Testing device for hydraulic radial gate structure parameter resonance

Abstract

A testing device for hydraulic radial gate structure parameter resonance is characterized in that one end of a bottom plate is provided with a supporting mechanism hinged to one ends of two support arm main trusses, the other ends of the support arm main trusses are connected with one side of an arc-shaped plate, and the other side of the arc-shaped plate is connected with the loading end of a force sensor through a force transmission connecting seat and a connecting shaft; the stress end of the force sensor is connected with the vibration exciter through a loading shaft; the double vibration exciters apply dynamic loads with adjustable phases, the dynamic loads are transmitted to the connecting plate and the force transmission connecting base through the loading shaft, the force sensor and the connecting shaft, the arc-shaped plate is driven, then the dynamic loads act on the main support arm truss and the auxiliary support arm truss, and gate stress is simulated. The actual gate stress state can be accurately simulated, and the test precision is ensured through real-time load monitoring and feedback; the laser displacement sensor is combined with signal processing to construct a vibration spectrum, and a parameter vibration rule and a dynamic evolution mechanism of the gate under the simulated pulsating water pressure are disclosed.

Description

Technical Field

[0001] The invention belongs to the technical field of engineering structure experiments, and in particular relates to a test device for structural parameter resonance of a hydraulic radial gate. Background Art

[0002] In water conservancy projects, when radial gates are opened to release water, especially when the opening is small, the pulsating pressure generated by the water flow causes the gates to be subjected to strong periodic pulsating loads, resulting in severe parametric resonance of the radial gate arm structure and, in turn, structural damage. Previous studies have shown that flow-induced vibration is the primary factor causing gate structural instability, and parametric resonance of the arm structure is one of the key causes of gate damage. Currently, research on fluid-structure interaction and gate parametric resonance at home and abroad is still in the exploratory stage, with the theoretical mechanism not fully revealed. Existing computational and experimental methods cannot effectively guide engineering design. Therefore, there is an urgent need for an experimental device that can simulate the parametric resonance behavior of radial gates to gain a deeper understanding of their internal mechanisms and provide theoretical support for structural optimization design.

[0003] The patent application document with publication number CN219757713U discloses a radial gate parameter load simulation test device. The device controls the opening and closing movement of the radial gate by setting a gate opening and closing unit (including a propulsion component and an adjustment component), uses a pressure sensor to monitor the gate force, and realizes the limit control of the opening and closing state through a photoelectric switch. The device ensures the horizontal movement of the push rod through a screw drive and a bearing adjustment mechanism, simulating the opening and closing process of the gate in an actual project. However, because its propulsion component only uses a single linear drive method, the test device can only simulate static loads and cannot simulate the multi-band and multi-phase coupling effect of dynamic pulsating water pressure. In addition, there is a lack of dynamic constraints on the boundary conditions of the support arm structure (such as the simultaneous realization of the free rotation of the hinge support and the lateral displacement limit). As a result, it is difficult to reproduce the parametric resonance behavior of the gate under discharge conditions and cannot accurately reveal the dynamic instability mechanism of the support arm structure parameter resonance. Summary of the Invention

[0004] In order to overcome the deficiencies of the above-mentioned prior art, the purpose of the present invention is to provide a test device for the structural parameter resonance of a hydraulic radial gate. The main part of the device consists of a main truss of the support arm, a secondary truss of the support arm and a curved plate. A high-precision force sensor is arranged between the curved plate and the exciter to realize real-time dynamic monitoring of the loading axis force; dynamic loads with adjustable amplitude, frequency and phase are applied by dual exciters to accurately simulate the pulsating water pressure exerted on the radial gate, accurately reproduce and systematically study the parameter resonance law of the gate, and further reveal the dynamic evolution mechanism of the hydraulic structure under discharge conditions.

[0005] In order to achieve the above object, the technical solution adopted by the present invention is:

[0006] A test device for structural parameter resonance of a hydraulic arc gate comprises a base plate 1, one end of the base plate 1 is provided with a support mechanism, the support mechanism is hinged to one end of two arm main trusses 2 extending from a point and forming an angle, the two ends of the two arm main trusses 2 extending from a point are respectively connected to the two ends of one side of a curved plate 4, the other two ends of the curved plate 4 are respectively connected to the connecting plate 11 through a force transmission connecting seat 10, the connecting plate 11 is connected to the loading end of the force sensor 7 through a connecting shaft 9, the force-bearing end of the force sensor 7 is connected to the driving side of the exciter 8 through the loading shaft 6, a connecting bar 12 is vertically connected between the force transmission connecting seat 10 and the base plate 1, and an arm sub-truss 3 is arranged in parallel between the two arm main trusses 2 close to the support mechanism, and the arm sub-truss 3 forms a spatial truss structure with the arm main truss 2 through the connecting bar 12.

[0007] The supporting mechanism includes a main shaft 16 vertically arranged on the base plate 1, and the outer wall of the main shaft 16 is provided with a thread, and the upper surface of the base plate 1 in contact with the main shaft 16 is provided with a screw hole, and the bottom end of the main shaft 16 is connected to the base plate 1 through a thread, and the square fixing nut 15 includes four outer walls, all of which are provided with screw holes. The outer wall of the square fixing nut 15 is connected to the connecting end of the supporting plate 13 by bolts passing through the screw holes. The supporting end of the support plate 13 is fixed to the base plate 1, and a bearing seat 5 is provided above the square fixing nut 15. The bearing seat 5 includes an inner side 5.1 of the bearing seat and an outer side 5.2 of the bearing seat. A precision roller bearing 5.3 is provided between the inner side 5.1 of the bearing seat and the outer side 5.2 of the bearing seat. The outer side 5.2 of the bearing seat is connected to one end of the two support arm main trusses 2 extending from a point and forming an angle. The inner side 5.1 of the bearing seat is sleeved on the main shaft 16, and the outer side 5.2 of the bearing seat can rotate freely around the main shaft 16, and a hinge is formed between the outer side 5.2 of the bearing seat and the main shaft 16.

[0008] The force transmission connection seat 10 is connected to the top end of the connection bar 12 through a hinge 14 , and the bottom end of the connection bar 12 is connected to the bottom plate 1 .

[0009] The force transmission connection seat 10 includes a connection seat bottom plate 10.1, and channel steels 10.2 are symmetrically arranged above the connection seat bottom plate 10.1. The groove-shaped openings of the two channel steels 10.2 are arranged back to back outward, and a first channel steel hole 10.3 is opened on the end of the channel steel 10.2 close to the connecting plate 11. The two ends of the connecting plate 11 close to the connecting shaft 9 are respectively provided with a first connecting plate hole 11.1 and a third connecting plate hole 11.3 corresponding to the first channel steel holes 10.3 of the two force transmission connection seats 10. The force transmission connection seat 10 is connected to the connection seat 10 by bolts passing through the first channel steel hole 10.3, the first connecting plate hole 11.1 or the third connecting plate hole 11.3. The plates 11 are connected; a second channel steel hole 10.4 is opened on the end of the channel steel 10.2 near the arc plate 4, and the second channel steel hole 10.4 is connected to the arc plate 4 by a bolt. A second connecting plate hole 11.2 is opened in the middle position of one side of the connecting plate 11 near the connecting shaft 9, and the connecting shaft 9 passes through the second connecting plate hole 11.2, so that the connecting shaft 9 is fixed to the connecting plate 11 by a nut, and connecting seat bottom plate holes 10.5 are opened at both ends of the connecting seat bottom plate 10.1 of the force transmission connecting seat 10. The connecting seat bottom plate hole 10.5 is connected to one end of the hinge 14 by a bolt, and the other end of the hinge 14 is connected to the top of the connecting strip 12 by a bolt.

[0010] Compared with the prior art, the present invention has the following beneficial effects:

[0011] 1. The present invention accurately simulates the boundary conditions of the actual hinge support. Through the design of the articulated bearing seat 5 and the main shaft 16, it realizes the dual-degree-of-freedom simultaneous simulation of the lateral displacement constraint and the free rotation around the axis at the ends of the two support arm main trusses 2 (the existing technology only supports single-degree-of-freedom rotation), restores the dynamic characteristics of the hinge support in actual engineering, and greatly reduces the vibration response error of the support arm structure.

[0012] 2. The present invention has the ability to reproduce dynamic multi-band flow-induced vibrations. It adopts dual exciters 8 for collaborative loading, supports independent adjustment of amplitude (0-5kN), frequency (0-100Hz), and phase difference (0°-180°), generates a multi-frequency coupled dynamic load spectrum, and accurately simulates the time-history characteristics of pulsating water pressure under discharge conditions. The existing technology CN 219757713 U can only simulate a single linear opening and closing load.

[0013] 3. The present invention places a high-precision force sensor between the dual vibrator 8 and the curved plate 4 to achieve real-time dynamic monitoring of the force acting on the loading shaft 6. Real-time force feedback ensures that the load applied to the loading shaft 6 by the dual vibrator 8 is strictly consistent each time, avoiding uncontrollable factors caused by vibrator performance drift, environmental changes or load differences, and significantly improving the reliability and comparability of experimental data.

[0014] 4. The present invention is a three-dimensional space force transmission system. The space truss structure formed by the support arm main truss 2-the support arm secondary truss 3-the connecting bar 12 truly reflects the spatial force state of the radial gate during discharge. Compared with the plane force transmission structure of CN 219757713 U, the simulation accuracy of the support arm stress distribution is greatly improved.

[0015] 5. The present invention provides key rigid support for the structure by setting up connecting bars 12, which is specifically used to resist bending deformation and inter-layer dislocation (shear force) caused by vertical loads, thereby significantly enhancing the vertical stiffness, strength, overall stability and deformation resistance of the structure.

[0016] In summary, the present invention realizes dual-degree-of-freedom boundary simulation (lateral constraint + free rotation) through the design of articulated bearing seat 5 and main shaft 16; dual exciters 8 cooperate in loading (amplitude, frequency, and phase are independently adjustable) to generate a multi-frequency coupled dynamic load spectrum; high-precision force sensor 7 performs real-time dynamic monitoring and feedback to ensure load consistency; the main truss 2 of the support arm, the auxiliary truss 3 of the support arm and the connecting bar 12 construct a three-dimensional space force transmission system; the connecting bar 12 provides bending and shear rigid support to enhance vertical stiffness and stability; the present invention has the core advantages of accurately restoring the actual dynamic characteristics of the hinged support and the discharge pulsating load, significantly reducing the vibration response error and stress distribution deviation of the support arm, greatly improving the reliability and comparability of experimental data, and comprehensively simulating the spatial stress state of the radial gate. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 It is a front view of the overall structure of the present invention.

[0018] Figure 2 It is a top view of the overall structure of the present invention.

[0019] Figure 3 It is a structural schematic diagram of the base plate 1 of the present invention.

[0020] Figure 4 1 is a positional relationship diagram of the support arm main truss 2, the support arm sub-truss 3 and the curved plate 4 of the present invention.

[0021] Figure 5 This is a schematic structural diagram of the bearing seat 5 of the present invention, wherein: Figure 5 (a) is a top view of the bearing seat 5, Figure 5 (b) is a front view of the bearing seat 5.

[0022] Figure 6 It is a schematic structural diagram of the loading shaft 6 of the present invention.

[0023] Figure 7 It is a structural schematic diagram of the connecting shaft 9 of the present invention.

[0024] Figure 8It is a schematic diagram of the connection structure between the force transmission connection seat 10 and the connection plate 11 of the present invention.

[0025] Figure 9 It is a structural diagram of the force transmission connection seat 10 of the present invention.

[0026] Figure 10 This is a schematic structural diagram of the connecting plate 11 of the present invention, wherein: Figure 10 (a) is a top view of the connecting plate 11, Figure 10 (b) is a front view of the connecting plate 11.

[0027] Figure 11 Schematic diagram of the structure of the connecting strip 12 of the present invention, wherein: Figure 11 (a) is a side view of the connecting bar 12, Figure 11 (b) is a front view of the connecting bar 12.

[0028] Figure 12 is a schematic structural diagram of the support plate 13 of the present invention, wherein: Figure 12 (a) is a side view of the support plate 13, Figure 12 (b) is a front view of the support plate 13, Figure 12 (c) is a top view of the support plate 13 .

[0029] Figure 13 It is a structural diagram of the hinge 14 of the present invention.

[0030] Figure 14 This is a schematic structural diagram of the square fixing nut 15 of the present invention, wherein: Figure 14 (a) is a front view of the square fixing nut 15, Figure 14 (b) is a top view of the square fixing nut 15.

[0031] Figure 15 It is a schematic structural diagram of the main shaft 16 of the present invention.

[0032] Figure 16 It is a front view of the present invention.

[0033] Figure 17 It is a top view of the physical object of the present invention.

[0034] In the figure, 1. Base plate; 2. Support arm main truss; 3. Support arm sub-truss; 4. Arc plate; 5. Bearing seat; 6. Loading shaft; 7. Force sensor; 8. Exciter; 9. Connecting shaft; 10. Force transmission connecting seat; 11. Connecting plate; 12. Connecting bar; 13. Support plate; 14. Hinge; 15. Square fixing nut; 16. Main shaft. DETAILED DESCRIPTION

[0035] The present invention will be further described below with reference to the accompanying drawings and examples.

[0036] A test device for the structural parameter resonance of a hydraulic radial gate comprises: a main arm truss 2, a secondary arm truss 3, and a curved plate 4. A high-precision force sensor is provided between the curved plate 4 and the vibrator 8 to achieve real-time dynamic monitoring of the loading axis force. A phase-adjustable dynamic load is applied by a dual vibrator 8, supporting amplitude (0-5kN), frequency (0-100Hz), and phase difference (0°-180°), accurately simulating the pulsating water pressure acting on the radial gate. The specially designed articulated bearing support effectively limits the displacement of the arm end while retaining its free rotation characteristic around the axis, truly restoring the boundary conditions of the hinge support of the actual engineering structure. The device can accurately reproduce and systematically study the dynamic instability law of the gate through systematic regulation of the excitation parameters, thereby further revealing the dynamic evolution mechanism of the hydraulic structure under discharge conditions.

[0037] like Figure 1 、 Figure 2 、 Figure 16 and Figure 17 As shown, a test device for structural parameter resonance of a hydraulic radial gate comprises a base plate 1, one end of the base plate 1 is provided with a supporting mechanism, the supporting mechanism is hinged to one end of two arm main trusses 2 extending from a point and forming an angle, the two ends of the two arm main trusses 2 extending from a point are respectively connected to the two ends of one side of a curved plate 4, the other two ends of the curved plate 4 are respectively connected to the connecting plate 11 through a force transmission connecting seat 10, the connecting plate 11 is connected to the loading end of the force sensor 7 through a connecting shaft 9, the force-bearing end of the force sensor 7 is connected to the driving side of the exciter 8 through a loading shaft 6, a connecting bar 12 is vertically connected between the force transmission connecting seat 10 and the base plate 1, and an arm sub-truss 3 is arranged in parallel between the two arm main trusses 2 close to the supporting mechanism, and the arm sub-truss 3 forms a spatial truss structure with the arm main truss 2 through the connecting bar 12.

[0038] The force sensor 7 is used to monitor the dynamic load transmitted by the vibrator 8 and transmit the data to the computer to achieve real-time dynamic monitoring of the loading axis force.

[0039] The exciter 8 is used to apply a dynamic load with adjustable phase to accurately simulate the pulsating water pressure acting on the radial gate.

[0040] After receiving the signals from the signal detector and the signal amplifier, the exciter 8 pushes the loading shaft 6, the force sensor 7 collects the action signal of the loading shaft 6, the signal collector collects the signal of the force sensor 7, and the signal collector outputs the data to the computer.

[0041] The support mechanism includes a main shaft 16 vertically arranged on the base plate 1, the outer wall of the main shaft 16 is provided with a thread, and the upper surface of the base plate 1 in contact with the main shaft 16 is provided with a screw hole, and the bottom end of the main shaft 16 is connected to the base plate 1 through a thread, and the square fixing nut 15 includes four outer walls, each of which is provided with a screw hole. The outer wall of the square fixing nut 15 is connected to the connecting end of the supporting plate 13 by a bolt passing through the screw hole, and the supporting end of the supporting plate 13 is fixed on the base plate 1 to provide horizontal support force for the main shaft 16; located above the square fixing nut 15 A bearing seat 5 is provided, and the bearing seat 5 includes an inner side 5.1 of the bearing seat and an outer side 5.2 of the bearing seat. A precision roller bearing 5.3 is provided between the inner side 5.1 of the bearing seat and the outer side 5.2 of the bearing seat. The outer side 5.2 of the bearing seat is connected to one end of the two support arm main trusses 2 extending from one point and forming an angle. The inner side 5.1 of the bearing seat is sleeved on the main shaft 16, and the main shaft 16 only provides constraints (limiting its movement). The outer side 5.2 of the bearing seat can rotate freely around the main shaft 16, and a hinge is formed between the outer side 5.2 of the bearing seat and the main shaft 16 to simulate an actual hinged support.

[0042] The force transmission connection seat 10 is connected to the top end of the connection bar 12 through a hinge 14 , and the bottom end of the connection bar 12 is connected to the bottom plate 1 .

[0043] The two connecting bars 12 serve to support the vertical weight of the structure while also preventing the structure from moving horizontally.

[0044] The force transmission connection seat 10 includes a connection seat bottom plate 10.1, and channel steels 10.2 are symmetrically arranged above the connection seat bottom plate 10.1. The groove-shaped openings of the two channel steels 10.2 are arranged back to back outward, and a first channel steel hole 10.3 is opened on the end of the channel steel 10.2 close to the connecting plate 11. The two ends of the connecting plate 11 close to the connecting shaft 9 are respectively provided with a first connecting plate hole 11.1 and a third connecting plate hole 11.3 corresponding to the first channel steel holes 10.3 of the two force transmission connection seats 10. The force transmission connection seat 10 is connected to the connection seat 10 by bolts passing through the first channel steel hole 10.3, the first connecting plate hole 11.1 or the third connecting plate hole 11.3. The plates 11 are connected; a second channel steel hole 10.4 is opened on the end of the channel steel 10.2 near the arc plate 4, and the second channel steel hole 10.4 is connected to the arc plate 4 by a bolt. A second connecting plate hole 11.2 is opened in the middle position of one side of the connecting plate 11 near the connecting shaft 9, and the connecting shaft 9 passes through the second connecting plate hole 11.2, so that the connecting shaft 9 is fixed to the connecting plate 11 by a nut, and connecting seat bottom plate holes 10.5 are opened at both ends of the connecting seat bottom plate 10.1 of the force transmission connecting seat 10. The connecting seat bottom plate hole 10.5 is connected to one end of the hinge 14 by a bolt, and the other end of the hinge 14 is connected to the top of the connecting strip 12 by a bolt.

[0045] The structural relationship and positional relationship of the device of the present invention are described as follows:

[0046] Base plate 1: As the basic bearing platform, it is fixed to the test bench base through anchor bolts. The surface is provided with standardized base holes for installing the main shaft 16 and support plate 13. Figure 3 shown.

[0047] The main truss of the support arm 2: one end is hinged to the bearing seat 5 through the main shaft 16, and the other end is rigidly connected to the arc plate 4 through bolts, such as Figure 4 shown.

[0048] The auxiliary truss 3 of the support arm is arranged in parallel with the front end of the main truss 2 of the support arm, and forms a space truss structure with the main truss 2 of the support arm through the connecting bar 12. The two ends of the connecting bar 12 are locked by bolts, such as Figure 4 shown.

[0049] Curved plate 4: simulates the gate panel. One end of the curved plate 4 is connected to the main truss 2 of the support arm, and the other end is connected to the force transmission connection seat 10. It is also connected to the exciter 8 through the connecting plate 11, the connecting shaft 9, the force sensor 7, and the loading shaft 6. Figure 4 shown.

[0050] Bearing seat 5: fixed to the front end of the base plate 1, with built-in precision roller bearing 5.3. The inner side 5.1 of the bearing seat is sleeved on the main shaft 16. The main shaft 16 only provides constraints (limits its movement). The main truss 2 of the support arm is connected to the outer side 5.2 of the bearing seat, and the outer side 5.2 of the bearing seat can rotate freely around the main shaft 16. It realizes lateral displacement constraint + free rotation (simulating an actual hinge support), such as Figure 5 (a) Figure 5 (b) shown.

[0051] Loading shaft 6: connected to the exciter 8, and the other end is connected to the force sensor 7, as shown Figure 6 shown.

[0052] Force sensor 7: connected in series between the loading shaft 6 and the curved plate 4, to monitor the dynamic load in real time, such as Figure 1-2 shown.

[0053] Vibrator 8: symmetrically mounted on both sides of the base plate 1, the horizontal position is adjusted through the force transmission connection seat 10, and the vibrator 8 is connected to the loading shaft 6, such as Figure 1-2 shown.

[0054] Connecting shaft 9: penetrates the connecting plate 11 and connects to the force transmission connecting seat 10, and realizes multi-directional force transmission through double-row angular contact bearings, such as Figure 7 shown.

[0055] Force transmission connection base 10: By opening a hole in the force transmission connection base 10, its three components are connected in series, namely the arc plate 4, the exciter 8 and the connecting bar 12. The force transmission connection base 10 is connected to the arc plate 4 with bolts, and the force transmission connection base 10 is connected to the exciter 8 through the connecting plate 11, the connecting shaft 9, the force sensor 7, and the loading shaft 6. It is connected to the connecting bar 12 through the hinge 14. Figure 8 、 Figure 9 shown.

[0056] Connecting plate 11: fixed on the force transmission connection seat 10 by bolts, so that the connecting shaft 9 can be connected to the force transmission connection seat 10, such as Figure 10 (a) Figure 10 (b) shown.

[0057] Connecting bar 12: The upper end of the connecting bar 12 is connected to the connecting base bottom plate 10.1 at the bottom of the force transmission connecting base 10 through a hinge 14, and the lower end of the connecting bar 12 is connected to the bottom plate 1 to provide support for the structure and resist the bending moment and shear force perpendicular to the plane of the bottom plate 1 (i.e., the vertical direction). Figure 11 (a) Figure 11 (b) shown.

[0058] Support plate 13: connected to the square fixing nut 15, providing support force for the main shaft 16, such as Figure 12 (a) Figure 12 (b) and Figure 12 (c) shown.

[0059] Hinge 14: connects its force transmission connection seat 10 with the connecting strip 12, and the connecting strip 12 is connected to the bottom plate 1, such as Figure 13 shown.

[0060] Square fixing nut 15: It is set on the main shaft 16 and has holes around it. The support plate 13 can be connected to the square fixing nut 15 by bolts passing through the screw holes on the four outer walls of the square fixing nut 15, indirectly providing support force for the main shaft 16, such as Figure 14 (a) Figure 14 (b) shown.

[0061] Spindle 16: The bearing seat 5 and the square fixing nut 15 are installed on the spindle 16. The spindle 16 is installed vertically on the base plate 1 and fixed through the base hole to resist the overturning moment caused by the vibration of the support arm. Figure 15 shown.

[0062] Examples of key position markings in the attached figures:

[0063] like Figure 1-Figure 2 As shown, the connection point between the bearing seat 5 and the main truss of the support arm 2 is located on one side, and the exciters 8 are symmetrically arranged at both ends of one side of the base plate 1.

[0064] like Figure 2As shown, the arc plate 4 is connected to the force transmission connecting seat 10 by bolts, the connecting plate 11 is connected to the force transmission connecting seat 10 by bolts, the connecting shaft 9 passes through the connecting plate 11 and is connected to the force sensor 7, and the connecting shaft 9 and the loading shaft 6 are respectively at both ends of the force sensor 7.

[0065] like Figure 1-Figure 2 As shown, both ends of the connecting shaft 9 are fixed with locking nuts to ensure that the main truss 2 of the support arm and the curved plate 4 can simulate the real situation when the exciter 8 outputs the load.

[0066] The invention is a novel experimental device for studying the resonance of radial gate structural parameters, and is suitable for engineering research on the operation safety of hydraulic structures, fluid-structure interaction, and the like.

[0067] This invention aims to develop a test device for the parametric resonance of hydraulic radial gate structures, filling the gap in experimental equipment for radial gate parametric resonance (dynamic stability) research both domestically and internationally. Currently, research in this field is still in its exploratory phase, with its theoretical mechanisms not yet fully understood. Existing computational methods and experimental approaches are insufficient to effectively guide practical engineering designs. By establishing a systematic experimental platform, this device will provide efficient and reliable technical support for the study of the dynamic characteristics and optimized design of radial gate structures.

[0068] The excitation system of the present invention can simulate the dynamic response of an actual gate by controlling the parameters of the signal generator and the power amplifier, accurately adjusting the frequency, amplitude, and phase difference of the two exciters, and can effectively excite the parametric resonance behavior of the main truss of the radial gate arm. The system monitors the force applied by the loading shaft in real time through a high-precision force sensor. The periodic excitation force generated by the exciter can drive the structure to undergo significant lateral vibration. The amplitude and characteristics of the vibration can be monitored in real time by a laser displacement sensor. The relationship between the excitation force amplitude and frequency and the vibration characteristics of the main truss of the arm is explored to provide a scientific physical mechanism to avoid parametric resonance in actual radial gates and improve the safety and stability of hydraulic structures.

[0069] The working principle of the present invention is as follows:

[0070] Dual vibrators 8 apply a phase-adjustable dynamic load, which is transmitted to the curved plate 4 via the loading shaft 6 and connecting shaft 9. This load then acts on the main arm truss 2 and the secondary arm truss 3, simulating the stress conditions of a radial gate in actual construction. A force sensor 7, positioned between the loading shaft 6 and connecting shaft 9, monitors the load in real time and provides feedback, ensuring that the load applied by the dual vibrators 8 to the loading shaft 6 is strictly consistent throughout each test.

[0071] The force-transmitting connector 10 and connecting plate 11 in the structure are used to transfer load, allowing the load generated by the dual vibrators 8 to effectively act on the curved plate 4. The base of the force-transmitting connector 10 has holes and is secured to the connecting bar 12 via bolts. The main function of the connecting bar 12 is to bear the vertical load (such as deadweight) of the structure and to restrain its horizontal displacement.

[0072] Laser displacement sensors are installed on both sides of the main truss 2 to measure its displacement response. Combined with digital signal processing algorithms, a spectrum reflecting the vibration characteristics of the structural parameters can be constructed. This method can reveal the parametric vibration patterns of the radial gate structure under external loads (simulating pulsating water pressure), thereby further revealing the dynamic evolution mechanism of the hydraulic structure under discharge conditions.

[0073] The present invention achieves accurate reproduction of the structural instability boundary and flow-induced vibration effects through the bearing seat simulating hinge support constraints, collaborative loading of two exciters and high-precision sensor monitoring, providing a reliable test platform for gate parameter resonance analysis.

Claims

1. A test device for structural parameter resonance of a hydraulic radial gate, comprising a bottom plate (1), characterized in that: One end of the base plate (1) is provided with a support mechanism, which is hinged to one end of the two arm main trusses (2) extending from a point and forming an angle. The two ends of the two arm main trusses (2) extending from a point are respectively connected to the two ends of one side of the arc plate (4), and the two ends of the other side of the arc plate (4) are respectively connected to the connecting plate (11) through a force transmission connecting seat (10). The connecting plate (11) is connected to the loading end of the force sensor (7) through a connecting shaft (9), and the force-bearing end of the force sensor (7) is connected to the driving side of the exciter (8) through a loading shaft (6). A connecting bar (12) is vertically connected between the force transmission connecting seat (10) and the base plate (1). A support arm sub-truss (3) is arranged in parallel between the two arm main trusses (2) close to the support mechanism. The support arm sub-truss (3) forms a spatial truss structure with the arm main trusses (2) through the connecting bar (12).

2. A test device for structural parameter resonance of hydraulic radial gate according to claim 1, characterized in that: The support mechanism includes a main shaft (16) vertically arranged on the bottom plate (1), the outer wall of the main shaft (16) is provided with a thread, the upper surface of the bottom plate (1) in contact with the main shaft (16) is provided with a screw hole, the bottom end of the main shaft (16) is connected to the bottom plate (1) through the thread, the square fixing nut (15) includes four outer walls, the four outer walls are provided with screw holes, the outer wall of the square fixing nut (15) is connected to the connecting end of the supporting plate (13) through a bolt passing through the screw hole, the supporting end of the supporting plate (13) is fixed on the bottom plate (1), and the square fixing nut (15) is provided with a screw hole. 5), a bearing seat (5) is provided above the bearing seat (5), the bearing seat (5) includes an inner side (5.1) of the bearing seat and an outer side (5.2) of the bearing seat, a precision roller bearing (5.3) is provided between the inner side (5.1) of the bearing seat and the outer side (5.2) of the bearing seat, the outer side (5.2) of the bearing seat is connected to one end of the two support arm main trusses (2) extending from a point and forming an angle, the inner side (5.1) of the bearing seat is sleeved on the main shaft (16), the outer side (5.2) of the bearing seat can rotate freely around the main shaft (16), and a hinge is formed between the outer side (5.2) of the bearing seat and the main shaft (16).

3. A test device for structural parameter resonance of hydraulic radial gate according to claim 1, characterized in that: The force transmission connection seat (10) is connected to the top end of the connection bar (12) via a hinge (14), and the bottom end of the connection bar (12) is connected to the bottom plate (1).

4. A test device for structural parameter resonance of hydraulic radial gates according to claim 1 or 3, characterized in that: The force transmission connection seat (10) comprises a connection seat bottom plate (10.1), channel steels (10.2) are symmetrically arranged above the connection seat bottom plate (10.1), the groove-shaped openings of the two channel steels (10.2) are arranged outwardly back to back, a first channel steel hole (10.3) is opened on the end of the channel steel (10.2) close to the connection plate (11), and a first connection plate hole (11.1) and a third connection plate hole (11.3) corresponding to the first channel steel holes (10.3) of the two force transmission connection seats (10) are opened at both ends of one side of the connection plate (11) close to the connection shaft (9), respectively. The force transmission connection seat (10) is connected to the connection plate (10) by bolts passing through the first channel steel hole (10.3), the first connection plate hole (11.1) or the third connection plate hole (11.3). 11); a second channel steel hole (10.4) is provided on the end of the channel steel (10.2) close to the arc plate (4), and the second channel steel hole (10.4) is connected to the arc plate (4) by a bolt; a second connecting plate hole (11.2) is provided at the middle position of one side of the connecting plate (11) close to the connecting shaft (9); the connecting shaft (9) passes through the second connecting plate hole (11.2), so that the connecting shaft (9) is fixed to the connecting plate (11) by a nut; connecting seat bottom plate holes (10.5) are provided at both ends of the connecting seat bottom plate (10.1) of the force transmission connecting seat (10); the connecting seat bottom plate holes (10.5) are connected to one end of the hinge (14) by a bolt, and the other end of the hinge (14) is connected to the top of the connecting strip (12) by a bolt.

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