A vibration control device and control method for a large-scale wind tunnel model

Abstract

The present invention discloses a vibration control device and a control method for a large-scale wind tunnel model, belonging to the technical field of aerospace wind tunnel tests, and solving the problem that the existing methods have unsatisfactory vibration suppression effects on large-scale wind tunnel test models; it includes a fixed bottom plate and a fixed top plate; both ends of the fixed bottom plate and the fixed top plate are connected by support and guiding components, a mass block group is arranged between the two support and guiding components, and damping adjustment components are arranged on both sides of the mass block group and are installed on both sides of the fixed bottom plate and act on the mass block group; the present invention places the vibration control device inside the test model, and forms a tuning system through the mass block group, the support and guiding components, and the damping adjustment components, so that the vibration control device can provide a significant vibration suppression effect within the main frequency band of the structural vibration of the test model, thereby improving the reliability and accuracy of the wind tunnel test.

Description

Technical Field

[0001] The present invention relates to the technical field of aerospace wind tunnel testing, and particularly to a vibration control device and method for a large-scale wind tunnel model. Background Art

[0002] Wind tunnel testing is an important means to obtain the aerodynamic characteristics and flow characteristics of aircraft in the aerospace field. With the gradual development of aircraft design towards large-scale and high-maneuverability, in order to simulate the real flight environment under ground conditions, the requirements for the size of the wind tunnel test model and the simulation accuracy of the test environment are also continuously increasing.

[0003] When the model size increases or high-angle-of-attack tests such as large angles of attack are carried out, the model is prone to large-amplitude vibrations under the action of aerodynamic loads. Especially when the structural mode is near the unstable boundary, the vibrations will be further amplified, resulting in distorted or difficult-to-measure measurement data, thereby affecting the reliability and accuracy of wind tunnel tests. In the prior art, methods such as increasing the model stiffness, adjusting the test parameters, or using external supports are usually adopted to reduce vibrations. However, these methods either increase the difficulty of model design and manufacturing or interfere with the test itself, and it is difficult to achieve effective vibration suppression without affecting the aerodynamic test conditions. In recent years, active control technology has developed rapidly, using piezoelectric ceramics, etc. as actuators for vibration control to cancel the vibrations of the model. However, for large-scale wind tunnel models, it is difficult to achieve high-power input for this type of active control, and the actual vibration suppression effect is not ideal.

[0004] Therefore, how to reduce the vibration influence of large-scale models through an in-built vibration suppression device without changing the original wind tunnel test layout has become an urgent problem to be solved in wind tunnel tests. Summary of the Invention

[0005] In view of the above problems in the prior art, the present invention provides a vibration control device and method for a large-scale wind tunnel model, which solves the problem that the existing methods have an unsatisfactory vibration suppression effect on large-scale wind tunnel test models.

[0006] To achieve the above object, the technical solution adopted by the present invention is as follows:

[0007] On the one hand, a vibration control device for a large-scale wind tunnel model is provided, which includes a fixed bottom plate and a fixed top plate; both ends of the fixed bottom plate and the fixed top plate are connected by support and guiding components, a mass block group is arranged between the two support and guiding components, and damping adjustment components are arranged on both sides of the mass block group and act on the mass block group and are installed on both sides of the fixed bottom plate.

[0008] The present invention incorporates a vibration control device inside the test model. A tuning system is formed by a mass block group, a support and guiding assembly, and a damping adjustment assembly, enabling the vibration control device to provide a significant vibration suppression effect within the main frequency band of the structural vibration of the test model, thereby improving the reliability and accuracy of the wind tunnel test.

[0009] Further, the support and guiding assembly includes two optical axis mounting seats respectively installed on the fixed bottom plate and the fixed top plate. An optical axis is arranged between the two optical axis mounting seats; a linear bearing is sleeved on the middle of the optical axis, and spring assemblies are sleeved on the optical axis at both ends of the linear bearing.

[0010] Further, the spring assembly includes a compression spring and a spring seat located at the end of the compression spring. The compression spring and the spring seat are sleeved on the optical axis; a rubber gasket is arranged on the collision surface of the spring seat.

[0011] Further, the mass block group includes a plurality of mass blocks and a support cross beam passing through the middle of the plurality of mass blocks; the end of the support cross beam is sleeved on the linear bearing and connected to the linear bearing.

[0012] Further, the damping adjustment assembly includes a magnet mounting assembly arranged in the middle of the mass block group and damping mounting assemblies arranged on both sides of the middle of the fixed bottom plate; the magnet mounting assembly includes a magnet mounting plate group located in the middle of the mass block group and sleeved on the support cross beam.

[0013] The magnet mounting plate group includes two oppositely arranged magnet mounting plates; a through hole matching the support cross beam is opened in the middle of the magnet mounting plate, and two mounting ears are arranged at both ends of the magnet mounting plate, and a permanent magnet is arranged on each mounting ear.

[0014] Further, the damping mounting assembly includes a fixed connecting ear in the middle of the fixed bottom plate. An adjusting plate is movably mounted on the fixed connecting ear, and a conductive metal plate is arranged at the top end of the adjusting plate.

[0015] Further, a strip hole is opened on the fixed connecting ear, and a threaded hole is opened at the bottom of the adjusting plate. The fixed connecting ear and the adjusting plate are connected by inserting a bolt through the strip hole into the threaded hole.

[0016] On the other hand, a control method using a vibration control device for a large - size wind tunnel model is provided, which includes the following steps:

[0017] Step S1, according to the requirements of the wind tunnel test and the size of the test model, obtain the modal frequency range of the test model; determine the stiffness of the compression spring, the weight of the mass block, and the initial gap between the permanent magnet and the conductive metal plate according to the modal frequency range.

[0018] Step S2: Install the vibration control device in the reserved cavity inside the top of the test model. Meanwhile, connect the test model to the scimitar mechanism through the model support rod.

[0019] Step S3: Conduct a wind tunnel test.

[0020] Step S4: After the wind tunnel test is completed, verify and evaluate the vibration suppression effect. If the vibration suppression effect does not meet the expected effect, perform damping and frequency adjustment. After adjustment, repeat Step S3 and Step S4 until the expected vibration suppression effect is achieved, and then the test is completed.

[0021] Furthermore, the method of damping and frequency adjustment in Step S4 is as follows: If the vibration suppression effect is insufficient, the installation position of the adjustment plate on the fixed connection ear can be adjusted to adjust the gap between the permanent magnet and the conductive metal plate, so as to increase or decrease the eddy current damping.

[0022] If there is a deviation in the vibration frequency, different stiffness compression springs can be replaced to change the system stiffness, or the number of mass blocks can be increased or decreased to change the weight of the mass block group, so as to achieve the adjustment of the tuned frequency.

[0023] The present invention discloses a vibration control device and a control method for a large-size wind tunnel model, and its beneficial effects are as follows:

[0024] The present invention places the vibration control device inside the test model, and forms a tuned system through the mass block group, the support and guiding component, and the damping adjustment component, so that the vibration control device can provide a significant vibration suppression effect within the main frequency band of the structural vibration of the test model, thereby improving the reliability and accuracy of the wind tunnel test. Description of the Drawings

[0025] Figure 1 It is a structural schematic diagram of a vibration control device for a large-size wind tunnel model of the present invention.

[0026] Figure 2 It is a sectional structural schematic diagram of a vibration control device for a large-size wind tunnel model of the present invention.

[0027] Figure 3 It is a partial structural schematic diagram of a vibration control device for a large-size wind tunnel model of the present invention.

[0028] Figure 4 It is a structural schematic diagram of the magnet mounting plate of the present invention.

[0029] Figure 5 It is an installation structural schematic diagram of the vibration control device of the present invention.

[0030] Among them, 1. Fixed bottom plate; 2. Fixed top plate; 3. Support and guiding assembly; 31. Optical axis mounting seat; 32. Optical axis; 33. Linear bearing; 34. Compression spring; 35. Spring seat; 36. Rubber gasket; 4. Mass block group; 41. Mass block; 42. Support cross beam; 5. Damping adjustment assembly; 51. Magnet mounting plate; 52. Through hole; 53. Mounting ear; 54. Permanent magnet; 55. Fixed connection ear; 56. Adjusting plate; 57. Conductive metal plate; 58. Slot hole; 59. Threaded hole; 6. Test model; 7. Reserved cavity; 8. Model support rod; 9. Scimitar mechanism. Detailed implementation manners

[0031] The detailed implementation manners of the present invention will be described to facilitate those skilled in the art of the present technology to understand the present invention. However, it should be clear that the present invention is not limited to the scope of the detailed implementation manners. For those of ordinary skill in the art of the present technology, as long as various changes are within the spirit and scope of the present invention defined and determined by the appended claims, these changes are obvious, and all inventions created using the concept of the present invention are within the scope of protection.

[0032] Embodiment 1

[0033] Reference Figures 1 - 5 , this embodiment provides a vibration control device for a large-scale wind tunnel model, and its purpose is to solve the problem that the existing method has an unsatisfactory vibration suppression effect on the large-scale wind tunnel test model. The specific structure in this embodiment will be elaborated in detail below.

[0034] A vibration control device for a large-scale wind tunnel model, which includes a fixed bottom plate 1 and a fixed top plate 2;

[0035] Among them, both ends of the fixed bottom plate 1 and the fixed top plate 2 are connected by support and guiding assemblies 3. A mass block group 4 is arranged between the two support and guiding assemblies 3, and damping adjustment assemblies 5 are arranged on both sides of the mass block group 4 and are installed on both sides of the fixed bottom plate 1 and act on the mass block group 4.

[0036] In this embodiment, this device is placed inside the test model 6. The support and guiding assembly provides guidance and support for the mass block group 4, so that the mass block group 4 matches or is close to the main vibration frequency of the test model 6 in the wind tunnel test. When the test model 6 is vibrated by aerodynamic excitation, the mass block group 4 will have relative movement with the model main body, forming anti-phase vibration, thereby weakening the vibration amplitude of the test model 6 main body, and further enabling this device to provide a significant vibration suppression effect within the main frequency band where the test model 6 has structural vibration, thereby improving the reliability and accuracy of the wind tunnel test.

[0037] Specifically, the support and guide assembly 3 includes two optical axis mounting seats 31 respectively mounted on the fixed bottom plate 1 and the fixed top plate 2, and an optical axis 32 is arranged between the two optical axis mounting seats 31; a linear bearing 33 is sleeved in the middle of the optical axis 32, and spring assemblies are sleeved on the optical axis 32 at both ends of the linear bearing 33.

[0038] Specifically, the spring assembly includes a compression spring 34 and a spring seat 35 located at the end of the compression spring 34 . The compression spring 34 and the spring seat 35 are sleeved on the optical axis 32 . A rubber gasket 36 is provided on the collision surface of the spring seat 35 .

[0039] In this embodiment, two optical axis mounting seats 31 are respectively mounted on the fixed bottom plate 1 and the fixed top plate 2 by bolts, and an optical axis 32 is arranged between the two optical axis mounting seats 31 to connect the fixed bottom plate 1 and the fixed top plate 2.

[0040] A linear bearing 33 is sleeved on the optical axis 32, and the mass block group 4 is installed between the two linear bearings 33, so that the optical axis 32 and the linear bearings 33 can maintain linear guidance for the mass block group 4 in the vibration direction, reduce deviation or shaking, ensure its smooth movement and reduce friction. At the same time, the compression spring 34 provides elastic support for the mass block group 4, so that the mass block group 4 can vibrate relative to the main body of the test model 6 within a certain degree of freedom.

[0041] A rubber gasket 36 is provided on the collision surface of the spring seat 35 to reduce noise, absorb unnecessary high-frequency vibration, and protect the surface of the component, thereby further reducing noise and energy loss.

[0042] Specifically, the mass block group 4 includes a plurality of mass blocks 41 and a support beam 42 passing through the middle of the plurality of mass blocks 41 ; an end of the support beam 42 is sleeved on the linear bearing 33 and connected to the linear bearing 33 .

[0043] In this embodiment, the mass block group 4 includes a plurality of mass blocks 41 . The mass blocks 41 are made of high-density materials, such as tungsten, etc., so as to obtain a larger mass in a limited space.

[0044] Optionally, limit buckles are provided on the support beams 42 at both ends of the mass block 41 , and the mass block 41 can be fixed on the support beam 42 by the limit buckles to prevent the mass block 41 from shifting.

[0045] Specifically, the damping adjustment assembly 5 includes a magnet mounting assembly disposed in the middle of the mass block group 4 and damping mounting assemblies disposed on both sides of the middle of the fixed base plate 1; the magnet mounting assembly includes a magnet mounting plate group located in the middle of the mass block group 4 and sleeved on the support cross beam 42; the magnet mounting plate group includes two oppositely disposed magnet mounting plates 51; a through hole 52 that fits the support cross beam 42 is provided in the middle of the magnet mounting plate 51, and two mounting ears 53 are provided at both ends of the magnet mounting plate 51, and a permanent magnet 54 is provided on each mounting ear 53.

[0046] Specifically, the damping mounting assembly includes a fixed connection ear 55 in the middle of the fixed base plate 1, an adjusting plate 56 is movably mounted on the fixed connection ear 55, and a conductive metal plate 57 is provided at the top of the adjusting plate 56.

[0047] Specifically, a strip-shaped hole 58 is provided on the fixed connection ear 55, a threaded hole 59 is provided at the bottom of the adjusting plate 56, and the fixed connection ear 55 and the adjusting plate 56 are connected by a bolt passing through the strip-shaped hole 58 and inserted into the threaded hole 59.

[0048] In this embodiment, the permanent magnet 54 can be selected from high-performance rare earth magnets such as N52, and the material of the conductive metal plate 57 can be selected from aluminum or copper. A certain gap is maintained between the conductive metal plate 57 and the permanent magnet 54, and eddy current damping is generated during the relative movement in the direction of cutting the magnetic induction line of the permanent magnet 54.

[0049] The two magnet mounting plates 51 are arranged oppositely. The two magnet mounting plates 51 are disposed in the middle of the mass block group 4 by passing the support cross beam 42 through the through hole 52. Mounting ears 53 are provided at both ends of the magnet mounting plate 51, and a plurality of threaded holes are evenly provided in the mounting ears 53. Through holes that fit the threaded holes are provided in the permanent magnet 54. Thus, the permanent magnet 54 is mounted on the magnet mounting plate 51 through a bolt passing through the through hole and inserted into the threaded hole, and then mounted on both sides of the mass block group 4.

[0050] Fixed connection ears 55 are provided on both sides of the middle of the fixed base plate 1. A strip-shaped hole 58 is provided on the fixed connection ear 55, a threaded hole 59 is provided at the bottom of the adjusting plate 56, and the fixed connection ear 55 and the adjusting plate 56 are connected by a bolt passing through the strip-shaped hole 58 and inserted into the threaded hole 59. The strip-shaped hole 58 can adjust the mounting position of the adjusting plate 56, thereby adjusting the distance between the conductive metal plate 57 and the permanent magnet 54.

[0051] During the operation of the present device, the mass block group 4 moves up and down or horizontally reciprocally along with the vibration, driving the permanent magnet 54 and the conductive metal plate 57 to move relatively. Since there is a magnetic field between the permanent magnet 54 and the conductive metal plate 57, when the permanent magnet 54 moves relative to the conductive metal plate 57, eddy currents will be induced in the conductive metal plate 57. The eddy currents interact with the magnetic field to generate a damping force. It itself constitutes a second-order system, which is composed of the mass block group 4, the compression spring 34 and the magnetic-eddy current damping assembly, and can be described by the following second-order differential equation:

[0052]

[0053] Among them, m, c, and k represent the mass, damping, and stiffness parameters respectively, x represents the displacement of the mass block, F represents the external force received by the mass block, and t represents time. By reasonably designing these parameters, the natural frequency of the second-order system is made to match the vibration frequency of the main structure or a suitable phase difference is generated, thereby introducing additional natural damping and stiffness.

[0054] Specifically, the addition of the second-order system has the following effect of improving stability:

[0055] In the vibration transfer function, after adding a finely tuned second-order system, the system poles (i.e., the roots of the response function) will gradually move from the imaginary axis or the right half-plane to the left half-plane. This means that the natural damping of the system is increased, and the vibration energy can be dissipated more quickly, thereby effectively suppressing and attenuating vibrations and avoiding the continuous existence of the unstable state.

[0056] Since the parameters of the second-order system (mass, stiffness, damping coefficient) are adjustable, by adjusting these parameters, the device can maintain the best vibration suppression state under different test conditions. This tuning ability enables the system to quickly adapt to different working conditions and stabilize the system dynamic response, preventing the vibration out-of-control phenomenon caused by unstable modes.

[0057] Embodiment 2

[0058] Reference Figures 1 - 5 , this embodiment provides a vibration control device for a large-scale wind tunnel model, and its purpose is to solve the problem that the existing method has an unsatisfactory vibration suppression effect on the large-scale wind tunnel test model. The specific structure in this embodiment will be elaborated in detail below.

[0059] A control method using the vibration control device for a large-scale wind tunnel model is provided, which includes the following steps:

[0060] Step S1, according to the requirements of the wind tunnel test and the size of the test model 6, obtain the modal frequency range of the test model 6; determine the stiffness of the compression spring 34, the weight of the mass block 41, and the initial gap between the permanent magnet 54 and the conductive metal plate 57 according to the modal frequency range.

[0061] In this embodiment, according to the requirements of the wind tunnel test and the size of the test model 6, the main modal frequency range of the test model 6 is calculated or measured to obtain the modal frequency range of the test model 6; based on the modal frequency range, the stiffness of the compression spring 34 and the weight of the mass block 41, as well as the initial gap between the permanent magnet 54 and the conductive metal plate 57 are determined, so as to select the compression spring 34 with appropriate stiffness and the number of mass blocks 41 in the mass block group 4, making the natural vibration frequency of this close to or slightly lower than the main vibration frequency of the test model 6, and determining the initial gap between the permanent magnet 54 and the conductive metal plate 57 to ensure the required eddy current damping magnitude.

[0062] Step S2: Install the vibration control device in the reserved cavity 7 inside the top of the test model 6. At the same time, the test model 6 is connected to the scimitar mechanism 9 through the model support rod 8.

[0063] In this embodiment, the vibration suppression device is built inside the large-size wind tunnel test model 6, and the test model 6 is connected to the scimitar mechanism 9 through the model support rod 8. A reserved cavity 7 is provided inside the top of the test model 6 for installing the vibration suppression device of the present invention. Refer to Figure 3 , only the general layout of the present invention in the wind tunnel test environment is shown; in specific implementation, the device position and installation method can be appropriately adjusted according to the structural characteristics and experimental requirements of different models.

[0064] After the vibration suppression device is arranged in the reserved cavity 7, check whether each connection part is firm and whether the movement is smooth to ensure that the mass block group 4 can move smoothly on the optical axis 32.

[0065] Step S3: Conduct a wind tunnel test; in the wind tunnel test, monitor the vibration response and aerodynamic force data of the test model 6 through force sensors, acceleration sensors, etc.

[0066] Step S4: After the wind tunnel test is completed, verify and evaluate the vibration suppression effect. If the vibration suppression effect does not reach the expected effect, perform damping and frequency adjustment, and repeat Step S3 and Step S4 after adjustment until the expected vibration suppression effect is achieved, and the test is completed.

[0067] After the wind tunnel test is completed, compare the vibration amplitude and aerodynamic measurement results of the test model 6 before and after installing the vibration suppression device or under different parameter configurations to evaluate the performance of the vibration suppression device;

[0068] According to the feedback of the test data, further optimize the parameters of the vibration suppression device to make it play the best vibration suppression effect under large angles of attack, high speeds or other extreme working conditions.

[0069] The method of damping and frequency adjustment in step S4 is as follows: If the vibration suppression effect is insufficient, the installation position of the adjusting plate 56 on the fixed connecting ear 55 can be adjusted to adjust the gap between the permanent magnet 54 and the conductive metal plate 57, so as to increase or decrease the eddy current damping.

[0070] If there is a deviation in the vibration frequency, different stiffness compression springs 34 can be replaced to change the system stiffness, or the number of mass blocks 41 can be increased or decreased to change the weight of the mass block group 4, so as to realize the adjustment of the tuning frequency.

[0071] Application Scenarios and Effects

[0072] a) Application under large angle of attack flight conditions

[0073] For large angle of attack wind tunnel tests, the test model 6 is often subjected to strong unsteady aerodynamic forces such as flow separation and vortex shedding, and is extremely prone to structural vibration or flutter phenomena. Through the vibration suppression device of the present invention, the vibration amplitude of the test model 6 can be significantly reduced without changing the shape and support structure, ensuring the stability and accuracy of aerodynamic measurement data such as forces and moments.

[0074] b) Other structural modal instability conditions

[0075] For wind tunnel models that need to work under special test conditions such as high Mach number, pulsating flow field or high Reynolds number, the device of the present invention can also be used to suppress the severe vibration generated during structural modal coupling or instability.

[0076] The device parameters can be flexibly adjusted according to different models and experimental conditions, and have strong versatility.

[0077] c) Maintenance and Expansion

[0078] The components of the present invention adopt a modular design, which is convenient for disassembly and maintenance. If subsequent adjustments are needed for different frequencies or different damping requirements, only the springs, mass blocks need to be replaced or increased or decreased, or the gap between the magnet and the aluminum block needs to be repositioned.

[0079] This device can be used in coordination with other vibration monitoring or active control systems to help further improve the accuracy of wind tunnel tests.

[0080] Although the specific implementation manners of the invention have been described in detail in conjunction with the accompanying drawings, it should not be construed as a limitation on the protection scope of this patent. Within the scope described in the claims, various modifications and deformations that can be made by those skilled in the art without creative labor still fall within the protection scope of this patent.

Claims

1. A vibration control device for a large-scale wind tunnel model, characterized in that: It includes a fixed bottom plate (1) and a fixed top plate (2); both ends of the fixed bottom plate (1) and the fixed top plate (2) are connected by support and guide assemblies (3), a mass block group (4) is arranged between the two support and guide assemblies (3), and damping adjustment assemblies (5) which are installed on both sides of the fixed bottom plate (1) and act on the mass block group (4) are arranged on both sides of the mass block group (4); The support and guide assembly (3) includes two optical axis mounting seats (31) respectively installed on the fixed bottom plate (1) and the fixed top plate (2), and an optical axis (32) is arranged between the two optical axis mounting seats (31); A linear bearing (33) is sleeved in the middle of the optical axis (32), and spring assemblies are sleeved on the optical axis (32) at both ends of the linear bearing (33); The mass block group (4) includes several mass blocks (41) and a support cross beam (42) passing through the middle of the several mass blocks (41); the end of the support cross beam (42) is sleeved on the linear bearing (33) and connected to the linear bearing (33); The damping adjustment assembly (5) includes a magnet mounting assembly arranged in the middle of the mass block group (4) and damping mounting assemblies arranged on both sides of the middle of the fixed bottom plate (1); The magnet mounting assembly includes a magnet mounting plate group located in the middle of the mass block group (4) and sleeved on the support cross beam (42); The magnet mounting plate group includes two relatively arranged magnet mounting plates (51); a through hole (52) matching the support cross beam (42) is opened in the middle of the magnet mounting plate (51), two mounting ears (53) are arranged at both ends of the magnet mounting plate (51), and a permanent magnet (54) is arranged on each mounting ear (53).

2. The vibration control device for a large-scale wind tunnel model according to claim 1, wherein: The spring assembly includes a compression spring (34) and a spring seat (35) located at the end of the compression spring (34), and the compression spring (34) and the spring seat (35) are sleeved on the optical axis (32); a rubber gasket (36) is arranged on the collision surface of the spring seat (35).

3. The large-scale wind tunnel model vibration control device according to claim 1, characterized in that: The damping mounting assembly includes a fixed connection ear (55) in the middle of the fixed bottom plate (1), an adjusting plate (56) is movably installed on the fixed connection ear (55), and a conductive metal plate (57) is arranged at the top end of the adjusting plate (56).

4. The large-size wind tunnel model vibration control device according to claim 3, wherein: A strip-shaped hole (58) is opened on the fixed connection ear (55), a threaded hole (59) is opened at the bottom of the adjusting plate (56), and the fixed connection ear (55) and the adjusting plate (56) are connected by inserting a bolt through the strip-shaped hole (58) into the threaded hole (59).

5. The control method of the large-size wind tunnel model vibration control device according to any one of the above-mentioned claims 1-4, characterized in that, It includes the following steps: Step S1, according to the requirements of the wind tunnel test and the size of the test model (6), obtain the modal frequency range of the test model (6); determine the stiffness of the compression spring (34), the weight of the mass block (41), and the initial gap between the permanent magnet (54) and the conductive metal plate (57) according to the modal frequency range; Step S2, install the vibration control device in the reserved cavity (7) inside the top of the test model (6). At the same time, the test model (6) is connected to the scimitar mechanism (9) through the model support rod (8); Step S3: Conduct a wind tunnel test; Step S4: After the wind tunnel test is completed, verify and evaluate the vibration suppression effect. If the vibration suppression effect fails to meet the expected effect, perform damping and frequency adjustment. After adjustment, repeat Step S3 and Step S4 until the expected vibration suppression effect is achieved, and then the test is completed.

6. The control method of the vibration control device for the large-scale wind tunnel model according to claim 5, characterized in that, The method of damping and frequency adjustment in Step S4 is as follows: If the vibration suppression effect is insufficient, the installation position of the adjusting plate (56) on the fixed connection ear (55) can be adjusted, and the gap between the permanent magnet (54) and the conductive metal plate (57) can be adjusted to increase or decrease the eddy current damping; If there is a deviation in the vibration frequency, replace the compression springs (34) with different stiffnesses to change the system stiffness, or increase or decrease the number of mass blocks (41) to change the weight of the mass block group (4) to achieve the adjustment of the tuned frequency.

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