber pressure, the nitrogen chamber expands and releases the stored energy to maintain the stability of the oil circuit pressure;

[0113] The hydraulic damper can release the gas in the nitrogen chamber during the load pulse process with a peak frequency of more than 5 Hz of the pulse curve loaded by the electro-hydraulic servo valve group, ensure the passage between the first electro-hydraulic servo valve and the second electro-hydraulic servo valve, and ensure the high sensitivity of the control of the electro-hydraulic servo valve group;

[0114] The oil accumulator is connected to the electro-hydraulic servo valve through a pipeline, and is used to store hydraulic oil and provide supplementary pressure or flow during the system pressure fluctuation or short-term demand peak. Especially under high-dynamic or high-load conditions, it ensures that the electro-hydraulic servo valve can obtain sufficient oil pressure in time. Specifically: before the test, the controller starts the oil pump to pre-charge the high-pressure oil to the set pressure in the oil accumulator, and real-time monitors the pressure of the accumulator through a pressure sensor. When the pressure reaches the target value, the oil pump switches to the standby mode, and the accumulator enters the pressure-holding state, reducing the energy consumption and temperature rise of the oil pump. When the controller receives the impact command, it controls the proportional valve at the outlet of the oil accumulator to open instantaneously, and the pre-stored high-pressure oil is directly supplied to the electro-hydraulic servo valve group through the pipeline. At the same time, the oil pump synchronously supplements the flow to ensure that the instantaneous flow peak value ≥ 400 L / min;

[0115] The oil distributor is connected to the oil accumulator through a pipeline, and by adjusting the oil distributor, the oil flow or pressure of each circuit can be controlled;

[0116] The oil source is connected to the oil distributor through a pipeline. The oil source consists of three parts: a fuel tank, a cooling system, and an oil pump. In the system, the oil pump extracts the hydraulic oil from the fuel tank and transports the pressurized oil to the inlet of the oil distributor through a pipeline or an oil circuit. The cooling system cools down other components;

[0117] The controller is connected to the electro-hydraulic servo valve, the oil source, the oil distributor, and the oil accumulator through a control circuit. Among them,

[0118] The controller is responsible for generating electrical signals to regulate the opening and closing of the electro-hydraulic servo valve or adjust control parameters such as the flow rate and pressure of the valve, thereby controlling the operation of the hydraulic actuator. For load-time history curves with different peak values and frequency response loading requirements, the control method is as follows: For non-linear load-time history curves with high load peak requirements of 80 - 100 kN, the controller simultaneously controls the first and second electro-hydraulic servo valves for flow control. The controller simultaneously transmits phase control electrical signals to the first and second electro-hydraulic servo valves. The motors inside the first and second electro-hydraulic servo valves control the change in the valve opening. The control signals of the two valves achieve phase synchronization compensation inside the controller, thereby controlling the working flow rate and further controlling the change in the working oil pressure inside the actuator, so as to achieve the loading of non-linear load-time history curves with high load peak requirements of 80 - 100 kN; For medium load peak requirements of 20 - 80 kN, for highly non-linear loads with a peak frequency of the curve greater than 20 Hz and an irregular geometric shape, the controller controls the first electro-hydraulic servo valve for flow control, while the second electro-hydraulic servo valve provides fine adjustment. The controller simultaneously transmits phase control electrical signals to the first and second electro-hydraulic servo valves. The motors inside the first and second electro-hydraulic servo valves control the change in the valve opening. The valve opening threshold of the first electro-hydraulic servo valve is 0% - 100%, and the valve opening threshold of the second electro-hydraulic servo valve is 80% - 100%. The adjustment step of the second electro-hydraulic servo valve is smaller than that of the first electro-hydraulic servo valve. The control signals of the two valves achieve phase synchronization compensation inside the controller, thereby controlling the working flow rate and further controlling the change in the working oil pressure inside the actuator, so as to achieve the loading of highly non-linear load-time history curves under medium load peak requirements of 20 - 80 kN; For medium load peak requirements of 20 - 80 kN, for simple loads with a peak frequency of the curve less than 20 Hz or a regular geometric shape, the controller controls the first electro-hydraulic servo valve for flow control. The controller transmits the phase control electrical signal to the first electro-hydraulic servo valve. The motor inside the first electro-hydraulic servo valve controls the change in the valve opening. The valve opening threshold of the first electro-hydraulic servo valve is 0% - 100%, while the second electro-hydraulic servo valve remains open, that is, the opening remains 100%, thereby controlling the working flow rate and further controlling the change in the working oil pressure inside the actuator, so as to achieve the loading of simple load-time history curves with a peak frequency of the curve less than 20 Hz or a regular geometric shape under medium load peak requirements of 20 - 80 kN; For low load peak requirements of 0 - 20 kN, the controller controls the second electro-hydraulic servo valve for flow control. The controller transmits the phase control electrical signal to the second electro-hydraulic servo valve. The motor inside the second electro-hydraulic servo valve controls the change in the valve opening. The valve opening threshold of the first electro-hydraulic servo valve is 0% - 100%, while the first electro-hydraulic servo valve remains open, that is, the opening remains 100%, thereby controlling the working flow rate and further controlling the change in the working oil pressure inside the actuator, so as to achieve the loading of various load-time history curves under low load peak requirements of 0 - 20 kN;Meanwhile, in the above working conditions, when the controller determines that the local load loading rate exceeds the set 375 kN / s, it controls the hydraulic accumulator to instantaneously supplement high-pressure hydraulic oil; through this multi-stage control method, it is ensured that the hydraulic actuator can accurately reproduce the impact load-time history curve within a wide range of load peaks, frequencies, and shapes applied.

[0119] The controller is connected to the hydraulic accumulator through a control circuit, and adjusts the working state of the accumulator according to factors such as the pressure change of the system, load demand, and loading frequency to ensure that the system pressure is within a suitable range to cope with load changes or avoid excessive or too low pressure.

[0120] The controller is connected to the oil distributor through a control circuit, and the oil distributor distributes the hydraulic oil provided by the oil source to the oil source return hydraulic circuit or the hydraulic accumulator input hydraulic circuit according to the instructions of the controller.

[0121] The controller is connected to the oil source through a control circuit, controls the start-stop, flow rate, and pressure of the oil pump to provide the required hydraulic oil power, and controls the switch and cooling intensity of the cooling system of the oil source to meet the oil source temperature control requirements.

[0122] The controller communicates with the electronic computer through optical fiber to meet the control, display, and recording requirements.

[0123] Specifically, the test measurement module includes a strain gauge array, an accelerometer array, a centralized dynamic strain collector, a laser displacement sensor array, a CAN data acquisition module, a CAN analyzer, and an electronic computer.

[0124] The strain gauge array and the accelerometer array are pasted and installed on the surface of the wall panel according to the test requirements and are connected to the centralized dynamic strain collector through a collection circuit.

[0125] The centralized dynamic strain collector has multiple data acquisition channels to meet the test data acquisition requirements.

[0126] The laser displacement sensor array is installed below the wall panel, and the laser irradiation site is the position where the displacement change of the wall panel to be monitored is located. The initial value of the laser displacement should be as close as possible to the upper limit of displacement monitoring.

[0127] The CAN data acquisition module is responsible for receiving the measurement data from the laser displacement sensor array and converting it into a format suitable for further processing.

[0128] The CAN analyzer, as an analysis tool, is used to monitor and analyze the data stream transmitted through the CAN bus and further convert the data signal transmitted through the CAN bus into a data signal transmitted through the USB cable.

[0129] The electronic computer is connected to the centralized dynamic strain acquisition instrument through an optical fiber, and is used to acquire, record, and store signals such as strain and acceleration generated by the test;

[0130] The electronic computer is connected to the CAN analyzer through a USB cable, and is used to acquire, record, and store signals such as displacement generated by the test;

[0131] The electronic computer is connected to the controller through an optical fiber, and is used to control the operation of each electromechanical component of the testing machine to ensure the normal function of the test;

[0132] At the same time, a panel impact test method for simulating the water impact load is proposed, and the specific steps are as follows:

[0133] Step 1: Install the panel and fix it on the test fixture tooling module, and adjust the loading punch to align with the preset impact position of the panel;

[0134] Step 2: Input the preset load-time history curve through the controller, and perform a preloading of 10% of the water impact load simulation loading data to calibrate the parameters;

[0135] Step 3: Gradually load in stages according to a ratio, and perform real-time data acquisition; the loading ratios are 20%, 30%, 50%, 75%, 100%, and 150% of the water impact load simulation loading data respectively;

[0136] Step 4: Use the oil hydraulic accumulator to instantaneously supplement high-pressure oil to achieve the precise reproduction of high-amplitude and high-frequency response impact loads;

[0137] Step 5: Compare the error between the input and output data, and adjust the control parameters until the error is less than 5%;

[0138] Step 6: Save the data and disassemble the test piece after the test is completed.

[0139] The above technical solutions will be further described below in conjunction with the embodiments and the drawings:

[0140] In one embodiment, refer to Figure 1As shown in the figure, in this embodiment, a typical two-frame and five-stringer panel structure member is used as the panel test piece. The panel impact test device for simulating water impact load is composed of a water impact wave load simulation loading module, a test fixture tooling module, and a test measurement module. The water impact wave load simulation loading module includes a controller 101, an oil source 102, an oil distributor 103, an oil accumulator 104, an electro-hydraulic servo valve group 105, an actuator 106, a ball joint 107, a loading punch 108, and a loading pad 109. The test fixture tooling module includes a first base 201, a second base 202, a first column 203, a second column 204, a cross beam 205, a panel 206, and a panel support structure 207. The test measurement module includes a strain gauge array 301, an accelerometer array 302, a centralized dynamic strain acquisition instrument 303, a laser displacement sensor array 304, a CAN data acquisition module 305, a CAN analyzer 306, and an electronic computer 307.

[0141] Specifically, the controller 101 adopts a WinPWS full digital hydraulic servo controller to realize the automatic control function of the testing machine. It is configured with a sensor signal conditioning unit for force and displacement, the control mode is PID closed-loop control, the frequency range is 0.01 - 100 Hz, the frequency resolution is 0.01 Hz, and the counter capacity ≥ 10 9Next, one end of the controller 101 is connected to an electronic computer for data recording and control at the electronic computer end. The other end of the controller 101 is connected to an oil source 102, an oil distributor 103, an oil accumulator 104, and an electro-hydraulic servo valve group 105 for controlling, monitoring, and data acquisition of each component. The oil source 102 includes an oil pump 1021, an oil tank 1022, a cooling system 1023, an oil source housing 1024, a control circuit and panel 1025, and a lifting lug 1026. The oil pump 1021 is connected to the oil tank 1022 through an inlet and return oil pipeline. The maximum flow rate of the oil pump 1021 is 50 L / min, and it is installed immersed in oil. The cooling system 1023 cools the inlet and return oil pipelines between the oil pump 1021 and the oil tank 1022 through a cooling water pipeline and a fan. The oil source housing 1024 is made of a lightweight alloy material. The control circuit and panel 1025 are integrally installed at the end of the pump station to achieve electrical control of the pump station system. It is equipped with a servo motor driver, pre / post filters, a pressure sensor, etc., and can achieve pressure feedback adaptive control. The lifting lug 1026 is installed on the side of the oil source housing 1024. The controller 101 is connected to the oil source 102 through a control circuit, which can control the start / stop of the oil source and the oil pumping pressure of the oil source, and monitor necessary information such as liquid level, oil temperature, and oil pressure. The oil distributor 103 serves as a relay station connecting the oil source 102 and the oil accumulator 104, providing the required hydraulic power for the actuator 106. The maximum inlet flow rate of the oil distributor 103 is ≥100 L / min, the maximum pressure is 21 MPa, the filtration accuracy is 3 μm, and the maximum return flow rate is ≥400 L / min. The oil distributor 103 is equipped with a precision oil filter to reduce oil contamination. The controller 101 is connected to the oil distributor 103 through a control circuit. The oil distributor 103 adjusts the flow rate and pressure of the oil according to the signal sent by the controller 101 to ensure that the actuator 106 can be accurately loaded according to the preset control program. The oil accumulator 104 includes a 2.5 L high-pressure accumulator 1041, which meets the requirements of impact tests with large instantaneous flow rates and high speeds, and can provide an instantaneous large flow rate of hydraulic oil ≥400 L / min. The controller 101 is connected to the oil accumulator 104 through a control circuit. The oil accumulator 104 stores and releases oil according to the signal sent by the control 101.

[0142] The specific control method of the controller is to load a preset water impact load-time history curve into the controller to set the target load waveform F target (t). Based on the target load waveform F target (t) and its change rate dF target / dt, a reasonable control mode and control method are selected to control the oil storage and energy storage of the oil accumulator. After the impact command is triggered, based on the feedback value F output (t) of the force sensor installed at the actuator and the difference F of the stress load values between the target load waveform F target (t)error F(t) = F target F(t) - F output F(t), synchronously control the first electro-hydraulic servo valve and the second electro-hydraulic servo valve through the PID control method, control the opening changes of the first electro-hydraulic servo valve and the second electro-hydraulic servo valve, and control the oil accumulator to release flow energy, so as to control the movement of the actuator and output the load waveform F to the wall panel. output F(t), making the difference F error F(t) be controlled within a reasonable error range. At the same time, the controller real-time monitors signals such as oil temperature and vibration through the safety monitoring method and can perform an emergency shutdown.

[0143] The specific control mode is as follows:

[0144] At the peak load (80 - 100 kN), control mode M1 is adopted; at the medium load peak (20 - 80 kN) and the maximum change rate dF target / dt > 200 kN / s, control mode M2 is adopted; at the medium load peak (20 - 80 kN) and the maximum change rate dF target / dt ≤ 200 kN / s, control mode M3 is adopted; at the low load peak (0 - 20 kN), control mode M4 is adopted.

[0145] The specific control mode M1 is as follows: the opening range of the first electro-hydraulic servo valve is set to 0 - 100%, the opening range of the second electro-hydraulic servo valve is set to 0 - 100%, the phase difference of the opening signals of the two valves is calibrated in real time by the controller to ensure that the action synchronization error is less than or equal to 5 ms. At the moment when the controller issues the loading instruction, control the accumulator to instantaneously release the flow to meet the impact requirement, and at the same time control the high-flow pressure compensation of the oil pump. The control method of the first electro-hydraulic servo valve during the loading process can be briefly recorded as:

[0146]

[0147] In the formula, α1(t) is the opening state parameter of the first electro-hydraulic servo valve, t is the current moment, K P 、K I 、K D are the input PID control parameters respectively, t f is the previous sampling moment, and T is the loading period. The control method of the second electro-hydraulic servo valve during the loading process combines the control signal uniformly issued by the controller and the phase signal α1(t) of the first solenoid valve at the previous sampling moment, and can be briefly recorded as:

[0148]

[0149] In the formula, α2(t) is the opening state parameter of the second electro-hydraulic servo valve, e(t f ) = α1(t f) - α2(t f ),K P,2 、K I,2 、K D,2 are the input PID control parameters respectively, and t f is the previous sampling moment.

[0150] The specific control mode M2 is as follows: the opening range of the first electro-hydraulic servo valve is set to 0 - 100%, the opening range of the second electro-hydraulic servo valve is set to 80% - 100%. The controller calibrates the time-delay difference of the opening signals of the two valves in real time to ensure that the action synchronization error is less than or equal to 5 ms. At the moment when the controller issues the loading instruction, the accumulator is controlled to instantaneously release the flow rate to meet the impact requirement, and at the same time, the oil pump is controlled to replenish the pressure with high flow rate. The control method of the first electro-hydraulic servo valve during the loading process is the same as formula (1), and the control method of the second electro-hydraulic servo valve during the loading process can be briefly recorded as:

[0151]

[0152] In the formula, K P,3 、K I,3 、K D,3 、K P,4 、K I,4 、K D,4 are the input PID control parameters respectively.

[0153] The specific control mode M3 is as follows: the opening range of the first electro-hydraulic servo valve is set to 0 - 100%, the opening range of the second electro-hydraulic servo valve is set to 100%. At the moment when the controller issues the loading instruction, the accumulator is controlled to instantaneously release the flow rate to meet the impact requirement, and at the same time, the oil pump is controlled to replenish the pressure with high flow rate. The control method of the first electro-hydraulic servo valve during the loading process is the same as formula (1).

[0154] The specific control mode M4 is as follows: the opening range of the first electro-hydraulic servo valve is set to 100%, the opening range of the second electro-hydraulic servo valve is set to 0 - 100%. At the moment when the controller issues the loading instruction, the accumulator is controlled to instantaneously release the flow rate to meet the impact requirement, and at the same time, the oil pump is controlled to replenish the pressure with high flow rate. The control method of the second electro-hydraulic servo valve during the loading process can be briefly recorded as:

[0155]

[0156] The flow rate adjustment method of the oil pump during the loading process is:

[0157] Q pump = n·V g ·η·ω(t) (5)

[0158] In the formula, Q pump is the output flow rate of the oil pump, n is the pump displacement coefficient, and V g$Q$ is the geometric displacement of the oil pump, $\eta$ is the volumetric efficiency, and $\omega(t)$ is the rotational speed of the oil pump output by the controller.

[0159] The specific safety monitoring method is as follows: During the startup process, the controller monitors signals such as oil temperature and vibration in real time. If the oil temperature in the fuel tank is higher than 65 °C for more than 60 s or the vibration frequency of the loading unit is greater than 5 mm / s and the duration exceeds 10 s, an emergency shutdown will be performed.

[0160] Specifically, the electro-hydraulic servo valve group 105 includes two electro-hydraulic servo valves. The flow rate of the first electro-hydraulic servo valve is 230 L / min, and the flow rate of the second electro-hydraulic servo valve is 170 L / min. The oil circuits between the two electro-hydraulic servo valves are connected in series, and the control circuits between the controller 101 and the two electro-hydraulic servo valves are connected in parallel, which can respectively control the start-stop opening and closing of the two servo valves. The controller 101 is connected to the electro-hydraulic servo valve group 105 through the control circuit, and can drive the combination of the two electro-hydraulic servo valves or a single electro-hydraulic servo valve to act alone, so as to realize the actuator action under different load requirements.Specifically: when the non-linear load-time history curve has a high load peak demand of 80 - 100 kN, the controller simultaneously controls the first and second electro-hydraulic servo valves for flow control. The controller simultaneously transmits the phase control electrical signals to the first and second electro-hydraulic servo valves respectively. The motors inside the first and second electro-hydraulic servo valves control the valve opening changes. The control signals of the two valves achieve phase synchronization compensation in the controller, thereby controlling the working flow rate and further controlling the change of the working oil pressure inside the actuator, so as to achieve the loading of the non-linear load-time history curve with a high load peak demand of 80 - 100 kN; when the medium load peak demand is 20 - 80 kN, for the highly non-linear load with a peak frequency of the curve greater than 20 Hz and an irregular geometric shape, the controller controls the first electro-hydraulic servo valve for flow control, and the second electro-hydraulic servo valve makes supplementary fine adjustments. The controller simultaneously transmits the phase control electrical signals to the first and second electro-hydraulic servo valves respectively. The motors inside the first and second electro-hydraulic servo valves control the valve opening changes. The valve opening threshold of the first electro-hydraulic servo valve is 0% - 100%, and the valve opening threshold of the second electro-hydraulic servo valve is 80% - 100%. The adjustment step of the second electro-hydraulic servo valve is smaller than that of the first electro-hydraulic servo valve. The control signals of the two valves achieve phase synchronization compensation in the controller, thereby controlling the working flow rate and further controlling the change of the working oil pressure inside the actuator, so as to achieve the loading of the highly non-linear load-time history curve under the medium load peak demand of 20 - 80 kN; when the medium load peak demand is 20 - 80 kN, for the simple load with a peak frequency of the curve less than 20 Hz or a regular geometric shape, the controller controls the first electro-hydraulic servo valve for flow control. The controller transmits the phase control electrical signal to the first electro-hydraulic servo valve. The motor inside the first electro-hydraulic servo valve controls the valve opening change. The valve opening threshold of the first electro-hydraulic servo valve is 0% - 100%, while the second electro-hydraulic servo valve remains open, that is, the opening remains 100%, thereby controlling the working flow rate and further controlling the change of the working oil pressure inside the actuator, so as to achieve the loading of the simple load-time history curve with a peak frequency of the curve less than 20 Hz or a regular geometric shape under the medium load peak demand of 20 - 80 kN; when the low load peak demand is 0 - 20 kN, the controller controls the second electro-hydraulic servo valve for flow control. The controller transmits the phase control electrical signal to the second electro-hydraulic servo valve. The motor inside the second electro-hydraulic servo valve controls the valve opening change. The valve opening threshold of the first electro-hydraulic servo valve is 0% - 100%, while the first electro-hydraulic servo valve remains open, that is, the opening remains 100%, thereby controlling the working flow rate and further controlling the change of the working oil pressure inside the actuator, so as to achieve the loading of various load-time history curves under the low load peak demand of 0 - 20 kN. At the same time, in the above working conditions, the controller 101 judges that when the local load loading rate exceeds the set 375 kN / s, it controls the hydraulic accumulator 104 to instantaneously supplement high-pressure oil. Through this multi-stage control method, it is ensured that the hydraulic actuator can accurately reproduce the impact load-time history curve within a wide range of load peaks, frequencies, and shapes applied.

[0161] Furthermore, the oil source 102, the oil separator 103, the oil accumulator 104, and the electro-hydraulic servo valve group 105 are all connected by an oil pipeline system composed of high-pressure hoses, specifically, the oil pump 1021 of the oil source 102 to the oil separator 103 high-pressure hose assembly, including one set of oil inlet pipeline, oil return pipeline, and oil drain pipeline, with a length of 4m. The oil separator 103 to the oil accumulator 104 high-pressure hose assembly, including one set of oil inlet pipeline, oil return pipeline, and oil drain pipeline, with a length of 3m. The oil accumulator 104 to the electro-hydraulic servo valve group 105 oil inlet pipeline high-pressure hose assembly, including one set of oil inlet pipeline, oil return pipeline, and oil drain pipeline, with a length of 3m. The oil flow diagram in the electro-hydraulic servo valve group is shown in the figure. Figure 8 As shown, the outlet of the oil accumulator 104 is connected to the oil inlet of the first electro-hydraulic servo valve through a high-pressure hard pipe, the working oil port of the first valve is connected to the oil inlet of the second electro-hydraulic servo valve through a high-pressure hose, the working oil port of the second electro-hydraulic servo valve is connected to the actuator 106 through a high-pressure hose, the return oil of the actuator 106 flows out through the return oil port of the second electro-hydraulic servo valve, and is merged into the return oil port of the first electro-hydraulic servo valve through a large-diameter return oil pipe, and finally returns to the oil distributor 103 through the main return oil pipe. The flow rate of the return oil pipeline is greater than or equal to 400L / min, and the oil pipeline system uses high-quality hydraulic oil with suitable working temperature and viscosity to ensure its working stability.

[0162] Specifically, the fixed end of the actuator 106 is called the upper end, and the loading end of the actuator 106 is called the lower end. The overall structure of the actuator 106 is a double-rod piston symmetric structure. The hydraulic pressure provided by the electro-hydraulic servo valve group 105 acts on both ends of the symmetric pistons, and it consists of a housing, a piston, a piston rod, a force sensor, a displacement sensor, a hydraulic oil pipe, and a sealing device. Among them, the housing is a cylindrical structure made of high-strength metal materials, mainly used to bear the internal pressure and protect the internal components. The inner surface of the housing is coated with a wear-resistant coating to reduce friction and ensure the service life of the actuator. The piston is located inside the actuator 106 and moves within the inner cavity of the actuator 106. It is made of metal alloy. One side of the piston pushes the load inside the actuator 106 through the pressure of the hydraulic oil, while the other side is connected to the control circuit of the hydraulic system. The piston rod connects the piston to the external structure. When the piston moves inside the actuator, the piston rod also moves accordingly. The piston rod is made of corrosion-resistant and wear-resistant materials. The hydraulic oil pipe is used to connect the electro-hydraulic servo valve group 105 to the hydraulic cavity of the actuator 106. The actuator 106 integrated with the electro-hydraulic servo valve group 105 has a compact plate structure. The rated test force of the actuator 106 is + / - 100 kN, and the effective stroke is ±75 mm. The actuator 106 is equipped with a sealing structure composed of a Glyd ring, a Struthers seal, and a support ring. The actuator 106 is configured with a high-speed dust-proof ring to effectively prevent dust and debris from entering. The actuator 106 is internally provided with an LVDT displacement sensor at the piston rod, with an indication accuracy of ±0.5% FS. The actuator 106 is provided with a force sensor at the loading end. The range of this force sensor is + / - 100 kN, the overload capacity is 200%, the indication accuracy is ±1%, and the accuracy range is 2% - 100% FS. This force sensor is connected to the piston rod with a prestressing ring, and after applying a pre-tightening force, it is locked to ensure a reliable connection for the impact simulation test.

[0163] Specifically, the ball joint 107 is installed on the piston rod of the actuator 106 by means of a stud direct connection. The piston rod and the end of the ball joint 107 are directly pre-tightened and installed through a spiral washer to ensure no clearance. The loading punch 108 includes a pair of upper and lower parallel loading punch upper plates 1081 and loading punch lower plates 1082, and four loading punch reinforcing ribs 1083 perpendicular to the loading punch lower plate 1082. Both the loading punch upper plate 1081 and the loading punch lower plate 1082 are square. The size of the loading punch upper plate 1081 is 300 mm × 300 mm × 50 mm, the size of the loading punch lower plate 1082 is 400 mm × 400 mm × 50 mm, the loading punch reinforcing ribs 1083 are trapezoidal, and the material of the loading punch 108 is 45 steel.

[0164] Specifically, the first base 201 is placed parallel to the concrete floor. Its dimensions are 3000mm × 2000mm × 250mm, and the material is cast iron. Its upper surface and lower surface are both parallel to the ground. The upper surface is evenly engraved with parallel first-base T-slots 2011. A first-base T-nut 2012 that can move along the first-base T-slot 2011 is placed in the first-base T-slot 2011. The outer edge at the bottom surface of the second base 202 is fixed to the upper surface of the first base 201 through a T-bolt, the first-base T-nut 2012, and the first-base T-slot 2011. Its dimensions are 1500mm × 1000mm × 160mm. Its upper surface and lower surface are both parallel to the upper surface of the first base. The upper surface is evenly engraved with parallel T-slots. Both the first column 203 and the second column 204 are cylinders, and the material is alloy steel. The bottom is fixedly installed on the second base 202 through bolts. The distance between the axes of the first column 203 and the second column 204 is 950mm. The plane formed by the axes of the first column 203 and the second column 204 is perpendicular to the axis of the T-slot of the second base 202. Both ends of the cross beam 205 are fixedly installed between the first and second columns through bolts. After installation, the axis of the cross beam 205 is parallel to the ground. Before and after the test, the upper and lower test spaces can be adjusted by moving the cross beam 205 up and down. In this embodiment, the maximum upper and lower test clear spaces ≥ 1000mm. The upper end of the actuator 106 is fixedly installed in the middle of the cross beam 205, and the direction is vertically downward. The wall panel 206 and the wall panel support structure 207 are installed below the actuator 106. The wall panel support structure 207 is made of 45 steel and includes a first end clamping component 2071, a second end clamping component 2072, a first vertical support component 2073, and a second vertical support component 2074. The upper parts of the first vertical support component 2073 and the second vertical support component 2074 are evenly provided with through holes. The first vertical support component 2073 and the second vertical support component 2074 are symmetrically arranged along the plane formed by the axes of the first column 203 and the second column 204, and the bottom is fixed to the upper surface of the second base 202 through a T-bolt, a T-slot nut, and a T-slot. The first end clamping component 2071 is L-shaped, and through holes are provided on both the side surface and the bottom surface. The first end clamping component 2071 is installed on the upper part of the first vertical support component 2073 through the through hole 20712 on the side surface of the first end clamping component. The second end clamping component 2072 is installed on the upper part of the first vertical support component 2074 through the through hole on the side surface of the second end clamping component.On both sides of the wall panel 206, there are flat potting end extension parts 2061. Through holes 2067 are evenly formed in the potting end extension parts 2061. The wall panel 206 is respectively matched with the bottom through holes 20711 of the first end clamping part 2071 and the bottom through holes of the first end clamping part of the second end clamping part 2072 through the through holes 2067 on both sides of the potting end extension parts, and are connected by self-locking bolts.

[0165] Specifically, the wall panel 206 is selected from the wall panels of the fuselage-type lower fuselage structure of a surface vehicle. It also includes a skin 2062, stringers 2063, frames 2064, potting end housings 2065, and potting glue 2066. Specifically, the skin 2062 is a flat carbon fiber composite material structure, and the stringers 2063 are five Z-shaped carbon fiber composite material structures, including a first stringer, a second stringer, a third stringer, a fourth stringer, and a fifth stringer. The 5 stringers 2063 are respectively arranged parallel to the surface of the skin 2062 and are bonded and connected to the skin 2062 by EA9360 glue. The frames 2064 are metal thin-wall structures, including a first frame and a second frame. Each frame is riveted and connected to the skin 2062, and each frame is fixedly connected to the stringers 2063 through shear plates and Hi-Lok bolts. The two ends of the skin 2062 and the stringers 2063 are integrally formed by the potting glue 2066 poured into the potting end housings 2065 on both sides.

[0166] Specifically, the impact position of the loading punch 108 is aligned with the preset impact position of the wall panel 206. A flat loading pad is arranged between the loading punch 108 and the wall panel 206. The loading pad is made of foamed rubber and has an area of 500 mm × 500 mm, which is larger than the area of the preset loading area of the test.

[0167] Specifically, the strain gauge array 301 and the accelerometer array 302 are pasted and installed on the surface of the wall panel 206 according to the test requirements, as Figure 3As shown, both are pasted with 495 glue and assisted in installation with electrical tape. The wiring of the strain gauge array follows the self-compensated quarter-bridge connection method, and the wiring of the accelerometer is carried out according to the relevant instruction manual. The total number of strain gauges used in the strain gauge array 301 is 24, all of which are 350Ω resistive strain gauges and are all within the validity period. The total number of accelerometers used in the accelerometer array 302 is 5, all of which are DH1B109 piezoresistive acceleration sensors. A single crystal silicon is used as the cantilever beam, and four resistors are diffused at its root. When the mass block at the free end of the cantilever beam is subjected to an acceleration, the cantilever beam is subjected to a bending moment, generating stress and causing the resistance values of the four resistors to change. The strain gauge array 301 and the accelerometer array 302 are connected to the centralized dynamic strain collector 303 through signal acquisition lines. The centralized dynamic strain collector is of the DH5921B type and has 64 data acquisition channels, meeting the requirements for test data acquisition; the laser displacement sensor array 304 includes 4 HL-08A laser displacement sensors and an attached power supply, which are installed under the panel. The laser irradiation site is the center position of the skin 2062 divided by the stringer 2063. The initial value of the laser displacement is as close as possible to the displacement monitoring upper limit +20mm, and the voltage of the attached power supply is 24V. The CAN data acquisition module 305 is responsible for receiving the measurement data from the laser displacement sensor array and converting it into a format suitable for further processing. The CAN analyzer 306, as an analysis tool, is used to monitor and analyze the data stream transmitted through the CAN bus and further convert the data signal transmitted through the CAN bus into a data signal transmitted through the USB line. The electronic computer 307 is connected to the centralized dynamic strain collector 303 through an optical fiber to obtain, record, and store signals such as strain and acceleration generated during the test. The electronic computer 307 is connected to the CAN analyzer 306 through a USB line to obtain, record, and store signals such as displacement generated during the test. The measurement range is 60mm to 100mm, and the acquisition frequency can reach 200Hz. In addition, the electronic computer 307 is connected to the controller 101 through an optical fiber to obtain and store the force and displacement signals of the test load.

[0168] After the panel impact test device for simulating the water impact and wave impact loads of a waterplane aircraft is built in this embodiment, the following test functions can be better realized. During the test, the measured water impact load of the waterplane aircraft or other preset load time history curves are input into the electronic computer. The oil distributor 102 supplies the hydraulic oil in the oil source 101 to the hydraulic accumulator 103. After the impact command is issued, the hydraulic accumulator 103 releases the hydraulic oil to supply the actuator 106. The opening and closing angle of the electro-hydraulic servo valve group is controlled by the controller 101 to apply an impact load similar to the preset waveform to the loaded position of the panel 206. The approximation error between the loading waveform and the preset waveform can be basically controlled within 5%.

[0169] As Figure 9 shown in the comparison chart of the water landing load curves, compared with the water landing load curve of the watercraft measured in actuality, since the traditional test device has no accumulator and only one electro-hydraulic servo valve, it cannot take into account the water landing load characteristics of "high amplitude, high frequency response, and highly non-linear", and the peak delay and fitting error are relatively large; while the present invention combines multiple electro-hydraulic servo valves and hydraulic accumulators, and can take into account the loading requirements of "high amplitude, high frequency response, and highly non-linear" of the water landing load time history curve of the watercraft, and the error of its loading curve is basically within 5%.

[0170] In one embodiment, a panel impact test method for simulating the water landing and wave impact load of a watercraft includes the following process:

[0171] S1. Install measuring devices on the surface of the panel 206, including a strain gauge array 301 and an accelerometer array 302.

[0172] S2. Before the test, conduct multiple inspections by multiple people on the panel support structure 207, and carefully inspect the pasted strain gauge array 301 and accelerometer array 302. The strain gauges should be accurately positioned, there should be no extra bubbles inside the strain gauges, and there should be no short circuit or open circuit in the circuit.

[0173] S3. After the test environment meets the requirements, install the panel 206 according to the test requirements. The potting ends at both ends of the panel 206 are respectively matched with the bottom through holes 20711 of the first end clamping member bottom surface of the first end clamping member 2071 and the bottom through holes of the first end clamping member of the second end clamping member 2072, and are connected by self-locking bolts. The first end clamping member 2071 and the second end clamping member 2072 are respectively installed on the first vertical support member 2073 and the second vertical support member 2074 by bolts, and adjust the positions of the first vertical support member 2073 and the second vertical support member 2074 on the second base 202 to align the center of the panel 206 with the loading punch 108. A loading pad 109 is installed at the bottom surface of the loading punch 108. Install a laser displacement sensor array 304 so that its laser irradiation point is located at the center point position of the skin 2062 of the panel 206. Connect the laser displacement sensor array 304 with the CAN data acquisition module 305, the CAN analyzer 306, and the electronic computer 307, check the laser displacement measurement effect, and check its laser intensity, data quality, etc. to ensure the accuracy of the data.

[0174] S4. Zero the strain data of the strain gauge array 301, the acceleration data of the accelerometer array 302, the displacement data of the laser displacement sensor array 304, the force sensor data of the actuator 106, and the displacement sensor data of the actuator 106 in the electronic computer 307. Input the theoretical loading data, multiply it by a coefficient of 10%, set the load control parameters of the actuator 106, and perform a simulated preloading on the panel 206. During the loading process, collect the load data and output the actual loading data. Calculate and compare the error between the input data of the water impact test load and the actual loading data of the wave impact load simulation. According to the test data error, adjust the parameters of the load control of the actuator 106. After zeroing the strain data of the strain gauge array 301, the acceleration data of the accelerometer array 302, the displacement data of the laser displacement sensor array 304, the force sensor data of the actuator 106, and the displacement sensor data of the actuator 106, load the panel 206 again. Compare the input data and the output data, and end the pre-test when the error is less than 5%.

[0175] S5. Zero the strain data of the strain gauge array 301, the acceleration data of the accelerometer array 302, the displacement data of the laser displacement sensor array 304, the force sensor data of the actuator 106, and the displacement sensor data of the actuator 106. Input the load simulation loading data, and perform a simulated loading on the panel 206 by multiplying it by coefficients of 20%, 30%, 50%, 75%, 100%, 150%, etc. During the loading process, collect the load, strain, displacement, and acceleration data.

[0176] S6. After the test load is loaded and there are no abnormalities during the test and the test data is effectively recorded, after the panel 206 is confirmed as a valid part, remove and store the panel 206, save the test data, and end this test.

[0177] Although the embodiments of the present invention have been shown and described above, it can be understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those of ordinary skill in the art can make changes, modifications, substitutions, and variations to the above embodiments within the scope of the present invention without departing from the principles and purposes of the present invention.

Claims

1. A panel impact test device for simulating water landing loads, characterized in that: It includes a water impact load simulation loading module for generating and simulating the water impact load of the test panel. The test panel is fixed by a test fixture tooling module. During the test impact process, the real-time monitoring data obtained is sent to the controller of the water impact load simulation loading module by the test measurement module to complete the closed-loop control of imitating the dynamic load during water impact. The water impact load simulation loading module includes a controller, a hydraulic power unit, and a loading unit. The controller compares the experimental data of the real water impact load experiment with the real-time simulation data obtained by the test measurement module, converts the obtained difference into an electrical signal and sends it to the hydraulic power unit, and the hydraulic power unit converts the electrical signal into a pressure load for the loading unit to perform actions.

2. The wall panel impact test device for simulating water application load according to claim 1, characterized in that: The hydraulic power unit includes an oil source, an oil distributor, an oil accumulator, and an electro-hydraulic servo valve group connected by pipelines. The oil distributor distributes the hydraulic oil provided by the oil source to the input circuit, return circuit of the oil accumulator, or the input circuit, return circuit of the electro-hydraulic servo valve group as required to control the flow rate and pressure of each circuit. The oil accumulator is used to store hydraulic oil and provide supplementary pressure or flow rate during the pressure fluctuation of the electro-hydraulic servo valve group or short-term demand peaks; or to ensure that the electro-hydraulic servo valve can obtain the required oil pressure in a timely manner under high-dynamic or high-load conditions. The electro-hydraulic servo valve group includes a first electro-hydraulic servo valve, a hydraulic damper, and a second electro-hydraulic servo valve connected in series in sequence, and its control circuits are in parallel to ensure the step-by-step adjustment of the hydraulic oil flow rate and pressure and achieve phase synchronization compensation. The first electro-hydraulic servo valve is a two-stage valve with a designed flow rate of 230 L / min and is used for high-load peak demands. The second electro-hydraulic servo valve is a two-stage valve with a designed flow rate of 170 L / min and is used for fine adjustment of medium and low-load peak demands.

3. The wall panel impact test device for simulating water application load according to claim 2, characterized in that: The loading unit includes an actuator and a loading punch installed at the loading end through a ball joint. The flexible connection between the two and the degree-of-freedom compensation and dynamic attitude adjustment of the loading punch are realized through the ball joint, which can avoid stress concentration or structural damage caused by rigid connection and ensure that the load is accurately transmitted to the panel along the preset direction. The loading surface of the loading punch faces the preset impact position of the experimental panel, and a flexible loading pad for protection is arranged between the two. During impact loading, the experimental panel may generate instantaneous angular offsets due to deformation or vibration. The attitude of the loading punch is adjusted in real time through the multi-directional degree-of-freedom characteristics of the ball joint to maintain perpendicular contact with the loading surface of the panel and avoid the interference of lateral component forces on the test data.

4. The wall panel impact test device for simulating water application load according to claim 3, characterized in that: The specific control method of the controller is as follows: Load the preset water impact load-time history curve into the controller and set the target load waveform. Select the corresponding control mode according to the change rate of the target waveform; the control modes include M1 mode, M2 mode, M3 mode, and M4 mode; the peak load of M1 mode is 80 - 100 kN: the opening ranges of both electro-hydraulic servo valves are 0 - 100%, the synchronization error ≤ 5 ms, the accumulator instantaneously releases flow, and the oil pump performs high-flow pressure compensation; the peak load of M2 mode is 20 - 80 kN and high change rate: the opening of the first valve is 0 - 100%, the opening of the second valve is 80 - 100%, and the synchronization error ≤ 5 ms; the peak load of M3 mode is 20 - 80 kN and low change rate: the opening of the first valve is 0 - 100%, and the second valve remains fully open at 100%; the peak load of M4 mode is 0 - 20 kN: the first valve remains fully open at 100%, and the opening of the second valve is 0 - 100%. Synchronously adjust the openings of the first electro-hydraulic servo valve and the second electro-hydraulic servo valve through the PID control method, and combine the energy of the accumulator instantaneously releasing flow to control the output load waveform of the actuator. Real-time monitor the difference between the feedback value of the actuator force sensor and the target value, and limit the error within the allowable range through PID closed-loop control. Safely monitor the oil temperature and vibration signal. If the oil temperature > 65 °C lasts for 60 seconds or the vibration > 5 mm / s lasts for 10 seconds, trigger an emergency stop.

5. The wall panel impact test device for simulating water landing load according to claim 1, characterized in that: The test fixture tooling module is used to fix the wall panel, including a first base at the bottom and a second base, columns, cross beams, and wall panel support structures installed thereon. The second base is installed on the upper surface of the first base through a T-slot and a T-nut, and can adjust the installation position of the wall panel. The cross beam is installed above the second base through two symmetrically arranged columns, used to fix the fixed end of the actuator, and adjust the height position of the actuator by adjusting the installation position on the columns vertically. The wall panel support structure includes end clamping components and vertical support components. Both ends of the wall panel are integrally connected to the potting end housing by potting, and the potting end housings at both ends are respectively fixed to the symmetrically arranged vertical support components on both sides through the clamping components; the vertical support components are installed on the upper surface of the second base through a T-slot and a T-nut.

6. The wall panel impact test device for simulating water application load according to claim 1, wherein: The test measurement module is used to collect impact data, including a strain gauge array, an accelerometer array, a centralized dynamic strain acquisition instrument, a laser displacement sensor array, a CAN data acquisition module, a CAN analyzer, and a computer. The strain gauge array and the accelerometer array are installed on the surface of the wall panel according to the test requirements and are connected to the centralized dynamic strain acquisition instrument through a collection circuit. The centralized dynamic strain acquisition instrument has multiple data acquisition channels to meet the test data acquisition requirements. The laser displacement sensor array is installed below the wall panel, and the laser irradiation site is the position where the displacement change of the wall panel to be monitored is required. The initial value of the laser displacement should be as close as possible to the upper limit of displacement monitoring. The CAN data acquisition module is responsible for receiving the measurement data from the laser displacement sensor array and converting it into a format suitable for further processing. The CAN analyzer, as an analysis tool, is used to monitor and analyze the data stream transmitted through the CAN bus, and further convert the data signals transmitted through the CAN bus into data signals transmitted through the USB cable; The electronic computer is connected to the centralized dynamic strain collector through an optical fiber, and is used to acquire, record, and store the strain and acceleration signals generated by the test; The electronic computer is connected to the CAN analyzer through a USB cable, and is used to acquire, record, and store signals such as displacement generated by the test; it is connected to the controller through an optical fiber, and is used to control the operation of each electromechanical component of the testing machine to ensure the normal function of the test.

7. A method for simulating the impact test of a panel under water landing load, which is implemented based on the panel impact test device for simulating the water landing load according to any one of claims 1-6, characterized in that The specific steps are as follows: Install the wall panel and fix it to the test fixture tooling module, and adjust the loading punch to align with the preset impact position of the wall panel; Input the preset load-time history curve through the controller, and perform a preloading of 10% of the simulated loading data of the water impact load to calibrate the parameters; Load step by step in proportion in stages, and perform real-time data acquisition; the loading ratios are 20%, 30%, 50%, 75%, 100%, and 150% of the simulated loading data of the water impact load respectively; Use the hydraulic accumulator to instantaneously supplement high-pressure oil to achieve the accurate reproduction of high-amplitude and high-frequency response impact loads; Compare the input and output data errors, and adjust the control parameters until the error is less than 5%; After the test is completed, save the data and disassemble the test piece.

8. The method for simulating the impact test of a panel under water spray load according to claim 7, characterized in that: During the staged loading: Under the high load peak of 80 - 100 kN, control the flow rates of the first and second electro-hydraulic servo valves simultaneously; Under the medium load peak of 20 - 80 kN, the first electro-hydraulic servo valve controls the main flow rate, and the second valve assists in the adjustment; Under the low load peak of 0 - 20 kN, only the second electro-hydraulic servo valve controls the flow rate.

9. The method for simulating the impact test of a wall panel under water spray load according to claim 7, wherein: The data acquisition includes: Monitor the strain distribution on the surface of the wall panel through the strain gauge array; Record the displacement of the skin center point of the wall panel through the laser displacement sensor array; Capture the dynamic response characteristics through the accelerometer array; Real-time feedback of the loading data through the built-in force sensor and displacement sensor of the actuator.

10. The method for simulating the impact test of a wall panel under water spray load according to claim 7, characterized in that: The controller adopts PID closed-loop control, with a frequency range of 0.01 - 100 Hz, and supports multi-valve phase synchronization compensation.

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