Vibration reduction test platform

Abstract

The invention belongs to the technical field of rail vibration reduction test devices, and particularly relates to a vibration reduction test platform. The vibration reduction test platform comprises a single-degree-of-freedom simulation test mechanism which is used for simulating a first-order vertical rigid body vibration modal shape corresponding to a first-order inherent frequency of the floating slab track; the four-point supporting plate simulation test mechanism is used for simulating a high-order rigid body vibration modal shape, bending modal shapes, torsion modal shapes and other modal shapes in a higher-frequency range of the floating slab track; the vibration sensing device is arranged on the single-degree-of-freedom simulation test mechanism and the four-point support plate simulation test mechanism and is used for measuring and collecting force response and acceleration response; a bottom plate; sliding grooves are symmetrically formed in the bottom plate, and the single-degree-of-freedom simulation test mechanism and the four-point supporting simulation test mechanism are arranged on the bottom plate side by side and located between the symmetrical sliding grooves. And the jacking hoisting mechanism is positioned on the bottom plate, is connected with the sliding chute in a sliding fit manner, and is used for hoisting and carrying the test mechanism, mounting the loading mechanism and adjusting test operation.

Description

Technical Field

[0001] The invention belongs to the technical field of track vibration reduction test devices, and in particular relates to a vibration reduction test platform. Background Art

[0002] Floating plate track vibration reduction technology is a widely used and excellent vibration reduction technology in the current field of urban rail transit vibration reduction. Corresponding vibration reduction test devices and equipment are required to carry out floating plate track tests in the field of rail transit vibration reduction. Many tests are carried out based on full-size floating plate tracks, which require large-scale handling equipment to transport the track plates and large-scale loading equipment to excite the track plates to produce vibrations. There are problems such as difficult handling, high test costs, and large space occupation. "Urban Rail Transit Steel Spring Floating Plate Track Construction Quality Acceptance Standard" (DG / TJ 08-2416-2023J16935-2023) and other normative documents and some senior track vibration detection units in the industry simplify the track plate into a single-degree-of-freedom vibration system, and propose a vibration reduction test device that places a single vibration isolator at the center of the bottom surface of a concrete mass block to form a single-degree-of-freedom mass-spring-damper system. The weight of the concrete mass block is designed according to the weight of the track plate shared by a single vibration isolator in the actual floating plate track. The single-degree-of-freedom system vibration reduction test device can not only simulate the vertical vibration characteristics of the track structure, but also reduce the volume and mass of the test device to facilitate equipment handling and debugging. However, in actual use, the concrete mass block of the existing single-degree-of-freedom system vibration reduction test device is prone to shaking due to the lack of lateral constraints, resulting in test data errors. Patent document CN103149048A discloses a multifunctional test platform for track vibration isolation based on magnetorheological technology. On this test platform, an eccentric block exciter semi-rigidly connected to the track is used to simulate the external exciting force of the train wheel and rail, which is inconsistent with the actual situation of nonlinear contact between the wheel and rail during the operation of the train. More importantly, this device coupling the loading device with the loaded structure forms a new vibration system, and its system natural frequency is no longer the natural frequency of the track system. Therefore, it is difficult to accurately test the vibration reduction effect near the natural frequency of the track system, and the relevant test results are difficult to guide actual engineering design. Patent document CN108240894A discloses a track vibration reduction test device and a track vibration reduction test equipment. This patent solves the problem that the coupling of the loading device and the loaded structure changes the natural frequency of the test device when simulating actual track vibration, thereby causing measurement errors. However, the test device still has some limitations. For example, the rail vibration reduction test device realizes a single-degree-of-freedom vibration system by vertically arranging a spring part and a magnetorheological damper between a simulated floating plate and a simulated lower substrate, and the spring part only moves up and down. However, when the magnetorheological damper or other vibration reduction elements are tested by this device, the spring part used to support the simulated floating plate will provide excess support stiffness, causing test deviation, and the support stiffness will also change the natural frequency of the test device.In addition, the existing single-degree-of-freedom test device simulates the first-order vertical rigid body vibration mode corresponding to the first-order natural frequency of the floating plate track. It is mainly used to test the vibration reduction performance of a single isolator on the first-order mode of the floating plate track. It cannot reflect other higher-order rigid body vibration mode modes and bending and torsion mode modes of the floating plate track. The test results cannot prove the vibration reduction performance of other higher-order mode modes of the floating plate track. In addition, the thickness or cross-sectional form of the floating plate in different track lines will be different, that is, the plate weight shared by each isolator will change or the natural frequency of the vibration system will change. However, the vibrator mass of the test device cannot be adjusted and cannot reflect the change of the plate weight shared by each isolator. There are also problems such as single loading form, single test product, and difficult transportation. Summary of the invention

[0003] The purpose of the present invention is to solve the above-mentioned shortcomings and provide a vibration reduction test platform.

[0004] In the first aspect, a vibration reduction test platform adopts the following technical solutions:

[0005] A vibration reduction test platform, comprising:

[0006] A single-degree-of-freedom simulation test mechanism is used to simulate the first-order vertical rigid body vibration mode shape corresponding to the first-order natural frequency of the floating slab track, and adjust the natural frequency to correspond to the first-order natural frequency of the actual line track by adjusting the total mass of the single-degree-of-freedom vibrator;

[0007] The four-point support plate simulation test mechanism is used to simulate the high-order rigid body vibration mode vibration mode, bending and torsion mode vibration mode in the higher frequency range of the floating plate track, and adjust the vibration frequency to correspond to the high-frequency vibration of the actual line track by adjusting the total mass of the vibration plate;

[0008] A vibration sensing device, arranged on the single-degree-of-freedom simulation test mechanism and the four-point support plate simulation test mechanism, is used to measure and collect force response and acceleration response, calculate the transfer function between the input and output of the vibration system, and analyze the vibration characteristics and vibration reduction effect in each frequency band;

[0009] Bottom plate; the bottom plate is symmetrically provided with slide grooves, the single-degree-of-freedom simulation test mechanism and the four-point support simulation test mechanism are arranged side by side on the bottom plate and are located between the symmetrical slide grooves;

[0010] The lifting and hoisting mechanism is located on the bottom plate and is slidably connected with the slide groove, and is used for lifting and transporting the test mechanism, installing the loading mechanism and adjusting the test operation.

[0011] Further, the single-degree-of-freedom simulation test mechanism includes a first base, a single-degree-of-freedom vibrator, a first vibration-damping element, a first jack and a rigid limiting column;

[0012] The first base is fixedly connected to the bottom plate, a plurality of the rigid limiting columns are vertically inserted and fixed on the first base, and the first vibration-damping element is arranged at the center position; the single-degree-of-freedom vibrator is arranged above the first vibration-damping element, the single-degree-of-freedom vibrator is provided with a through hole, and is vertically slidably matched with the rigid limiting column sleeve through the through hole; the jack is symmetrically arranged on both sides of the first vibration-damping element, the bottom of the jack is fixedly connected to the bottom plate, and the top is in contact with the single-degree-of-freedom vibrator, so as to be used for retracting and lifting the single-degree-of-freedom vibrator upward.

[0013] Furthermore, the single-degree-of-freedom vibrator includes a heavy vibrator and a plurality of light vibrators, the heavy vibrator is stacked, aligned and fastened to the plurality of light vibrators, and the total mass of the single-degree-of-freedom vibrator is adjusted by adjusting the number of the light vibrators.

[0014] Furthermore, the rigid limiting column includes a ball spline screw structure, the ball spline screw structure includes a spline shaft and a spline nut, the bottom of the spline shaft is fixedly connected to the base plate, the spline nut is fixedly connected to the bottom of the heavy vibrator and is slidably matched with the spline shaft sleeve.

[0015] Further, the four-point support simulation test mechanism includes a second base, a second vibration reduction element, a second jack and a vibration plate;

[0016] The second base is fixedly connected to the bottom plate, and a plurality of the second vibration-damping elements are arranged at the corners, and the vibration plate is arranged on the top of the plurality of the second vibration-damping elements; the second jacks are symmetrically arranged on the second bottom plate, and the bottom of the second jacks is fixedly connected to the bottom plate, and the top abuts against the vibration plate, so as to be used for retracting and lifting the vibration plate upward.

[0017] Furthermore, the vibration plate includes a heavy plate and a plurality of light plates, the heavy plate is stacked, aligned and fastened to the plurality of light plates, and the total mass of the vibration plate is adjusted by adjusting the number of the light plates.

[0018] Furthermore, the vibration sensing device includes a force sensor and an acceleration sensor; a force sensor is arranged at the bottom of the first vibration-damping element and the second vibration-damping element; acceleration sensors are arranged at the top of the light vibrator and the light plate, as well as the first base and the second base; the force sensor is used to collect the force response in the test vibration system; the acceleration sensor is used to collect the acceleration response in the test vibration system.

[0019] Furthermore, the lifting and hoisting mechanism includes a portal frame, a hoisting hook and a loading device; the crossbeam of the portal frame is symmetrically provided with hoisting hooks, and the hoisting hooks are used for long-distance hoisting of the test mechanism; the crossbeam of the portal frame is provided with the loading device, and the loading device is used to apply a load to the test mechanism; the bottom of the portal frame is slidably matched with the slide groove, and is fixedly connected to the base plate after sliding to a specified position.

[0020] Furthermore, the loading device includes one or more of a handheld hammer, a drop hammer, a vibration exciter, and an actuator.

[0021] Furthermore, the loading device is the handheld hammer, which vertically hammers the single-degree-of-freedom vibrator or the center of the top surface of the vibration plate, and the internal force sensor of the handheld hammer measures the pulse excitation force input to the vibration system;

[0022] Or, the loading device is the drop hammer, which is released to freely impact the single-degree-of-freedom vibrator or the center of the top surface of the vibration plate, and the magnitude of each excitation force is controlled to be maintained at a desired force value by controlling the drop hammer height;

[0023] Or, the loading device is the exciter, the exciter applies a load downward, the excitation point is at the center of the top surface of the single-degree-of-freedom vibrator or the vibration plate, a specific frequency or swept frequency sinusoidal load or pulse excitation or white noise excitation is applied, and a force sensor is provided at the head of the exciter loading rod to measure the excitation force input to the vibration system;

[0024] Alternatively, the loading device is the actuator, the actuator applies a load downward, the excitation point is at the center of the top surface of the single-degree-of-freedom vibrator or the vibration plate, a specific frequency or swept frequency sinusoidal load or pulse excitation or white noise excitation is applied, or the wheel-rail force load spectrum applies wheel-rail force excitation, and a force sensor is provided on the actuator head to measure the excitation force input to the vibration system.

[0025] Beneficial effects of the present invention:

[0026] The vibration reduction test platform provided by the present invention realizes a comprehensive simulation of the vibration characteristics of the floating plate track by integrating a single-degree-of-freedom simulation test mechanism and a four-point support plate simulation test mechanism, and can respectively perform accurate tests on the vertical rigid body vibration mode corresponding to the first-order natural frequency and higher-order rigid body vibration modes, bending modes and torsional modes; the platform enables the natural frequency to flexibly match the vibration characteristics of the actual line track through the adjustability of the vibrator mass, thereby enhancing the adaptability and accuracy of the test; in addition, the vibration sensor device configured on the platform can measure and record the force response and acceleration response of the vibration system in real time, and analyze the vibration characteristics and vibration reduction effects in different frequency bands by means of transfer function calculation, providing a scientific basis for the performance evaluation of the vibration reduction element; at the same time, the slide groove structure on the bottom plate makes the layout of each test mechanism flexible, and the coordinated use of the jacking and hoisting mechanism significantly improves the installation efficiency and operation convenience of the test device. The overall platform is not only reasonable in structure but also comprehensive in function, and provides efficient and reliable test support for the vibration characteristic research of the floating plate track and the performance optimization of the vibration reduction element. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 This is a schematic diagram of the vibration reduction test platform structure;

[0028] Figure 2 It is a schematic diagram of the structure of a single-degree-of-freedom simulation test mechanism;

[0029] Figure 3 It is a structural diagram of a four-point support plate simulation test mechanism;

[0030] Figure 4 Schematic diagram of the rigid limit rod structure.

[0031] 1. Vibration reduction test platform; 10. Single-degree-of-freedom simulation test mechanism; 20. Four-point support plate simulation test mechanism; 30. Vibration sensing device; 40. Bottom plate; 50. Lifting and hoisting mechanism; 11. First base; 12. Single-degree-of-freedom vibrator; 13. First vibration reduction element; 14. First jack; 15. Rigid limiting column; 121. Heavy vibrator; 122. Light vibrator; 151. Spline shaft; 152. Spline nut; 21. Second base; 22. Second vibration reduction element; 23. Second jack; 24. Vibration plate; 241. Heavy plate; 242. Light plate; 31. Force sensor; 32. Acceleration sensor; 41. Slide; 51. Door frame; 52. Hoisting hook; 53. Loading device. DETAILED DESCRIPTION

[0032] In order to make the objectives, technical solutions and advantages of the present invention clearer, the present application will be further described in detail below in conjunction with the accompanying drawings. The described embodiments should not be regarded as limiting the present invention. All other embodiments obtained by ordinary technicians in the field without making creative work are within the scope of protection of the present invention.

[0033] In the following description, reference is made to "some embodiments", which describe a subset of all possible embodiments, but it is understood that "some embodiments" may be the same subset or different subsets of all possible embodiments, and may be combined with each other without conflict. Unless otherwise defined, all technical and scientific terms used in the embodiments of the present invention have the same meaning as those commonly understood by those skilled in the art to which the embodiments of the present invention pertain. The terms used in the embodiments of the present invention are only for the purpose of describing the embodiments of the present invention and are not intended to limit the present invention.

[0034] Those skilled in the art should understand that in the following description of the embodiments of the present invention, the order of serial numbers does not mean the order of execution, some or all of the steps can be executed in parallel or sequentially, and the execution order of each process should be determined by its function and internal logic, and should not constitute any limitation on the implementation process of the embodiments of the present invention.

[0035] The terms used in the embodiments of the present invention are only for the purpose of describing specific embodiments, and are not intended to limit the present invention. The singular forms "a", "an" and "the" used in the embodiments of the present invention and the appended claims are also intended to include plural forms, unless the context clearly indicates other meanings.

[0036] This embodiment provides a vibration reduction test platform 1, such as Figure 1 As shown. The vibration reduction test platform 1 includes:

[0037] The single-degree-of-freedom simulation test mechanism 10 is used to simulate the first-order vertical rigid body vibration mode shape corresponding to the first-order natural frequency of the floating slab track, and adjust the natural frequency to correspond to the first-order natural frequency of the actual line track by adjusting the total mass of the single-degree-of-freedom vibrator 12;

[0038] The four-point support plate simulation test mechanism 20 is used to simulate the high-order rigid body vibration mode vibration mode, bending and torsion mode vibration mode in the higher frequency range of the floating plate track, and the total mass of the vibration plate 24 is adjusted to adjust the vibration frequency to correspond to the high-frequency vibration of the actual line track;

[0039] The vibration sensing device 30 is arranged on the single-degree-of-freedom simulation test mechanism 10 and the four-point support plate simulation test mechanism 20, and is used to measure and collect force response and acceleration response, and calculate the transfer function between the input and output of the vibration system, and analyze the vibration characteristics and vibration reduction effect in each frequency band;

[0040] The bottom plate 40; the bottom plate 40 is symmetrically provided with slide grooves 41, and the single-degree-of-freedom simulation test mechanism 10 and the four-point support simulation test mechanism are arranged side by side on the bottom plate 40 and are located between the symmetrical slide grooves 41;

[0041] The lifting and hoisting mechanism 50 is located on the bottom plate 40 and is slidably connected to the slide groove 41 for lifting and transporting the test mechanism, installing the loading mechanism and adjusting the test operation.

[0042] The vibration reduction test platform 1 provided in this embodiment realizes the accurate simulation of the vibration characteristics of the floating plate track and the comprehensive test of the vibration reduction performance through the organic combination of various components. The platform includes a single-degree-of-freedom simulation test mechanism 10, which is used to simulate the first-order vertical rigid body vibration mode vibration type corresponding to the first-order natural frequency of the floating plate track. By adjusting the total mass of the single-degree-of-freedom vibrator 12, the natural frequency of the system can be changed to match the first-order natural frequency of the actual line track, thereby ensuring the accuracy of the test results. The mechanism provides the necessary vertical elastic support and lateral stability through vibration reduction elements and rigid limit columns 15, thereby ensuring the reliability of the vibration trajectory and dynamic response of the vibrator.

[0043] The four-point support plate simulation test mechanism 20 is used to simulate the high-order rigid body vibration mode vibration mode in a higher frequency range, as well as the bending mode and torsion mode of the floating plate track. The vibration plate 24 is used as a core component. By adjusting the total mass of the vibration plate 24, the natural frequency of the high-order mode vibration mode is changed to accurately restore the dynamic behavior of the actual track.

[0044] The vibration sensing device 30 is installed on the single-degree-of-freedom simulation test mechanism 10 and the four-point support plate simulation test mechanism 20, and can measure and record the force response and acceleration response in the test system. By collecting and processing these data in real time, the sensing mechanism can calculate the transfer function between the input and output of the vibration system, further analyze the vibration characteristics and vibration reduction effects in different frequency bands, and provide a scientific basis for optimizing the performance of vibration reduction components.

[0045] The bottom plate 40 serves as the supporting foundation of the platform, on which the slide grooves 41 are symmetrically arranged, and the single-degree-of-freedom simulation test mechanism 10 and the four-point support plate simulation test mechanism 20 are arranged side by side on the bottom plate 40 and located between the slide grooves 41. The slide groove 41 structure not only facilitates the position adjustment of the test mechanism, but also enhances the layout flexibility of the platform to meet the needs of various test scenarios.

[0046] The lifting and hoisting mechanism 50 is located on the bottom plate 40 and is slidably connected to the slide groove 41. The mechanism can be used for lifting and transporting the test device and installing and adjusting the loading equipment. During the test, the lifting and hoisting mechanism 50 can accurately adjust the position and height of the test device to ensure the accuracy of the loading operation, while facilitating the replacement of the vibration reduction element and the flexible adjustment of the test conditions.

[0047] The vibration reduction test platform 1 of this embodiment realizes comprehensive simulation and testing of the floating plate track from the first-order rigid body mode to the higher-order mode through the combination of the single-degree-of-freedom simulation test mechanism 10 and the four-point support plate simulation test mechanism 20, as well as the cooperation of the vibration sensor device 30, the base plate 40 and the jacking and hoisting mechanism 50. It has high precision, high efficiency and flexibility, and provides an important experimental tool for the research of track vibration reduction technology.

[0048] In some embodiments, Figure 2 As shown. The single-degree-of-freedom simulation test mechanism 10 includes a first base 11, a single-degree-of-freedom vibrator 12, a first vibration-damping element 13, a first jack 14 and a rigid limit column 15; the first base 11 is fixedly connected to the bottom plate 40, a plurality of rigid limit columns 15 are vertically inserted and fixed on the first base 11, and the first vibration-damping element 13 is arranged at the center; the single-degree-of-freedom vibrator 12 is arranged above the first vibration-damping element 13, the single-degree-of-freedom vibrator 12 is provided with a through hole, and is vertically slidably matched with the rigid limit column 15 through the through hole; the jacks are symmetrically arranged on both sides of the first vibration-damping element 13, the bottom of the jack is fixedly connected to the bottom plate 40, and the top is in contact with the single-degree-of-freedom vibrator 12, which is used to retract and lift the single-degree-of-freedom vibrator 12 upward. More specifically, the first base 11 is a base made of reinforced concrete, in a square shape, with dimensions of 1.5m long × 1.5m wide × 0.3m high, and is cast or bolted to the base plate 40; four smooth rigid limit columns 15 are vertically inserted into the four corners of the first base 11, and their bottoms are cast and fixed in the first base 11 and installed vertically; a first vibration reduction element 13 is placed in the center of the first base 11, and two first jacks 14 with the same performance are symmetrically arranged on both sides, and the bottom of the first jack 14 is fixed to the first base 11. On the base 11, the top can be retracted and lift heavy objects upward; a single-degree-of-freedom vibrator 12 is placed above the first vibration-damping element 13, which is 1.5m long and 1.5m wide. Through holes are opened at the four corners to allow four rigid limit columns 15 to pass through. The aperture of the through holes is slightly larger than the rigid limit columns 15. During the normal vertical vibration of the single-degree-of-freedom vibrator 12, the friction with the rigid limit columns 15 is ensured to be as small as possible. When the single-degree-of-freedom vibrator 12 is about to overturn due to eccentric load or other circumstances, the rigid limit columns 15 play a lateral protection role.

[0049] The first base 11 is used as the bearing foundation of the entire mechanism. It is made of reinforced concrete and has high strength and stability. The square shape and size of the base of 1.5m×1.5m×0.3m ensure its sufficient bearing capacity, and it is fixed to the bottom plate 40 by casting or bolts to provide a solid support platform. Four smooth rigid limit columns 15 are vertically inserted and fixed at the four corners of the base. These limit columns are tightly combined with the base in structure to ensure its verticality, so as to provide reliable lateral restriction for the vertical movement of the single-degree-of-freedom vibrator 12.

[0050] The single-degree-of-freedom vibrator 12 is arranged above the first vibration-damping element 13, and its length and width are the same as the base. The through holes opened at the four corners are slightly larger than the diameter of the rigid limit column 15, allowing the single-degree-of-freedom vibrator 12 to slide vertically along the rigid limit column 15 while minimizing the friction during the movement. The rigid limit column 15 is not only used to limit the movement direction of the single-degree-of-freedom vibrator 12, but also prevents the vibrator from overturning when an eccentric load is applied or in other special circumstances, and plays a role in lateral protection, thereby improving the safety of the test and the reliability of the data.

[0051] The first vibration-damping element 13 is placed at the center of the first base 11 to provide elastic support for the single-degree-of-freedom vibrator 12, so that the entire system has dynamic characteristics that simulate the vertical rigid body mode of the actual floating plate track during vibration. Through the elastic deformation of the vibration-damping element, the single-degree-of-freedom vibrator 12 can generate a vibration response according to the set natural frequency.

[0052] The first jacks 14 arranged symmetrically on both sides are used to assist in adjusting the height of the single-degree-of-freedom vibrator 12. The bottom of the jack is fixed on the first base 11, and the top can be freely extended and directly contact the single-degree-of-freedom vibrator 12. Through the lifting function of the jack, the test personnel can easily replace the first vibration reduction element 13 or adjust the initial position of the vibrator, while providing the necessary mechanical support for specific test conditions.

[0053] The single-degree-of-freedom simulation test mechanism 10 achieves accurate restoration of the first-order modal vibration type of the track through the close cooperation of the first base 11, the rigid limit column 15, the first vibration damping element 13, the first jack 14 and the single-degree-of-freedom vibrator 12, ensuring the authenticity of the system vibration response and the validity of the test data.

[0054] In some embodiments, Figure 2 As shown. The single-degree-of-freedom vibrator 12 includes a heavy vibrator 121 and a plurality of light vibrators 122, which are stacked, aligned and fastened with the heavy vibrator 121 and the plurality of light vibrators 122, and the total mass of the single-degree-of-freedom vibrator 12 is adjusted by adjusting the number of light vibrators 122. More specifically, the single-degree-of-freedom vibrator 12 includes two parts, a heavy vibrator 121 made of reinforced concrete with a size of 1.5m long × 1.5m wide × 0.3m thick, and a plurality of light vibrators 122 made of reinforced concrete with a size of 1.5m long × 1.5m wide × 0.05m thick, and the heavy vibrator 121 and the plurality of light vibrators 122 are stacked together, aligned and pre-tightened by vertically penetrating all vibrator bolts through a pre-tightening bolt rod so that all vibrators form a whole, and the total mass of the single-degree-of-freedom vibrator 12 is adjusted by adjusting the number of light vibrators 122, and the total mass of the single-degree-of-freedom vibrator 12 is about 2t and can be adjusted.

[0055] The single-degree-of-freedom vibrator 12 is made of reinforced concrete, and includes a heavy vibrator 121 and several light vibrators 122. The dimensions of the heavy vibrator 121 are 1.5m long × 1.5m wide × 0.3m thick. As the main part of the single-degree-of-freedom vibrator 12, its large mass and volume provide the basic inertial characteristics for the system. The dimensions of the light vibrator 122 are 1.5m long × 1.5m wide × 0.05m thick, which is consistent with the dimensions of the heavy vibrator 121 but thinner, and is designed as a stackable auxiliary mass block. The heavy vibrator 121 and the light vibrator 122 are penetrated and fixed together by pre-tightening bolt rods in the vertical direction to form an integral structure. During the assembly process, the various parts of the vibrator are strictly aligned, and the stability and consistency of the vibrator structure are ensured by the pre-tightening force of the bolts to avoid loosening or uneven mass distribution during the test.

[0056] By adjusting the number of light vibrators 122, the total mass of the single-degree-of-freedom vibrator 12 can be flexibly changed, thereby adjusting the natural frequency of the vibration system to match the natural frequency of the first-order mode of the actual floating plate track. For example, by increasing or decreasing the number of light vibrators 122, the total mass of the vibrator can be accurately changed without changing other system parameters, making the system more adaptable and accurate in the test. It not only meets the needs of simulating vibration characteristics under various track conditions, but also reduces the risk of inaccurate test results due to frequency errors.

[0057] During the vibration test, the single-degree-of-freedom vibrator 12 is the main vibration element, and its total mass directly affects the dynamic behavior of the system. When the vibrator is excited by an external force, its vibration characteristics are determined by the total mass of the vibrator, the elastic stiffness of the vibration-reducing element, and the damping characteristics. By adjusting the number of light vibrators 122, the tester can easily control the mass distribution of the vibrator to make it consistent with the vibration frequency characteristics of the target track, thereby effectively reproducing the vibration mode of the track under actual operating conditions.

[0058] In some embodiments, Figure 4 As shown. The rigid limit column 15 includes a ball spline screw structure, and the ball spline screw structure includes a spline shaft 151 and a spline nut 152. The bottom of the spline shaft 151 is fixedly connected to the base plate 40, and the spline nut 152 is fixedly connected to the bottom of the heavy vibrator 121, and is slidably fitted with the spline shaft 151. More specifically, the bottom of the spline shaft 151 is cast and fixed in the first base 11 to ensure verticality, and the spline nut 152 is cast and fixed or bolted in the heavy vibrator 121 of the single-degree-of-freedom vibrator 12. The spline nut 152 can move smoothly in a straight line along the spline shaft 151, with small friction and small gap, thereby ensuring that the single-degree-of-freedom vibrator 12 vibrates smoothly in the vertical direction, and the vertical friction and lateral shaking problems can be ignored.

[0059] The ball spline screw structure consists of a spline shaft 151 and a spline nut 152. The bottom of the spline shaft 151 is cast and fixed in the first base 11, and is strictly controlled for verticality to ensure its stability and precise positioning in the system. The spline nut 152 is fixed to the heavy vibrator 121 of the single-degree-of-freedom vibrator 12 by casting or bolting, forming an integrated connection with the overall structure of the vibrator. This structural design ensures that the vibrator can achieve precise linear sliding along the spline shaft 151 when moving vertically.

[0060] The spline shaft 151 and the spline nut 152 are slidably matched by ball transmission. The design features of the ball transmission are low friction and smooth movement, which effectively reduce the energy loss of the vibrator during vertical movement during the test, and reduce the test error caused by friction. In addition, the gap between the spline shaft 151 and the spline nut 152 is precisely controlled to ensure that it is small enough to reduce lateral shaking, thereby improving the stability of the test system and data accuracy. The silky linear motion characteristics of the spline nut 152 make the vertical vibration of the vibrator more stable, avoiding the jamming or uneven damping that may exist in traditional limit devices.

[0061] An important function of this structure is to provide necessary constraints to prevent the single-degree-of-freedom vibrator 12 from lateral displacement or overturning when it is vertically excited. When the vibrator has an eccentric moment due to the applied load, the mechanical fit between the spline shaft 151 and the spline nut 152 can provide lateral support in time to ensure that the vibrator can still maintain stable vibration in the vertical direction, thereby improving the anti-interference ability of the system and the safety of the test.

[0062] The application of the ball spline screw structure significantly optimizes the motion characteristics of the single-degree-of-freedom vibrator 12, which not only ensures the vertical vibration accuracy of the vibrator, but also effectively suppresses the lateral shaking problem, providing a stable and reliable operating environment for the dynamic response analysis of the system.

[0063] In some embodiments, Figure 3The four-point support simulation test mechanism includes a second base 21, a second vibration-damping element 22, a second jack 23 and a vibration plate 24; the second base 21 is fixedly connected to the bottom plate 40, a plurality of second vibration-damping elements 22 are arranged at the corners, and a vibration plate 24 is arranged on the top of the plurality of second vibration-damping elements 22; the second jacks 23 are symmetrically arranged on the second bottom plate 40, the bottom of the second jacks 23 is fixedly connected to the bottom plate 40, and the top is in contact with the vibration plate 24, so as to extend and lift the vibration plate 24 upward. More specifically, the second base 21 is made of concrete, is in the shape of a plate, has dimensions of 3m×3m×0.3m, and is cast or bolted on the base plate 40; four second vibration-damping elements 22 are symmetrically placed at the four corners of the second base 21, and four second jacks 23 with the same performance are symmetrically installed on the four sides of the second base 21. The bottom of the second jack 23 is fixed on the second base 21, and the top can be retracted and lift heavy objects upward; a vibration plate 24 is placed above the second vibration-damping element 22.

[0064] The second base 21 is used as the support foundation of the entire test mechanism. It is made of concrete and has a size of 3m×3m×0.3m, ensuring sufficient rigidity and stability. The second base 21 is fixed to the base plate 40 by casting or bolting, and provides a solid support platform for the entire mechanism, while providing a basis for the arrangement of vibration reduction elements and jacks. Four second vibration reduction elements 22 are symmetrically arranged at the four corners of the second base 21. These vibration reduction elements are located between the vibration plate 24 and the base, providing elastic support for the vibration plate 24 and simulating the characteristics of the vibration isolator in the floating plate track.

[0065] As a key component, the second vibration-damping element 22 provides damping and stiffness support for the vibration of the vibration plate 24 through its elastic deformation. The position and performance parameters of the second vibration-damping element 22 are carefully designed so that it can effectively restore the dynamic characteristics of the floating plate track in high-order rigid body modes, bending modes and torsional modes, thereby achieving a true reproduction of the vibration behavior.

[0066] Four second jacks 23 with the same performance are symmetrically installed on the four sides of the second base 21. The bottoms of these jacks are fixed on the second base 21, and the tops can be extended and contacted with the vibration plate 24. In actual tests, the jacks are mainly used to lift the vibration plate 24. By adjusting the extension and contraction of the jacks, the test personnel can flexibly replace the second vibration reduction element 22 or adjust the initial position of the vibration plate 24 to adapt to different test conditions or boundary parameters. The design of the jacks further improves the convenience and operating efficiency of the test.

[0067] The vibration plate 24, as the core component of the simulated floating plate track structure, is placed on top of the second vibration reduction element 22, and its vibration behavior is affected by the loading force and boundary conditions. The total mass of the vibration plate 24 is adjusted to adjust the vibration response corresponding to the target vibration mode. The elastic support provided by the second vibration reduction element 22 enables the vibration plate 24 to reflect the complex modal characteristics of the track system under dynamic conditions, including high-order rigid body modes, bending modes, and torsion modes.

[0068] The four-point support simulation test mechanism can truly reproduce the high-order modal vibration characteristics of the floating plate track through reasonable structural layout and functional coordination of various components, providing a reliable test platform for track vibration research under different working conditions. Its rigid base and elastic support system ensure the stability of the test, the jacking function significantly improves the convenience of operation, and the high adaptability of the vibration plate 24 allows the mechanism to be flexibly adjusted to meet different test requirements.

[0069] In some embodiments, Figure 3 As shown. The vibration plate 24 includes a heavy plate 241 and a plurality of light plates 242. The heavy plate 241 is stacked, aligned and fastened with the plurality of light plates 242, and the total mass of the vibration plate 24 is adjusted by adjusting the number of light plates 242. More specifically, the vibration plate 24 includes two parts, a heavy plate 241 made of reinforced concrete with a size of 3m long × 3m wide × 0.3m thick, the number of which is 1, and a plurality of light plates 242 made of reinforced concrete with a size of 3m long × 3m wide × 0.05m thick, the number of which is 3m long × 3m wide × 0.05m thick. The heavy plate 241 and the plurality of light plates 242 are stacked, aligned and pre-tightened by vertically penetrating all plates through pre-tightening bolt rods to form a whole. The total mass of the vibration plate 24 is adjusted by adjusting the number of light plates 242.

[0070] The vibration plate 24 consists of two parts, including a heavy plate 241 made of reinforced concrete and several light plates 242. The heavy plate 241, as the main part of the vibration plate 24, has the dimensions of 3m long × 3m wide × 0.3m thick, providing basic mass inertia and rigid support. The light plate 242 has the same length and width, but is only 0.05m thick. It is designed to achieve flexible adjustment of the total mass of the vibration plate 24 through modular combination. All light plates 242 are stacked together with the heavy plates 241 and connected through pre-tightened bolt rods in the vertical direction to form a whole.

[0071] In actual tests, the total mass of the vibration plate 24 can be flexibly changed by adjusting the number of light plates 242. This adjustment method can accurately match the design requirements of different floating plate track systems. For example, according to the specific working conditions of the track system or the natural frequency of the target mode, the mass of the vibration plate 24 is adapted to achieve true dynamic characteristics restoration. This mass adjustment mechanism provides a high degree of flexibility for simulating high-order rigid body modes, bending modes, and torsional modes, while ensuring that the dynamic response of the vibration plate 24 under the action of the loading force is consistent with the actual track conditions.

[0072] The pre-tightening bolt rods vertically penetrate and tighten the heavy plate 241 and the light plate 242, ensuring the stability and consistency of the overall structure of the vibration plate 24. The bolt pre-tightening force is sufficient to eliminate the relative displacement or looseness between the plate layers, so that the vibration plate 24 can participate in vibration as a complete rigid body under dynamic excitation. In addition, due to the precise alignment and tight connection between the light plate 242 and the heavy plate 241, the center of gravity position and mass distribution of the vibration plate 24 can be kept uniform, further improving the reliability of the test data.

[0073] In some embodiments, Figure 1 , 2 , 3. The vibration sensing device 30 includes a force sensor 31 and an acceleration sensor 32; the force sensor 31 is arranged at the bottom of the first vibration-damping element 13 and the second vibration-damping element 22; the acceleration sensor 32 is arranged at the top of the light vibrator 122 and the light plate 242, and the first base 11 and the second base 21; the force sensor 31 is used to collect the force response in the test vibration system; the acceleration sensor 32 is used to collect the acceleration response in the test vibration system. More specifically, multiple excitation methods are used to excite the single-degree-of-freedom vibrator 12 or the top center of the vibration plate 24, and the acceleration sensor 32 is used to measure the vibration acceleration response of the single-degree-of-freedom vibrator 12, the vibration plate 24, the first base 11 and the second base 21. The force sensor 31 is used to measure the force response transmitted to the first base 11 or the second base 21 via the first vibration damping element 13 or the second vibration damping element 22, and the transfer function between the input and output of the vibration system is calculated. The vibration characteristics and vibration damping effects in each frequency band are analyzed, and the vibration acceleration transmission loss of the upper and lower structures of the first vibration damping element 13 and the second vibration damping element 22 is calculated to evaluate the vibration damping performance. The vibration acceleration response or force response of the first base 11 or the second base 21 without vibration damping elements or with different vibration damping elements is calculated, and the vibration damping performance between different vibration damping elements is compared.

[0074] The force sensor 31 is arranged at the bottom of the first vibration-damping element 13 and the second vibration-damping element 22, and is used to measure in real time the force response of the vibration load transmitted to the first base 11 or the second base 21 through the vibration-damping element. By collecting these force response data, the mechanical properties of the vibration-damping element under different working conditions, such as the magnitude of the transmitted force and its changing law, can be intuitively understood.

[0075] The acceleration sensors 32 are distributed on the top of the light vibrator 122 of the single-degree-of-freedom vibrator 12, the top of the light plate 242 of the vibration plate 24, and the first base 11 and the second base 21, and are used to measure the vibration acceleration response of these key structural components. In the test, by applying various forms of excitation (such as hammering, actuator loading, etc.) to the center of the top of the single-degree-of-freedom vibrator 12 or the vibration plate 24, the acceleration sensor 32 can record the dynamic acceleration characteristics of the test system under the excitation, thereby capturing the response characteristics of the vibration system in different frequency bands.

[0076] The transfer function between the input (loading force) and output (vibration response) of the vibration system can be further calculated by combining the data of the force sensor 31 and the acceleration sensor 32. This transfer function reflects the vibration characteristics of the system at different frequencies and provides a quantitative basis for the test personnel to analyze the modal characteristics, stiffness distribution and damping performance of the system.

[0077] The vibration sensing device 30 also supports the evaluation of the performance of the vibration reduction element. By calculating the transmission loss of the vibration acceleration of the upper and lower structures of the first vibration reduction element 13 and the second vibration reduction element 22, the vibration reduction effect of the vibration reduction element can be quantified. For example, by comparing the acceleration difference of the upper and lower structures in different frequency bands, the vibration isolation capability of the vibration reduction element can be intuitively evaluated. In addition, by comparing the base vibration acceleration response or force response of different vibration reduction elements under the same working conditions, the test personnel can make a comprehensive comparison of the performance of different vibration reduction elements.

[0078] The vibration sensing device 30, through the multi-point arrangement and precise measurement of the force sensor 31 and the acceleration sensor 32, not only realizes a comprehensive analysis of the dynamic characteristics of the system, but also provides key data support for the performance evaluation and optimization of the vibration reduction element.

[0079] In some embodiments, Figure 1 The lifting and hoisting mechanism 50 includes a portal frame 51, a hoisting hook 52 and a loading device 53; the cross beam of the portal frame 51 is symmetrically provided with the hoisting hook 52, and the hoisting hook 52 is used for long-distance hoisting of the test mechanism; the cross beam of the portal frame 51 is provided with a loading device 53, and the loading device 53 is used to apply a load to the test mechanism; the bottom of the portal frame 51 is slidably matched with the slide groove 41, and is fixedly connected with the bottom plate 40 after sliding to a specified position.

[0080] The portal frame 51 is the core structure of the lifting and hoisting mechanism 50, which is composed of a crossbeam and supporting columns. Its width and height are designed to cover the range of the single-degree-of-freedom simulation test mechanism 10 and the four-point support plate simulation test mechanism 20, while ensuring sufficient rigidity and stability. The bottom of the portal frame 51 cooperates with the slide groove 41 on the bottom plate 40 through a pulley, so that the frame can slide smoothly along the slide groove 41. During the test preparation or adjustment process, the portal frame 51 can slide to the target test position and be firmly connected to the bottom plate 40 through a fixing device, thereby ensuring the accuracy and safety of the lifting and loading operations.

[0081] The crossbeam of the portal frame 51 is symmetrically provided with a lifting hook 52 for long-distance lifting of the test mechanism. When the test device needs to be moved or adjusted, the lifting hook 52 is used in conjunction with the steel rope and pulley to lift the test mechanism from the ground and move it smoothly to the designated position. This structure effectively reduces the complexity and safety risks of manual handling, while improving the efficiency of test preparation.

[0082] The loading device 53 is installed on the crossbeam of the portal frame 51 and is used to apply various forms of loading force to the test mechanism. The loading device 53 may include different types such as a force hammer, a drop hammer, an exciter or an actuator, and the appropriate loading form is selected according to the test requirements. The loading point is usually located at the center of the single-degree-of-freedom vibrator 12 or the vibration plate 24. A load of a specific frequency, amplitude or waveform is applied by the loading device 53, such as pulse excitation or sinusoidal loading, to excite the target vibration mode of the test mechanism. The installation position of the loading device 53 can be adjusted with the sliding of the portal frame 51 to achieve compatibility with different test mechanisms.

[0083] Through the coordinated action of the portal frame 51, the hoisting hook 52 and the loading device 53, the lifting and hoisting mechanism 50 not only completes the hoisting and transportation of the test mechanism, but also provides a stable loading platform, effectively reducing the interference to the test data that may be caused during the loading process. Its flexible sliding design improves site adaptability, supports the operation requirements of various test mechanisms and test conditions, and provides high-precision operation support for the dynamic loading of the test system, becoming an important auxiliary device for the entire test platform.

[0084] In some embodiments, Figure 1 As shown. The loading device 53 includes one or more of a handheld hammer, a drop hammer, a vibration exciter, and an actuator. More specifically, these loading devices 53 or excitation methods avoid coupling with the test mechanism and do not change the set vibration frequency of the test mechanism. Moreover, these loading devices 53 are installed on the portal frame 51 and can move with it to take into account the loading of the single-degree-of-freedom test mechanism and the four-point support plate test mechanism.

[0085] In some embodiments, the loading device 53 is a handheld hammer, which vertically strikes the center of the top surface of the single-degree-of-freedom vibrator 12 or the vibration plate 24, and the internal force sensor 31 of the handheld hammer measures the pulse excitation force input to the vibration system;

[0086] Or, the loading device 53 is a drop hammer, which is released to freely impact the center of the top surface of the single-degree-of-freedom vibrator 12 or the vibration plate 24, and the magnitude of each excitation force is controlled to be maintained at a desired force value by controlling the drop hammer height;

[0087] Or, the loading device 53 is a vibration exciter, which applies a load downward, with the excitation point at the center of the top surface of the single-degree-of-freedom vibrator 12 or the vibration plate 24, applying a specific frequency or swept frequency sinusoidal load or a pulse excitation or a white noise excitation, and a force sensor 31 is provided at the head of the vibration exciter loading rod to measure the excitation force input to the vibration system;

[0088] Alternatively, the loading device 53 is an actuator, which applies a load downward, with the excitation point at the center of the top surface of the single-degree-of-freedom vibrator 12 or the vibration plate 24, applying a specific frequency or a swept frequency sinusoidal load or a pulse excitation or a white noise excitation, or applying a wheel-rail force excitation using a wheel-rail force load spectrum, and a force sensor 31 is provided at the actuator head to measure the excitation force input to the vibration system.

[0089] The loading device 53 provides the testing organization with flexible and accurate loading functions through various forms of excitation to meet the different needs of rail vibration characteristic research, while avoiding the coupling effect during the loading process, thereby ensuring that the dynamic characteristics of the test system remain unchanged.

[0090] When the loading device 53 is a handheld hammer, the operator uses the hammer to vertically hammer the center of the top surface of the single-degree-of-freedom vibrator 12 or the vibration plate 24 to apply a short-time pulse excitation. The hammer is equipped with a force sensor 31, which can measure the pulse excitation force input to the vibration system in real time to ensure that the amplitude and direction of the loading force meet the test requirements. This excitation method is simple and efficient, and is particularly suitable for studying the transient vibration response of the system in the low-frequency band.

[0091] When the loading device 53 is a drop weight, the drop weight falls freely through the release mechanism to impact the top center of the single-degree-of-freedom vibrator 12 or the vibration plate 24, and the excitation force applied is determined by the height and weight of the drop weight. The non-contact characteristic of the drop weight loading method effectively avoids mechanical coupling with the test mechanism, ensuring that the natural frequency of the test system is not affected.

[0092] When the loading device 53 is an exciter, the exciter applies the load downward through the loading rod, and the excitation point is set at the center of the top surface of the single-degree-of-freedom vibrator 12 or the vibration plate 24. The exciter can apply a specific frequency, a swept frequency sinusoidal load or a pulse excitation or a white noise excitation, thereby stimulating the vibration response of the test mechanism in different frequency bands. The force sensor 31 equipped at the head of the exciter loading rod can record the dynamic force signal input to the vibration system in real time to ensure the accuracy of the loading process and the reliability of the data.

[0093] When the loading device 53 is an actuator, the actuator can simulate more complex dynamic loading conditions, such as applying a wheel-rail force load spectrum to reproduce the rail vibration characteristics under real working conditions. The actuator can apply a specific frequency, a swept frequency sine load or a pulse excitation or a white noise excitation downward, or directly apply a wheel-rail force load spectrum, and its loading point is also located at the top center of the single-degree-of-freedom vibrator 12 or the vibration plate 24. The loading amplitude of the actuator is larger, which is suitable for high-intensity dynamic testing requirements. At the same time, the force sensor 31 equipped on its head ensures the accurate measurement of the loading signal.

[0094] Regardless of the loading device 53 used, these excitation methods are installed on the portal frame 51, and the sliding design of the frame realizes compatible loading of the single-degree-of-freedom test mechanism and the four-point support plate test mechanism. The non-contact design of the loading device 53 and the test mechanism avoids the coupling effect, ensuring that the natural frequency of the test mechanism is not disturbed by the outside world during the loading process, thereby ensuring the accuracy and reliability of the test results.

[0095] The above is only a specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any person skilled in the art can easily think of changes or substitutions within the technical scope disclosed by the present invention, which should be included in the protection scope of the present invention. Therefore, the protection scope of the present invention should be based on the protection scope of the claims.

Claims

1. A vibration reduction test platform, characterized in that: The vibration reduction test platform comprises: A single-degree-of-freedom simulation test mechanism is used to simulate the first-order vertical rigid body vibration mode shape corresponding to the first-order natural frequency of the floating slab track, and adjust the natural frequency to correspond to the first-order natural frequency of the actual line track by adjusting the total mass of the single-degree-of-freedom vibrator; The four-point support plate simulation test mechanism is used to simulate the high-order rigid body vibration mode vibration mode, bending and torsion mode vibration mode in the higher frequency range of the floating plate track, and adjust the vibration frequency to correspond to the high-frequency vibration of the actual line track by adjusting the total mass of the vibration plate; A vibration sensing device, arranged on the single-degree-of-freedom simulation test mechanism and the four-point support plate simulation test mechanism, is used to measure and collect force response and acceleration response, calculate the transfer function between the input and output of the vibration system, and analyze the vibration characteristics and vibration reduction effect in each frequency band; Bottom plate; the bottom plate is symmetrically provided with slide grooves, the single-degree-of-freedom simulation test mechanism and the four-point support simulation test mechanism are arranged side by side on the bottom plate and are located between the symmetrical slide grooves; The lifting and hoisting mechanism is located on the bottom plate and is slidably connected with the slide groove, and is used for lifting and transporting the test mechanism, installing the loading mechanism and adjusting the test operation.

2. A vibration reduction test platform according to claim 1, characterized in that: The single-degree-of-freedom simulation test mechanism includes a first base, a single-degree-of-freedom vibrator, a first vibration-damping element, a first jack and a rigid limiting column; The first base is fixedly connected to the bottom plate, a plurality of the rigid limiting columns are vertically inserted and fixed on the first base, and the first vibration-damping element is arranged at the center position; the single-degree-of-freedom vibrator is arranged above the first vibration-damping element, the single-degree-of-freedom vibrator is provided with a through hole, and is vertically slidably matched with the rigid limiting column sleeve through the through hole; the jack is symmetrically arranged on both sides of the first vibration-damping element, the bottom of the jack is fixedly connected to the bottom plate, and the top is in contact with the single-degree-of-freedom vibrator, so as to be used for retracting and lifting the single-degree-of-freedom vibrator upward.

3. A vibration reduction test platform according to claim 2, characterized in that: The single-degree-of-freedom vibrator comprises a heavy vibrator and a plurality of light vibrators. The heavy vibrator is stacked, aligned and fastened to the plurality of light vibrators, and the total mass of the single-degree-of-freedom vibrator is adjusted by adjusting the number of the light vibrators.

4. A vibration reduction test platform according to claim 3, characterized in that: The rigid limiting column includes a ball spline screw structure, and the ball spline screw structure includes a spline shaft and a spline nut. The bottom of the spline shaft is fixedly connected to the base plate, and the spline nut is fixedly connected to the bottom of the heavy vibrator and slidingly cooperates with the spline shaft sleeve.

5. A vibration reduction test platform according to claim 1, characterized in that: The four-point support simulation test mechanism includes a second base, a second vibration reduction element, a second jack and a vibration plate; The second base is fixedly connected to the bottom plate, and a plurality of the second vibration-damping elements are arranged at the corners, and the vibration plate is arranged on the top of the plurality of the second vibration-damping elements; the second jacks are symmetrically arranged on the second bottom plate, and the bottom of the second jacks is fixedly connected to the bottom plate, and the top abuts against the vibration plate, so as to be used for retracting and lifting the vibration plate upward.

6. A vibration reduction test platform according to claim 5, characterized in that: The vibration plate comprises a heavy plate and a plurality of light plates, wherein the heavy plate is stacked, aligned and fastened to the plurality of light plates, and the total mass of the vibration plate is adjusted by adjusting the number of the light plates.

7. A vibration reduction test platform according to any one of claims 3 and 6, characterized in that: The vibration sensing device includes a force sensor and an acceleration sensor; the force sensor is arranged at the bottom of the first vibration-damping element and the second vibration-damping element; the top of the light vibrator and the light plate, as well as the first base and the second base are arranged with acceleration sensors; the force sensor is used to collect the force response in the test vibration system; the acceleration sensor is used to collect the acceleration response in the test vibration system.

8. A vibration reduction test platform according to claim 1, characterized in that: The lifting and hoisting mechanism includes a portal frame, a hoisting hook and a loading device; the crossbeam of the portal frame is symmetrically provided with hoisting hooks, and the hoisting hooks are used for long-distance hoisting of the test mechanism; the crossbeam of the portal frame is provided with the loading device, and the loading device is used to apply a load to the test mechanism; the bottom of the portal frame is slidably matched with the slide groove, and is fixedly connected to the base plate after sliding to a specified position.

9. A vibration reduction test platform according to claim 8, characterized in that: The loading device includes one or more of a handheld hammer, a drop hammer, a vibration exciter, and an actuator.

10. A vibration reduction test platform according to claim 9, characterized in that: The loading device is the handheld hammer, which vertically strikes the single-degree-of-freedom vibrator or the center of the top surface of the vibration plate, and the internal force sensor of the handheld hammer measures the pulse excitation force input to the vibration system; Or, the loading device is the drop hammer, which is released to freely impact the single-degree-of-freedom vibrator or the center of the top surface of the vibration plate, and the magnitude of each excitation force is controlled to be maintained at a desired force value by controlling the drop hammer height; Or, the loading device is the exciter, the exciter applies a load downward, the excitation point is at the center of the top surface of the single-degree-of-freedom vibrator or the vibration plate, a specific frequency or swept frequency sinusoidal load or pulse excitation or white noise excitation is applied, and a force sensor is provided at the head of the exciter loading rod to measure the excitation force input to the vibration system; Alternatively, the loading device is the actuator, the actuator applies a load downward, the excitation point is at the center of the top surface of the single-degree-of-freedom vibrator or the vibration plate, a specific frequency or swept frequency sinusoidal load or pulse excitation or white noise excitation is applied, or the wheel-rail force load spectrum applies wheel-rail force excitation, and a force sensor is provided on the actuator head to measure the excitation force input to the vibration system.

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