Sliding rail supporting type vibration isolator testing device and vibration isolator testing method

Abstract

The invention discloses a sliding rail supporting type vibration isolator testing device and a vibration isolator testing method. The testing device comprises a base, a vibration signal source, a sliding rail supporting mechanism, a vibration isolator, a first force sensor, a second force sensor and an eddy current displacement sensor. Wherein the vibration signal source is used for generating vibration to perform vibration isolation test. A balancing weight in the sliding rail supporting mechanism is used for bearing vibration and moving back and forth under the vibration effect. The vibration isolator is connected with the sliding rail supporting mechanism and absorbs kinetic energy in the sliding rail supporting mechanism, and the vibration reduction effect is achieved. Through the sliding block and the balancing weight which slide horizontally, the influence of gravity on the experiment is avoided, the zero-gravity stress environment of the space is simulated, and through the sliding block and the sliding rail, the friction resistance of the sliding block during movement is reduced; by arranging the first force sensor, the second force sensor and the eddy current displacement sensor, the vibration isolation effect of the vibration isolator after vibration can be more accurately detected, and therefore the performance of the vibration isolator with small and micro output can be more accurately detected.

Description

Technical Field

[0001] This invention relates to the field of vibration isolator technology, and in particular to a test device and test method for a slide rail supported vibration isolator. Background Technology

[0002] The rapid development of science and technology and the defense industry has placed higher demands on the agility, precision, and lightweight design of satellites, while also bringing numerous technical challenges. These satellites are extremely sensitive to micro-vibrations caused by onboard equipment; typical vibration sources include reaction wheel assemblies for attitude control and control moment gyroscopes. As a key component for suppressing vibration transmission, the performance of vibration isolators directly affects the operational stability and positioning accuracy of the payload. Therefore, accurately assessing the performance of vibration isolators during the ground phase is of great significance for ensuring the successful implementation of space missions.

[0003] However, the ground testing environment differs significantly from the on-orbit operating conditions, especially in terms of the impact of gravity. How to effectively simulate the micro-vibrations caused by spaceborne equipment such as reaction wheels in a ground-based gravity environment has become the primary issue in evaluating the performance of vibration isolators. To eliminate or compensate for the influence of gravity on testing, research institutions both domestically and internationally have proposed various technical solutions. Currently, most vibration isolator testing devices adopt a horizontal arrangement, mainly including suspended and supported types. However, suspended systems are difficult to level precisely, easily introducing additional eccentric moments and failing to achieve strictly aligned loading; furthermore, suspended structures are susceptible to excitation harmonic interference, leading to distorted test signals. In the horizontal support scheme, if a roller mechanism is used, the friction during the movement of the counterweight is significant. For some low-output vibration isolators, the friction may even exceed the damper's own output, making it impossible to accurately identify its damping characteristics. Furthermore, the rollers are prone to generating noise and vibration, interfering with the dynamic response of the testing system.

[0004] In summary, existing counterweight gravity compensation schemes all have certain limitations and cannot meet the testing requirements of high-precision, low-output vibration isolators. Suspension-type devices are difficult to level and align, and are susceptible to excitation harmonic interference; roller-supported devices have high friction and introduce nonlinear factors. Therefore, there is an urgent need to develop a new testing device that can achieve effective gravity compensation while improving the system's alignment accuracy and anti-interference capability, thereby more realistically simulating the microgravity environment and providing a reliable platform for vibration isolator performance testing. Summary of the Invention

[0005] The present invention aims to at least solve one of the aforementioned technical problems existing in the prior art. To this end, this application proposes a rail-supported vibration isolator testing device, which can test the performance of vibration isolators with small output in a ground gravity environment.

[0006] This application also proposes a test method for vibration isolators based on the above-mentioned slide rail supported vibration isolator test kit.

[0007] According to the first aspect of this application, the slide rail-supported vibration isolator testing device includes: Base; A vibration signal source, which is mounted on the base; A slide rail support mechanism includes a slide rail, a slider, and a counterweight. The slide rail is fixed to the base, and the counterweight is slidably connected to the slide rail via the slider. The output end of the vibration signal source is connected to the counterweight. A vibration isolator includes a coil assembly and a magnetic column. The coil assembly includes a frame structure, a coil, and an elastic element. The frame structure has a channel, the coil is fixed to the inner wall of the channel, and the magnetic column passes through the channel. The magnetic column is connected to the frame structure through the elastic element. One of the frame structure and the magnetic column is connected to a counterweight. The frame structure and the magnetic column move relative to each other due to the vibration of the counterweight. A first force sensor is installed between the vibration signal source and the counterweight; A second force sensor is installed between the vibration isolator and the base; An eddy current displacement sensor is mounted on one side of the vibration isolator.

[0008] The slide rail-supported vibration isolator testing device according to the embodiments of this application has at least the following beneficial effects: by using a horizontally sliding slider and a counterweight, the influence of gravity on the experiment is avoided, simulating the zero-gravity force environment in space; and by setting a slider and a slide rail that slide against each other, the frictional resistance when the slider moves is reduced; by setting a first force sensor, a second force sensor and an eddy current displacement sensor, the vibration isolation effect of the vibration isolator after vibration occurs can be detected more accurately, thereby enabling more accurate detection of the performance of vibration isolators with small output forces.

[0009] According to some embodiments of this application, the counterweight includes a fixed frame and a plurality of counterweights, the fixed frame is mounted on the slider, and each of the counterweights is detachably mounted in the fixed frame.

[0010] According to some embodiments of this application, the number of coil assemblies is at least two, and the magnetic post is inserted into each of the coil assemblies.

[0011] According to some embodiments of this application, the elastic element is a spring sheet, the outer edge of the spring sheet is connected to the frame structure, and a connecting hole for connecting the magnetic post is provided in the middle of the spring sheet.

[0012] According to some embodiments of this application, the slide rail supported vibration isolator testing device further includes a first fixing frame, the first fixing frame being fixed to the base, and the frame structure being connected to one of the magnetic columns to the first fixing frame.

[0013] According to some embodiments of this application, the vibration isolator is connected to the counterweight and the first fixing frame via a connecting rod.

[0014] According to some embodiments of this application, the slide rail supported vibration isolator testing device further includes a second fixing frame, which is fixed to the base, and the eddy current displacement sensor is connected to the second fixing frame.

[0015] According to some embodiments of this application, the coil assembly further includes a metal induction sheet connected to and extending outward from the frame structure, with the eddy current displacement sensor facing the metal induction sheet.

[0016] According to some embodiments of this application, the slide rail supported vibration isolator testing device further includes a limiting rod, which is fixed to the base and closely fits one side of the vibration signal source, the slide rail support mechanism and the vibration isolator to ensure the straightness of the three.

[0017] The vibration isolator testing method according to the second aspect of this application, which is based on the above-described slide rail-supported vibration isolator testing device, includes: Install the counterweight onto the slider, measure the sliding friction between the slider and the slide rail, and ensure that the sliding friction is much smaller than the output force of the vibration isolator; A sinusoidal excitation signal is output to the vibration signal source, the measurement results of the eddy current displacement sensor are monitored in real time, and the amplitude of the excitation signal is adjusted so that the displacement amplitude of the counterweight is controlled within the range of ±1mm. Adjust the output frequency of the vibration signal source and record the measurement data of the first force sensor, the second force sensor, and the eddy current displacement sensor at different frequencies; The input force amplitude is half the difference between the maximum and minimum values ​​of the first force sensor at the current frequency, denoted as F. in (S); The output force amplitude is half the difference between the maximum and minimum values ​​of the second force sensor at the current frequency, denoted as F. out (S); The vibration isolation performance curve of the vibration isolator in the specified frequency band can be obtained based on the following formula: .

[0018] The vibration isolator testing method according to the embodiments of this application has at least the following beneficial effects: by setting the slider and the slide rail to reduce the sliding friction between them, the influence of friction on the experimental process is reduced. Moreover, by analyzing the force sensing data and eddy current sensing data at different frequencies, the vibration isolation performance variation curve of the vibration isolator at different frequencies can be plotted, thereby providing a more accurate and detailed judgment on the vibration isolation performance of the vibration isolator.

[0019] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0020] The accompanying drawings are used to provide a further understanding of the technical solutions disclosed in this application and form part of the specification. They are used together with the embodiments disclosed in this application to explain the technical solutions of this application and do not constitute a limitation on the technical solutions disclosed in this application.

[0021] Figure 1 This is a schematic diagram of the structure of the slide rail supported vibration isolator testing device according to the first aspect of this application; Figure 2 This is a front view of the slide rail supported vibration isolator testing device according to the first aspect of this application; Figure 3 This is a cross-sectional view of the vibration isolator in the slide rail supported vibration isolator testing device according to the first aspect of this application; Figure 4 This is a three-dimensional view of the test device for a slide rail-supported vibration isolator according to the first aspect of this application; Figure 5 This is a top view of the slide rail-supported vibration isolator testing device according to the first aspect of this application.

[0022] Reference numerals: 100-base, 200-vibration signal source, 300-slide rail support mechanism, 310-slide rail, 320-slider, 330-counterweight, 331-fixed frame, 3311-top plate, 3312-bottom plate, 3313-side plate, 332-counterweight, 400-vibration isolator, 410-coil assembly, 411-frame structure, 4111-channel, 412-coil, 413-elastic element, 414-metal sensing sheet, 420-magnetic column, 500-first force sensor, 600-second force sensor, 700-eddy current displacement sensor, 800-first fixed frame, 900-second fixed frame, 1000-limiting rod. Detailed Implementation

[0023] The embodiments of this application are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this application, and should not be construed as limiting this application.

[0024] In the description of this application, it should be understood that the orientation descriptions, such as up, down, front, back, left, right, etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.

[0025] In the description of this application, "several" means one or more, "multiple" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. The use of "first" and "second" in the description is merely for distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0026] In the description of this application, unless otherwise expressly defined, terms such as "setup," "installation," and "connection" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this application in conjunction with the specific content of the technical solution.

[0027] In the description of this application, the terms "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0028] The rapid development of science and technology and the defense industry has placed higher demands on the agility, precision, and lightweight design of satellites, while also bringing numerous technical challenges. These satellites are extremely sensitive to micro-vibrations caused by onboard equipment; typical vibration sources include reaction wheel assemblies for attitude control and control moment gyroscopes. As a key component for suppressing vibration transmission, the performance of vibration isolators directly affects the operational stability and positioning accuracy of the payload. Therefore, accurately assessing the performance of vibration isolators during the ground phase is of great significance for ensuring the successful implementation of space missions.

[0029] However, the ground testing environment differs significantly from the on-orbit operating conditions, especially in terms of the impact of gravity. How to effectively simulate the micro-vibrations caused by spaceborne equipment such as reaction wheels in a ground-based gravity environment has become the primary issue in evaluating the performance of vibration isolators. To eliminate or compensate for the influence of gravity on testing, research institutions both domestically and internationally have proposed various technical solutions. Currently, most vibration isolator testing devices adopt a horizontal arrangement, mainly including suspended and supported types. However, suspended systems are difficult to level precisely, easily introducing additional eccentric moments and failing to achieve strictly aligned loading; furthermore, suspended structures are susceptible to excitation harmonic interference, leading to distorted test signals. In the horizontal support scheme, if a roller mechanism is used, the friction during the movement of the counterweight is significant. For some low-output vibration isolators, the friction may even exceed the damper's own output, making it impossible to accurately identify its damping characteristics. Furthermore, the rollers are prone to generating noise and vibration, interfering with the dynamic response of the testing system.

[0030] In summary, existing counterweight gravity compensation schemes all have certain limitations and cannot meet the testing requirements of high-precision, low-output vibration isolators. Suspension-type devices are difficult to level and align, and are susceptible to excitation harmonic interference; roller-supported devices have high friction and introduce nonlinear factors. Therefore, there is an urgent need to develop a new testing device that can achieve effective gravity compensation while improving the system's alignment accuracy and anti-interference capability, thereby more realistically simulating the microgravity environment and providing a reliable platform for vibration isolator performance testing.

[0031] In response, this application proposes a sliding rail-supported vibration isolator testing device. By using a horizontally sliding slider and counterweight, the influence of gravity on the experiment is avoided, simulating the zero-gravity force environment of space. Furthermore, by setting up mutually sliding sliders and rails, the frictional resistance during slider movement is reduced. By setting up a first force sensor, a second force sensor, and an eddy current displacement sensor, the vibration isolation effect of the vibration isolator after vibration occurs can be detected more accurately, thereby enabling more precise detection of the performance of vibration isolators with small output forces.

[0032] Furthermore, this application proposes a vibration isolator testing method based on the aforementioned slide rail-supported vibration isolator testing device. By setting the slider and slide rail to reduce the sliding friction between them, the influence of friction on the experimental process is reduced. Moreover, by analyzing force sensing data and eddy current sensing data at different frequencies, the vibration isolation performance variation curves of the vibration isolator at different frequencies can be plotted, thereby providing a more accurate and detailed assessment of the vibration isolation performance of the vibration isolator.

[0033] Reference Figure 1 and Figure 2The slide rail-supported vibration isolator testing device in the first aspect embodiment of this application includes a base 100, a vibration signal source 200, a slide rail support mechanism 300, a vibration isolator 400, a first force sensor 500, a second force sensor 600, and an eddy current displacement sensor 700. The base 100 provides support for the other components of the slide rail-supported vibration isolator testing device, and each component is fixed to the base 100 to define its position. The vibration signal source 200 generates vibration for vibration isolation testing. The counterweight 330 in the slide rail support mechanism 300 bears the vibration and moves back and forth under the vibration. The vibration isolator 400 is connected to the slide rail support mechanism 300 and absorbs the kinetic energy therein, thus reducing vibration. The first force sensor 500 detects the initiation force of the vibration signal source 200, and the second force sensor 600 detects the output force of the vibration isolator 400 after vibration isolation. By comparing the detection data of the first force sensor 500 and the second force sensor 600, the vibration isolation effect of the vibration isolator 400 can be analyzed. The eddy current displacement sensor 700 can detect the vibration of the vibration isolator 400 more accurately through the eddy current effect, thereby improving the detection accuracy.

[0034] Specifically, the vibration signal source 200 is mounted on the base 100 and can output periodic or non-periodic vibrations to meet the requirements of different experiments for the vibration source. The slide rail support mechanism 300 includes a slide rail 310, a slider 320, and a counterweight 330. The slide rail 310 is fixed to the base 100, and the counterweight 330 is slidably connected to the slide rail 310 through the slider 320. The output end of the vibration signal source 200 is connected to the counterweight 330, so that the counterweight 330 can slide through the slider 320 under the drive of the vibration signal source 200.

[0035] Reference Figure 3 The vibration isolator 400 includes a coil assembly 410 and a magnetic column 420. The coil assembly 410 includes a frame structure 411, a coil 412, and an elastic element 413. The frame structure 411 has a channel 4111. The coil 412 is fixed to the inner wall of the channel 4111. The magnetic column 420 passes through the channel 4111 and is movable along the central axis of the channel 4111. The magnetic column 420 is connected to the frame structure 411 via the elastic element 413. The elastic element 413 limits the displacement distance of the magnetic column 420 and allows it to oscillate back and forth within the channel 4111. One of the frame structure 411 and the magnetic column 420 is connected to a counterweight 330. When the counterweight 330 vibrates, the frame structure 411 and the magnetic column 420 move relative to each other.

[0036] Therefore, when the counterweight 330 vibrates under the excitation of the vibration signal source 200, the kinetic energy of the vibration is transferred to the vibration isolator 400, and the magnetic column 420 oscillates back and forth in the channel 4111. In this process, on the one hand, the elastic element 413 converts part of the kinetic energy of the vibration into elastic potential energy; on the other hand, the magnetic column 420 and the coil 412 move to cut the magnetic field lines, and an induced current is generated in the coil 412, generating a reverse Ampere force, which in turn absorbs the vibration energy.

[0037] A first force sensor 500 is installed between the vibration signal source 200 and the counterweight 330, and it is used to detect the output force of the vibration signal source 200. A second force sensor 600 is installed between the vibration isolator 400 and the base 100, and it is used to detect the output force of the vibration isolator 400 after vibration isolation. By comparing the detection results of the first force sensor 500 and the second force sensor 600, the vibration isolation effect of the vibration isolator 400 can be analyzed.

[0038] An eddy current displacement sensor 700 is installed on one side of the vibration isolator 400, which can detect the movement distance of the frame structure 411 through the eddy current effect.

[0039] Furthermore, the counterweight 330 includes a fixed frame 331 and multiple counterweights 332. The fixed frame 331 is mounted on the slider 320, and each counterweight 332 is detachably mounted in the fixed frame 331. By changing the number of counterweights 332 installed, the mass of the entire counterweight 330 can be changed, thereby changing the inertia of the counterweight 330 after it vibrates under force.

[0040] Furthermore, referring to Figure 4 The fixed frame 331 includes a top plate 3311, a bottom plate 3312, and two side plates 3313. Both ends of the bottom plate 3312 are connected to the two side plates 3313, and both ends of the top plate 3311 are also connected to the two side plates 3313. Thus, the top plate 3311, bottom plate 3312, and two side plates 3313 together form a frame structure. The bottom plate 3312 is fixedly connected to the slider 320, allowing the entire fixed frame 331 to move together with the slider 320.

[0041] As for the connection method between the counterweight 332 and the fixed frame 331, a detachable connection method such as bolt connection, pin connection or snap-fit ​​connection can be used, which will not be elaborated here.

[0042] Optionally, the number of coil assemblies 410 can be set to at least two, with magnetic posts 420 inserted into each coil assembly 410, thereby increasing the number of coil assemblies 410 to improve the vibration isolation and buffering effect.

[0043] Furthermore, the elastic element 413 can be a columnar spring, a rubber elastic layer, or a spring sheet. In this embodiment, the elastic element 413 is specifically a spring sheet, the outer edge of which is connected to the frame structure 411, and a connecting hole for connecting the magnetic post 420 is provided in the middle of the spring sheet. When either the frame structure 411 or the magnetic post 420 is subjected to an external force and moves in a certain direction, the spring sheet deforms, and the magnetic post 420 moves along the channel 4111 following the middle of the spring sheet; when the frame structure 411 returns to its original position, the spring sheet applies a reverse elastic force to the magnetic post 420, thereby forcing the magnetic post 420 to return to its initial position. The purpose of using a spring sheet is to ensure that the magnetic post 420 is subjected to a uniform elastic force and to confine the magnetic post 420 in the middle, preventing the magnetic post 420 from bumping into the channel 4111 when it oscillates back and forth.

[0044] It is easy to understand that the number of spring sheets can be set to multiple and arranged along the direction of channel 4111. By increasing or decreasing the number of spring sheets, the vibration isolation effect can be changed, thereby verifying the influence of different vibration isolation structures on the vibration isolation effect.

[0045] Furthermore, the slide rail supported vibration isolator testing device also includes a first fixed frame 800, which is fixed to the base 100. One of the frame structure 411 and the magnetic column 420 is connected to the first fixed frame 800, and the first fixed frame 800 bears the force from the vibration isolator 400.

[0046] Furthermore, the vibration isolator 400 is connected to the counterweight 330 and the first fixed frame 800 via a connecting rod. The connecting rod serves as a connecting component, enabling the interconnection of components and transmitting the force generated by vibration.

[0047] Furthermore, the slide rail supported vibration isolator testing device also includes a second fixed frame 900, which is fixed to the base 100. The eddy current displacement sensor 700 is connected to the second fixed frame 900, so that the eddy current displacement sensor 700 is fixed to the base 100 through the second fixed frame 900 and is set on one side of the vibration isolator 400.

[0048] Furthermore, the coil assembly 410 also includes a metal induction plate 414, which is connected to the frame structure 411 and extends outward, with the eddy current displacement sensor 700 facing the metal induction plate 414. When the frame structure 411 moves under the action of an external force, the eddy current displacement sensor 700 can detect the displacement change of the metal induction plate 414, thereby obtaining the position information of the frame structure 411.

[0049] Furthermore, referring to Figure 5The slide rail supported vibration isolator testing device also includes a limiting rod 1000, which is fixed to the base 100. The limiting rod 1000 is closely attached to one side of the vibration signal source 200, the slide rail support mechanism 300 and the vibration isolator 400 to ensure the straightness of the three and to ensure that the output force direction of the vibration signal source 200 is parallel to the length direction of the limiting rod 1000.

[0050] A vibration isolator testing method according to a second aspect embodiment of this application, which is based on the above-mentioned slide rail supported vibration isolator testing device, includes the following steps: S100. Install the counterweight 330 onto the slider 320, measure the sliding friction between the slider 320 and the slide rail 310, and ensure that the sliding friction is much smaller than the output force of the vibration isolator 400. S200. Output a sinusoidal excitation signal to the vibration signal source 200, monitor the measurement results of the eddy current displacement sensor 700 in real time, and adjust the amplitude of the excitation signal so that the displacement amplitude of the counterweight 330 is controlled within the range of ±1mm. S300. Adjust the output frequency of the vibration signal source 200 and record the measurement data of the first force sensor 500, the second force sensor 600, and the eddy current displacement sensor 700 at different frequencies; S400. The input force amplitude is half the difference between the maximum and minimum values ​​of the first force sensor 500 at the current frequency, denoted as F. in (S); The second force sensor 600 outputs a force amplitude of half the difference between its maximum and minimum values ​​at the current frequency, denoted as F. out (S); The vibration isolation performance curve of the vibration isolator 400 in a specified frequency band can be obtained based on the following formula: .

[0051] The embodiments of this application have been described in detail above with reference to the accompanying drawings. However, this application is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of this application. Furthermore, unless otherwise specified, the embodiments and features described in the embodiments of this application can be combined with each other.

Claims

1. A test device for a slide rail-supported vibration isolator, characterized in that, include: Base; A vibration signal source, which is mounted on the base; A slide rail support mechanism includes a slide rail, a slider, and a counterweight. The slide rail is fixed to the base, and the counterweight is slidably connected to the slide rail via the slider. The output end of the vibration signal source is connected to the counterweight. A vibration isolator includes a coil assembly and a magnetic column. The coil assembly includes a frame structure, a coil, and an elastic element. The frame structure has a channel, the coil is fixed to the inner wall of the channel, and the magnetic column passes through the channel. The magnetic column is connected to the frame structure through the elastic element. One of the frame structure and the magnetic column is connected to a counterweight. The frame structure and the magnetic column move relative to each other due to the vibration of the counterweight. A first force sensor is installed between the vibration signal source and the counterweight; A second force sensor is installed between the vibration isolator and the base; An eddy current displacement sensor is mounted on one side of the vibration isolator.

2. The test device for a slide rail-supported vibration isolator according to claim 1, characterized in that: The counterweight includes a fixed frame and multiple counterweights. The fixed frame is mounted on the slider, and each of the counterweights can be detachably mounted inside the fixed frame.

3. The test device for a slide rail-supported vibration isolator according to claim 1, characterized in that: The number of coil assemblies is at least two, and the magnetic post is inserted into each of the coil assemblies.

4. The test device for a slide rail-supported vibration isolator according to claim 1, characterized in that: The elastic element is a spring sheet, the outer edge of which is connected to the frame structure, and a connecting hole for connecting the magnetic post is provided in the middle of the spring sheet.

5. The test device for a slide rail-supported vibration isolator according to claim 1, characterized in that: The slide rail supported vibration isolator testing device also includes a first fixing frame, which is fixed to the base, and the frame structure and one of the magnetic columns are connected to the first fixing frame.

6. The test device for a slide rail-supported vibration isolator according to claim 5, characterized in that: The vibration isolator is connected to the counterweight and the first fixing frame via a connecting rod.

7. The test device for a slide rail-supported vibration isolator according to claim 1, characterized in that: The slide rail supported vibration isolator testing device also includes a second fixed frame, which is fixed to the base, and the eddy current displacement sensor is connected to the second fixed frame.

8. The test device for a slide rail-supported vibration isolator according to claim 1, characterized in that: The coil assembly also includes a metal induction plate, which is connected to the frame structure and extends outward, with the eddy current displacement sensor facing the metal induction plate.

9. The test device for a slide rail-supported vibration isolator according to claim 1, characterized in that: The slide rail supported vibration isolator testing device also includes a limiting rod, which is fixed to the base and fits tightly against one side of the vibration signal source, the slide rail support mechanism and the vibration isolator to ensure the straightness of the three.

10. A method for testing vibration isolators, based on the slide rail-supported vibration isolator testing device according to any one of claims 1 to 9, characterized in that, include: Install the counterweight onto the slider, measure the sliding friction between the slider and the slide rail, and ensure that the sliding friction is much smaller than the output force of the vibration isolator; A sinusoidal excitation signal is output to the vibration signal source, the measurement results of the eddy current displacement sensor are monitored in real time, and the amplitude of the excitation signal is adjusted so that the displacement amplitude of the counterweight is controlled within the range of ±1mm. Adjust the output frequency of the vibration signal source and record the measurement data of the first force sensor, the second force sensor, and the eddy current displacement sensor at different frequencies; The input force amplitude is half the difference between the maximum and minimum values ​​of the first force sensor at the current frequency, denoted as F. in (S); The output force amplitude is half the difference between the maximum and minimum values ​​of the second force sensor at the current frequency, denoted as F. out (S); The vibration isolation performance curve of the vibration isolator in the specified frequency band can be obtained based on the following formula: 。

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