Track fastener and elastic cushion vertical high-frequency dynamic stiffness testing machine

Abstract

The utility model discloses a rail fastener and elastic cushion vertical high-frequency dynamic stiffness testing machine, which comprises a vertical portal frame and a movable cross beam arranged in the vertical portal frame in a sliding manner, a vertical electromagnetic vibration exciter is mounted at the bottom of the movable cross beam, a static load cross beam and a base are sequentially arranged below the vertical electromagnetic vibration exciter, an inverted oil cylinder connected with the base is installed on the static load cross beam, a through hole allowing a vibration excitation ejector rod installed at the bottom of the vertical electromagnetic vibration exciter to pass through is formed in the static load cross beam, an upper flange, an upper decoupling spring and a lower flange which are coaxial with the vibration excitation ejector rod are sequentially installed at the bottom of the static load cross beam, and an excitation mass block is arranged at the bottom of the lower flange; a tested sample and a retarding mass block are sequentially arranged below the excitation mass block, and an output end dynamic force sensor or a lower decoupling spring is arranged between the retarding mass block and the base. The vertical high-frequency dynamic stiffness testing machine for the track fastener and the elastic cushion layer can be used for a vertical high-frequency dynamic characteristic measurement test of a track fastener system and the elastic cushion layer.

Description

Technical Field

[0001] The utility model relates to the technical field of rail transit testing, in particular to a vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushion layers. Background Art

[0002] Track elastic elements, including fastener systems and elastic cushions in fastener systems, are key elements that provide elasticity in track structures. Their dynamic characteristics (dynamic characteristics are generally described by dynamic stiffness and damping) have an important impact on driving safety, track structure vibration, wheel-rail rolling contact and other wheel-rail interactions. Studies have shown that the dynamic stiffness and damping of elastic elements are not constants, but are affected by multiple factors such as preload, excitation amplitude, excitation frequency, loading history and temperature.

[0003] In actual working conditions, when a train passes through the track at a high speed, it will cause the various components of the track structure to vibrate at a higher frequency. At this time, the elastic element is affected by the train axle weight, that is, the vertical static load; on the other hand, the action between the wheel and the rail produces a high-frequency and wide-band dynamic load excitation. Especially in areas with corrugation, this dynamic excitation is more intense. Under the dual effects of static and dynamic loads, the dynamic characteristics of the elastic element are more complicated.

[0004] At present, the research on the dynamic characteristics of track fastener systems and elastic cushions is mainly concentrated in the field of static stiffness or low-frequency dynamic stiffness. There is no testing equipment in China that can measure the dynamic stiffness and damping of track fastener systems and elastic cushions under high-frequency excitation. Utility Model Content

[0005] The purpose of the utility model is to provide a track fastener and elastic cushion vertical high-frequency dynamic stiffness testing machine, the track fastener and elastic cushion vertical high-frequency dynamic stiffness testing machine can be used for track fastener system and elastic cushion vertical high-frequency dynamic characteristic measurement test, for measuring the fastener system and elastic cushion vertical high-frequency dynamic stiffness and damping characteristics under 20 ~ 1000Hz dynamic excitation, the test results can provide relatively accurate technical parameters, for the subsequent fastener system and elastic cushion design to provide theoretical support and technical guidance.

[0006] In order to achieve the above-mentioned purpose, the utility model provides a vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions, comprising a vertical gantry and a moving crossbeam slidably arranged in the vertical gantry, a vertical electromagnetic exciter is installed at the bottom of the moving crossbeam, a static load crossbeam and a base are arranged in sequence below the vertical electromagnetic exciter, an inverted oil cylinder connected to the base is installed on the static load crossbeam, a through hole is provided on the static load crossbeam for an excitation push rod installed at the bottom of the vertical electromagnetic exciter to pass through, an upper flange coaxial with the excitation push rod, an upper decoupling spring and a lower flange are installed in sequence at the bottom of the static load crossbeam, an excitation mass block is arranged at the bottom of the lower flange, a sample to be tested and a blocking mass block are arranged in sequence below the excitation mass block, and an output end dynamic force sensor or a lower decoupling spring is arranged between the blocking mass block and the base.

[0007] Preferably, a U-shaped frame is installed at the bottom of the moving crossbeam, and the vertical electromagnetic exciter is connected to the U-shaped frame through an air spring.

[0008] Preferably, an upper pressure plate for pressing the air spring is arranged on the outer side of the vertical electromagnetic exciter housing, and a lower pressure plate for supporting the air spring is arranged on the inner side of the U-shaped frame.

[0009] Preferably, the movable cross beam is provided with a guide hole for the oil cylinder to pass through.

[0010] Preferably, a plurality of polished rods penetrating the static load beam are arranged on the base, and a locking device capable of being locked on the polished rods is arranged at the bottom of the static load beam.

[0011] Preferably, a T-shaped adapter is installed at the bottom of the excitation mass block.

[0012] Preferably, the upper end of the lower decoupling spring is connected to the blocking mass block through an upper flange, and the lower end is connected to the base through a lower flange.

[0013] Preferably, the output end dynamic force sensor is connected to the base via an adapter plate.

[0014] Preferably, the inner sides of the columns on both sides of the vertical gantry are provided with sliding grooves for the sliding of the movable crossbeam, and the sliding grooves are provided with screws that cooperate with the threads of the movable crossbeam. A driving mechanism that drives the screws on both sides to rotate synchronously is provided on the static crossbeam at the upper end of the vertical gantry.

[0015] Preferably, the driving mechanism comprises a dual-axis motor arranged in the middle of the static beam, and the output shafts at both ends of the dual-axis motor are connected to the lead screw through two mutually meshing bevel gears.

[0016] According to the above technical scheme, the utility model provides a vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions, which is used to measure the vertical high-frequency dynamic stiffness and damping characteristics of the fastener system or elastic cushion under 20-1000Hz dynamic excitation. The test results can provide relatively accurate technical parameters, providing theoretical support and technical guidance for the subsequent design of fastener systems and elastic cushions.

[0017] Other features and advantages of the present invention will be described in detail in the subsequent specific implementation section. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The accompanying drawings are used to provide a further understanding of the present invention and constitute a part of the specification. Together with the following specific embodiments, they are used to explain the present invention, but do not constitute a limitation to the present invention. In the accompanying drawings:

[0019] Figure 1 This is the front view of the track fastener system and elastic cushion vertical high-frequency dynamic stiffness testing machine of the direct method tooling system;

[0020] Figure 2 It is an axonometric view of the track fastener system and elastic cushion vertical high-frequency dynamic stiffness testing machine of the direct method tooling system;

[0021] Figure 3 This is the front view of the track fastener system and elastic cushion vertical high-frequency dynamic stiffness testing machine of the indirect method tooling system;

[0022] Figure 4 It is an axonometric view of the track fastener system and elastic cushion vertical high-frequency dynamic stiffness testing machine of the indirect method tooling system;

[0023] Figure 5 It is a schematic diagram of the connection structure of a preferred embodiment of the driving mechanism.

[0024] Description of Reference Numerals

[0025] 1-base; 2-locking device; 3-static load beam; 4-light rod; 5-oil cylinder; 6-column; 7-moving beam; 8-vertical electromagnetic exciter; 9-U-shaped frame; 10-air spring; 11-excitation top rod; 12-upper flange; 13-upper decoupling spring; 14-lower flange; 15-excitation mass block; 16-T-type transfer table; 17-tested sample; 18-blocking mass block; 19-output end dynamic force sensor or lower decoupling spring; 20-adapter plate; 21-slideway; 22-screw; 23-guide hole; 24-bevel gear; 25-output shaft; 26-dual-axis motor; 27-static beam; 28-upper pressure plate; 29-lower pressure plate. DETAILED DESCRIPTION

[0026] The specific implementation of the present invention is described in detail below in conjunction with the accompanying drawings. It should be understood that the specific implementation described here is only used to illustrate and explain the present invention, and is not used to limit the present invention.

[0027] In the present utility model, unless otherwise stated, directional words contained in terms such as "up, down, left, right, front, back, inside, outside" merely represent the orientation of the terms in normal usage, or are common names understood by those skilled in the art, and should not be regarded as limitations on the terms.

[0028] See also Figure 1-5 The vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions shown in the figure comprises a vertical gantry and a moving crossbeam 7 slidably arranged in the vertical gantry, a vertical electromagnetic exciter 8 is installed at the bottom of the moving crossbeam 7, a static load crossbeam 3 and a base 1 are arranged in sequence below the vertical electromagnetic exciter 8, an inverted oil cylinder 5 connected to the base 1 is installed on the static load crossbeam 3, a through hole is provided on the static load crossbeam 3 for the passage of an excitation push rod 11 installed at the bottom of the vertical electromagnetic exciter 8, an upper flange 12 coaxial with the excitation push rod 11, an upper decoupling spring 13 and a lower flange 14 are installed in sequence at the bottom of the static load crossbeam 3, an excitation mass block 15 is arranged at the bottom of the lower flange 14, a sample to be tested 17 and a blocking mass block 18 are arranged in sequence below the excitation mass block 15, and an output end dynamic force sensor or a lower decoupling spring 19 is arranged between the blocking mass block 18 and the base 1.

[0029] The rail fastener and elastic cushion vertical high-frequency dynamic stiffness testing machine is used to measure the vertical high-frequency dynamic stiffness and damping characteristics of the fastener system or elastic cushion under 20-1000Hz dynamic excitation. The test results can provide relatively accurate technical parameters and provide theoretical support and technical guidance for the subsequent design of the fastener system and elastic cushion.

[0030] The dynamic load is applied in the following way: the excitation top rod 11 passes through the through hole on the static load beam 3, the upper flange 12, the upper decoupling spring 13 and the lower flange 14, and then acts on the excitation mass block 15 to ensure the transmission and application of high-frequency dynamic force. The applied static load and vertical high-frequency dynamic load systems are independent of each other, which greatly reduces the mutual interference between dynamic and static loads during loading. The dynamic load system adopts a gantry and a vertical electromagnetic exciter 8 suspension structure to apply an excitation force with a maximum frequency of 2800Hz to the sample 17 under test.

[0031] The dynamic load high-frequency excitation force amplitude ranges from 0 to 40 kN, and the excitation frequency is from 0 to 2800 Hz. In this equipment, the static load system and the vertical high-frequency dynamic load system adopt completely independent structures, which greatly reduces the interference of the dynamic load on the static load during the loading process and can effectively ensure the accuracy of the input force.

[0032] The tooling system in the utility model adopts a mass block and a spring combination structure, in which the sample to be tested 17 is installed. The entire tooling system can be simplified into a single-degree-of-freedom system or a two-degree-of-freedom system vibration model, which can ensure the transmission of static and dynamic forces and ensure that during the test, the entire test equipment has no obvious resonance or the resonance is controllable within the frequency range of 20 to 1000 Hz, so as to meet the accuracy of the test results.

[0033] The control and measurement system in the utility model is used to control the static load and dynamic load applied to the sample 17 under test, and on the other hand, it is also used to collect the preload, dynamic exciting force and vibration response of the sample 17 under test. When the equipment starts the test, the static load system first applies a certain preload and keeps it constant, and then the vertical exciter applies a high-frequency exciting force of a certain frequency and amplitude when passing through the exciting mandrel 11. The whole process is parameter controlled and data collected by the control and measurement system. The dynamic stiffness and damping of the sample 17 under test can be directly calculated by measuring the dynamic force or acceleration response at the output end of the sample, and the acceleration or displacement at the input end of the sample.

[0034] In this embodiment, a U-shaped frame 9 is installed at the bottom of the moving cross beam 7, and the vertical electromagnetic exciter 8 is connected to the U-shaped frame 9 through an air spring 10. The air spring 10 is provided to isolate the vertical electromagnetic exciter 8 from the U-shaped frame 9, so as to prevent high-frequency dynamic excitation during the test from being transmitted to the gantry.

[0035] In this embodiment, in order to further provide a method for installing the air spring 10, an upper pressure plate 28 for pressing the air spring 10 is provided on the outer side of the shell of the vertical electromagnetic exciter 8, and a lower pressure plate 29 for supporting the air spring 10 is provided on the inner side of the U-shaped frame 9. Multiple air springs 10 can be arranged circumferentially around the U-shaped frame 9, and the upper pressure plate 28 presses on the air spring 10 and is supported by the lower pressure plate 29, so that a stable vibration isolation effect can be achieved during high-frequency excitation.

[0036] In this embodiment, the movable cross beam 7 is provided with a guide hole 23 for the oil cylinder 5 to pass through. The guide hole 23 can guide the vertical movement of the movable cross beam 7 on the one hand, and avoid the oil cylinder 5 on the other hand, thereby reducing the longitudinal space occupied by the entire device.

[0037] In this embodiment, the base 1 is provided with a plurality of polished rods 4 penetrating the static load beam 3, and the bottom of the static load beam 3 is provided with a locking device 2 capable of locking on the polished rod 4. The polished rod 4 is provided to play a stable guiding role for the static load beam 3 when it moves vertically, and the locking device 2 is used to lock the static load beam 3 to apply stable static load pressure to the sample 17 to be tested.

[0038] The locking device 2 can be an eccentric lock mounted on the light rod 4. The oil cylinder 5 can drive the static load beam 3 to move along the light rod in the vertical stroke, and then apply a vertical preload of up to 150kN to the sample 17 to be tested. When the target is reached, it remains stable and is fixed in position by the locking device 2, so as to adapt to the height requirements of different samples 17 and tooling during the test. The preload range is 0-150kN, which can be adjusted by the electro-hydraulic servo valve. The static load control mode is force control or displacement control. Through closed-loop feedback, the static load is guaranteed to remain unchanged during the test.

[0039] In this embodiment, when the sample 17 to be tested is a fastener system, a T-type adapter 16 is installed at the bottom of the excitation mass block 15. The T-type adapter 16 plays a guiding role, and the bottom of the T-type adapter 16 contacts the center position of the top of the rail in the fastener system. The bottom of the fastener system is a blocking mass block 18, which is used to assist in measuring the dynamic force at the output end of the sample. When the sample 17 to be tested is an elastic cushion layer, the T-type adapter 16 does not need to be installed in the tooling, and the rest of the tooling installation methods are completely consistent with those when measuring the fastener system. At this time, the elastic cushion layer is directly installed between the excitation mass block 15 and the blocking mass block 18, but the excitation mass block 15 and the blocking mass block 18 need to be redesigned according to the stiffness and geometric dimensions of the elastic cushion layer.

[0040] In this embodiment, when the blocking mass 18 is a lower decoupling spring, the upper end of the lower decoupling spring is connected to the blocking mass 18 through the upper flange 12, and the lower end is connected to the base 1 through the lower flange 14. When the blocking mass 18 is an output end dynamic force sensor, the output end dynamic force sensor is connected to the base 1 through the adapter plate 20.

[0041] In this embodiment, the inner side of the columns 6 on both sides of the vertical gantry is provided with a slide groove 21 for the sliding of the moving cross beam 7, and the slide groove 21 is provided with a lead screw 22 threadedly matched with the moving cross beam 7, and a driving mechanism for driving the lead screws 22 on both sides to rotate synchronously is provided on the static cross beam 27 at the upper end of the vertical gantry. The lead screws 22 on both sides are driven to rotate synchronously by the driving mechanism, and under the threaded match between the lead screw 22 and the static cross beam 27 and the guidance of the slide groove 21, the moving cross beam 7 can move a large amount in the vertical range, so as to drive the exciting top rod 11 to pass through the upper flange 12, the upper decoupling spring 13 and the lower flange 14 in sequence and then act on the excitation mass block 15.

[0042] In this embodiment, in order to further provide a driving mechanism, the driving mechanism includes a dual-axis motor 26 disposed in the middle of the static beam 27, and the output shafts 25 at both ends of the dual-axis motor 26 are transmission-connected to the lead screw 22 through two mutually meshing bevel gears 24. The rotation of the dual-axis motor 26 drives the output shafts 25 at both ends to rotate, drives the bevel gears 24 sleeved on the output shafts 25 to rotate, and then drives the bevel gears 24 sleeved on the upper end of the lead screw 22 to rotate, thereby driving the lead screw 22 to rotate.

[0043] In one embodiment, the main body of the utility model adopts a four-column 6 structure, that is, four polished rods 4 are arranged in a matrix, and two oil cylinders 5 are provided. The two oil cylinders 5 are respectively arranged in the middle position of the two polished rods 4 on both sides.

[0044] In order to ensure that the equipment can effectively measure the dynamic characteristics of the sample 17 under high-frequency and wide-band dynamic excitation, the fixture system needs to adopt two schemes according to the different test excitation frequency ranges, including direct method measurement fixture system and indirect method measurement fixture system. Specifically:

[0045] The direct method measurement fixture system is installed between the static load beam 3 and the base 1. Its effective test frequency range is 20~fmax. The value of fmax is related to the sample to be tested and the fixture design, and can reach up to thousands of hertz. At this time, the dynamic stiffness and damping of the sample to be tested 17 can be calculated by testing the dynamic force and acceleration at the output end of the sample to be tested 17 and the acceleration or displacement at the input end. When the sample to be tested 17 is a fastener system, the fixture is composed of the upper flange 12, the upper decoupling spring 13, the lower flange 14, the excitation mass block 15, the T-type adapter 16, the fastener system, the blocking mass block 18 and the adapter plate 20 from top to bottom. The upper part of the decoupling spring is fixedly mounted on the static load beam 3 through the upper flange 12, and the lower part is mounted on the lower flange 14. The excitation mandrel 11 passes through the upper flange 12, the upper decoupling spring 13 and the lower flange 14 and is connected to the excitation mass block 15. The lower part of the excitation mass block 15 is installed with a T-type adapter 16 to play a guiding role. The bottom of the T-type adapter 16 contacts the center position of the top of the rail in the fastener system. The bottom of the fastener system is a blocking mass block 18, which is used to assist in measuring the dynamic force at the output end of the sample. When the sample 17 to be measured is an elastic cushion layer, the T-type adapter 16 does not need to be installed in the tooling, and the rest of the tooling installation methods are exactly the same as when measuring the fastener system. At this time, the elastic cushion layer is directly installed between the excitation mass block 15 and the blocking mass block 18, but the excitation mass block 15 and the blocking mass block 18 need to be redesigned according to the stiffness and geometric dimensions of the elastic cushion layer.

[0046] The control and measurement system includes a static load electro-hydraulic servo control system, a dynamic load iteration control system and a sensor data acquisition system, which are respectively used for the control of static load and dynamic load during the test, as well as the static preload, dynamic excitation force and vibration response acquisition of each component of the equipment. The vibration response includes displacement and acceleration response in different directions. According to the principle of high-frequency dynamic stiffness and damping test, when the direct method tooling system is used for testing, in order to ensure the test accuracy, the dynamic force sensor is installed at the input and output ends of the sample 17 under test, the input end force sensor is installed between the end of the excitation mandrel 11 and the excitation mass block 15, and the output end sensor is installed between the blocking mass block 18 and the adapter plate 20; the acceleration sensor is symmetrically installed in different directions of the excitation mass block 15, the blocking mass block 18, the base 1 and the vertical gantry static beam 27 and the column 6. The acceleration signals at the input and output ends of the sample 17 under test are represented by the vertical acceleration of the excitation mass block 15 and the vertical acceleration of the blocking mass block 18, respectively.

[0047] Before the test, the design and calculation of the direct method fixture system shall be carried out according to the static stiffness and size of the sample 17 to ensure that the entire test equipment has no obvious resonance or the resonance is controllable within the effective test frequency range. During the test, a certain preload is first applied to the sample 17 to be tested and kept stable, and then a high-frequency excitation force is applied to perform a frequency sweep test, so that the fixture system and the sample 17 to be tested perform vertical reciprocating motion at a certain frequency and amplitude, thereby simulating the stress state of the track fastener system and the elastic cushion layer when subjected to high-frequency wheel-rail excitation. When the output end vibration response is much smaller than the input end response, and the equipment has no obvious resonance or the resonance is controllable during the frequency sweep, the high-frequency dynamic stiffness of the sample 17 to be tested can be calculated by directly measuring the acceleration or displacement signal at the input end of the sample 17 to be tested and the force signal and acceleration signal at the output end. According to the relevant theoretical knowledge of mechanical vibration, the dynamic stiffness is a complex number, and the damping of the sample 17 to be tested can be calculated according to its phase value.

[0048] The indirect method measurement fixture system is installed between the static load beam 3 and the base 1, and its effective test frequency range is f2~1000Hz. At this time, the dynamic stiffness and damping of the sample 17 under test can be calculated by testing the acceleration response of the output and input ends of the sample 17 under test. When the sample 17 under test is a fastener system, the fixture system is from top to bottom: upper decoupling spring 13, excitation mass block 15, T-type transfer table 16, fastener system, blocking mass block 18, and lower decoupling spring. The upper decoupling spring 13 is fixed on the static load beam 3 through the upper flange 12, and the lower part is installed on the lower flange 14. The excitation mandrel 11 passes through the upper decoupling spring 13 and the upper and lower flanges 14 to connect with the excitation mass block 15. The lower part of the excitation mass block 15 is installed with a T-type adapter 16 to guide. The bottom of the T-type adapter 16 and the center position of the top of the rail in the fastener system are in point contact to simulate the stress state of the fastener system when the actual train passes through the rail, and to ensure that the excitation force can be applied vertically to the fastener system. The fastener system is placed on the blocking mass block 18. The blocking mass block 18 has a large mass and is used to avoid resonance of the equipment at high frequencies. The blocking mass block 18 is installed on the base 1 through the lower decoupling spring and its upper and lower flanges 14. When the sample 17 to be tested is an elastic cushion layer, the T-type adapter 16 does not need to be installed in the tooling, and the other tooling installation methods are completely consistent with those when measuring the fastener system. At this time, the elastic cushion layer is directly installed between the excitation mass block 15 and the blocking mass block 18.

[0049] When the indirect method tooling system is used to test the dynamic stiffness within the range of excitation frequency f2 to 1000Hz (f2>100Hz, the specific value is related to the sample to be tested and the tooling design), the control system of static load and dynamic load remains unchanged, but there are differences in sensor acquisition. According to the principle of high-frequency dynamic stiffness and damping test, the equipment uses quartz ICP force chain dynamic force sensor and piezoelectric acceleration sensor to measure the high-frequency excitation force at the input end and the acceleration response at the input and output ends. Under the premise of ensuring the measurement accuracy, the input end dynamic force sensor is installed between the end of the excitation mandrel 11 and the excitation mass block 15 to measure the dynamic force value actually output by the exciter; the acceleration sensor is generally installed symmetrically in different directions of the excitation mass block 15, the blocking mass block 18, the base 1 and the gantry, where the acceleration signals at the input and output ends of the sample to be tested 17 are represented by the vertical acceleration of the excitation mass block 15 and the vertical acceleration of the blocking mass block 18, respectively.

[0050] Similarly, before the test, the indirect method fixture system needs to be designed and calculated according to the static stiffness and size of the sample 17 to ensure that within the effective test frequency range, the entire test equipment has no obvious resonance or the resonance is controllable. During the test, a certain preload is first applied to the sample 17 to be tested and kept stable, and then a high-frequency excitation force is applied to perform a sweep frequency test, so that the fixture system and the sample 17 to be tested perform vertical reciprocating motion at a certain frequency and amplitude, and the acceleration response of the input and output ends of the sample 17 to be tested is measured during the process. At this time, the dynamic stiffness and damping of the sample 17 to be tested can be directly calculated based on the acceleration of the blocking mass block 18 at the output end and the acceleration of the excitation mass block 15 at the input end.

[0051] The preferred embodiments of the present invention are described in detail above in conjunction with the accompanying drawings. However, the present invention is not limited to the specific details in the above embodiments. Within the technical concept of the present invention, the technical solution of the present invention can be subjected to a variety of simple modifications, and these simple modifications all belong to the protection scope of the present invention.

[0052] It should also be noted that the various specific technical features described in the above specific embodiments can be combined in any suitable manner without contradiction. In order to avoid unnecessary repetition, the present utility model will not further describe various possible combinations.

[0053] In addition, various embodiments of the present invention may be arbitrarily combined, and as long as they do not violate the concept of the present invention, they should also be regarded as the contents disclosed by the present invention.

Claims

1. A vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions, characterized in that: The invention comprises a vertical gantry and a moving crossbeam (7) slidably arranged in the vertical gantry, a vertical electromagnetic exciter (8) being installed at the bottom of the moving crossbeam (7), a static load crossbeam (3) and a base (1) being arranged in sequence below the vertical electromagnetic exciter (8), an inverted oil cylinder (5) connected to the base (1) being installed on the static load crossbeam (3), and a vibration ejector rod (11) being installed at the bottom of the vertical electromagnetic exciter (8) being provided on the static load crossbeam (3) for passing through. The bottom of the static load beam (3) is provided with an upper flange (12) coaxial with the excitation top rod (11), an upper decoupling spring (13) and a lower flange (14) in sequence, an excitation mass block (15) is provided at the bottom of the lower flange (14), a measured sample (17) and a blocking mass block (18) are provided below the excitation mass block (15) in sequence, and an output end dynamic force sensor or a lower decoupling spring (19) is provided between the blocking mass block (18) and the base (1).

2. The vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions according to claim 1 is characterized in that: A U-shaped frame (9) is installed at the bottom of the moving crossbeam (7), and the vertical electromagnetic exciter (8) is connected to the U-shaped frame (9) via an air spring (10).

3. The vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions according to claim 2 is characterized in that: An upper pressure plate (28) for pressing the air spring (10) is arranged on the outer side of the shell of the vertical electromagnetic exciter (8), and a lower pressure plate (29) for supporting the air spring (10) is arranged on the inner side of the U-shaped frame (9).

4. The vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions according to claim 1, characterized in that: The movable cross beam (7) is provided with a guide hole (23) through which the oil cylinder (5) passes.

5. The vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions according to claim 1, characterized in that: The base (1) is provided with a plurality of polished rods (4) penetrating the static load beam (3), and the bottom of the static load beam (3) is provided with a locking device (2) capable of locking on the polished rod (4).

6. The vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions according to claim 1, characterized in that: A T-shaped adapter (16) is installed at the bottom of the excitation mass block (15).

7. The vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions according to claim 1, characterized in that: The upper end of the lower decoupling spring is connected to the blocking mass block (18) via an upper flange (12), and the lower end is connected to the base (1) via a lower flange (14).

8. The vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions according to claim 1, characterized in that: The output end dynamic force sensor is connected to the base (1) via an adapter plate (20).

9. The vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions according to claim 1, characterized in that: The inner sides of the columns (6) on both sides of the vertical gantry are provided with sliding grooves (21) for providing the sliding of the movable cross beam (7), and the sliding grooves (21) are provided with screws (22) that are threadedly matched with the movable cross beam (7), and the static cross beam (27) at the upper end of the vertical gantry is provided with a driving mechanism that drives the screws (22) on both sides to rotate synchronously.

10. The vertical high-frequency dynamic stiffness testing machine for rail fasteners and elastic cushions according to claim 9, characterized in that: The driving mechanism comprises a double-axis motor (26) arranged in the middle of the static crossbeam (27), and output shafts (25) at both ends of the double-axis motor (26) are transmission-connected to the lead screw (22) via two mutually meshing bevel gears (24).

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