Variable load magnetic-levitation three-dimensional high-static-low-dynamic stiffness vibration isolator and method of use

Abstract

The application belongs to the field of vibration isolation and noise reduction equipment, and discloses a variable load magnetic gas type three-way high static low dynamic stiffness vibration isolator and a use method. The variable load magnetic gas type three-way high static low dynamic stiffness vibration isolator comprises a supporting assembly, a positive stiffness assembly and a negative stiffness assembly. The positive stiffness assembly provides static bearing capacity and is composed of an air spring and a linear spring, and the negative stiffness assembly is composed of a magnetic group and a supporting structure thereof, and the purpose of reducing dynamic stiffness is achieved by being connected in parallel with the positive stiffness assembly. The variable load magnetic gas type three-way high static low dynamic stiffness vibration isolator has large static stiffness and small dynamic stiffness, three-way forces generated by the movement between the inner magnetic group and the outer magnetic resistance are used to offset a part of three-way forces generated by the air bag, the function of reducing stiffness is realized, the variable load magnetic gas type three-way high static low dynamic stiffness vibration isolator can adapt to the change of load working conditions, has a wider application scene and better three-way low-frequency vibration isolation performance, a wide vibration isolation frequency band, and stable working performance.

Description

Technical Field

[0001] This invention belongs to the field of vibration isolation and noise reduction equipment, and relates to a variable load magnetic triaxial high static low dynamic stiffness vibration isolator and its usage method. Background Technology

[0002] Ship propulsion shaft systems must withstand longitudinal vibrations transmitted by the propeller and lateral and vertical vibrations generated during navigation. These three-dimensional vibrations severely impact stable operation and the ship's comfort and safety. Existing vibration isolators, limited by their structure, are characterized by high initial isolation frequencies and a lack of three-dimensional isolation capability. Therefore, effectively controlling the low-frequency three-dimensional vibrations generated during mechanical equipment operation is crucial for improving ship performance. Installing vibration isolators is a common method to reduce mechanical vibration, but ordinary linear vibration isolators are not ideal for low-frequency isolation. To expand the isolation frequency band, the system's natural frequency can be lowered. However, this approach reduces system stiffness, decreasing the load-bearing capacity of the isolation system and potentially causing instability in the isolated equipment during operation. Therefore, an ideal vibration isolator should have high static stiffness and low dynamic stiffness. Furthermore, traditional linear vibration isolators require multiple mechanisms to achieve three-dimensional isolation, resulting in complex structures and poor isolation performance.

[0003] The triaxial high static stiffness and low dynamic stiffness vibration isolator proposed in this invention connects a positive stiffness mechanism and a negative stiffness mechanism in parallel. Both the positive and negative stiffness mechanisms possess triaxial offset capabilities. The positive stiffness mechanism determines the load-bearing capacity of the isolator, while the negative stiffness mechanism reduces the system's dynamic stiffness. Therefore, the high static stiffness and low dynamic stiffness vibration isolator can simultaneously possess high static stiffness and low dynamic stiffness, enabling it to withstand large equipment loads while maintaining low dynamic stiffness when the equipment vibrates at its static equilibrium position. However, existing high static stiffness and low dynamic stiffness vibration isolators are mainly designed for specific working conditions. In actual engineering, changes in working conditions, external excitation, and the aging of elastic elements can cause a sharp decline in the system's vibration isolation performance. In such cases, traditional high static stiffness and low dynamic stiffness vibration isolators cannot fully utilize their excellent vibration isolation performance. Summary of the Invention

[0004] The purpose of this application is to provide a variable-load magnetic three-dimensional high static and low dynamic stiffness vibration isolator based on actual needs and the characteristics of air springs and magnetic arrays, through the interaction between magnets and the cooperation of air springs. This invention has excellent low-frequency vibration isolation performance and is not prone to instability, and can be applied to fields such as vibration isolation of precision instruments and vibration reduction of electromechanical equipment.

[0005] The technical solution of this application:

[0006] A variable-load magnetic triaxial high static low dynamic stiffness vibration isolator includes a support assembly, a positive stiffness assembly, and a negative stiffness assembly.

[0007] The vertical direction of the variable load magnetic triaxial high static low dynamic stiffness vibration isolator is defined as vertical Z, the plane formed by horizontal X and longitudinal Y is parallel to the bearing platform, and the angle between horizontal X and vertical Y is 90°.

[0008] The support assembly includes a load-bearing platform, four upper guide columns, a support column, four lower guide columns, and a base. The upper and lower guide columns are cylindrical structures with through holes in the middle. One end of the upper guide column is fixed to the lower surface of the load-bearing platform, and one end of the lower guide column is fixed to the upper surface of the base. The support column is a hollow cylindrical structure. Its upper end is fixed to the lower surface of the load-bearing platform, its outer surface contacts the inner surface of the inner magnetic ring of the negative stiffness component, and its lower end contacts the air spring of the positive stiffness component to transmit triaxial loads. The bottom of the base is provided with a mounting stop for positioning the air spring.

[0009] The positive stiffness assembly includes an air spring and four linear springs. The air spring is mounted and fixed on the base. The two ends of the linear springs are nested at the other ends of the upper and lower guide posts, respectively, to bear part of the vertical load. The air spring and the linear springs are synchronously compressed when subjected to load, providing vertical bearing capacity.

[0010] The negative stiffness component includes an outer magnetic ring, an outer aluminum ring, an inner magnetic ring, an inner aluminum ring, and an outer magnetic assembly bracket. The outer magnetic ring, outer aluminum ring, inner magnetic ring, and inner aluminum ring are located within the outer magnetic assembly bracket. The outer and inner magnetic rings are magnetized alternately radially, with the same layer in the same direction and different layers in opposite directions. Inner aluminum rings are placed between the inner magnetic rings, and the inner magnetic rings and inner aluminum rings are nested on support columns and fixed together with adhesive. Outer aluminum rings are placed between the outer magnetic rings, and the outer magnetic rings and outer aluminum rings are nested outside the inner magnetic rings and inner aluminum rings. The positions of the outer magnetic rings and inner magnetic rings, and the outer aluminum rings and inner aluminum rings, correspond respectively. The outer magnetic rings and outer aluminum rings are fixed together with adhesive. The bottom of the outer magnetic assembly bracket is connected to an air spring and a base.

[0011] Furthermore, the inner magnetic ring, inner aluminum ring, outer magnetic ring, and outer aluminum ring are coaxially mounted. The outer magnetic ring and outer aluminum ring are spaced apart on the outer magnetic assembly bracket, and n layers of outer magnetic rings and n+1 layers of outer aluminum rings form the outer magnetic assembly. The inner magnetic ring and inner aluminum ring are spaced apart on the support column, and n layers of inner magnetic rings and n+1 layers of inner aluminum rings form the inner magnetic assembly. The magnetization direction of each layer of outer and inner magnetic rings is the same, and an air gap is left between the outer and inner magnetic rings. Viewed from top to bottom, the magnetization direction of the first layer of outer and inner magnetic rings is towards the center, the magnetization direction of the second layer of outer and inner magnetic rings is away from the center, the magnetization direction of the third layer of outer and inner magnetic rings is towards the center, the magnetization direction of the fourth layer of outer and inner magnetic rings is away from the center, the magnetization direction of the fifth layer of outer and inner magnetic rings is towards the center, and so on.

[0012] The supporting components are made of high-strength structural steel.

[0013] The material of the outer magnetic assembly bracket is 42CrMo.

[0014] The outer and inner magnetic rings are made of neodymium iron boron (N35).

[0015] A method for using a variable-load magnetic triaxial high static and low dynamic stiffness vibration isolator is disclosed. This isolator is suitable for variable load conditions and reduces the variable load transmitted from the base to the isolated object. It meets the vibration isolation requirements of various load conditions. During use, the object to be isolated must be placed horizontally or fixed on a load-bearing platform, and an appropriate working air pressure must be selected according to the requirements. The load-displacement curves of this variable-load magnetic triaxial high static and low dynamic stiffness vibration isolator under different air pressures are shown in the graph. The appropriate working air pressure can be selected based on this graph. The specific steps are as follows:

[0016] For fixed load conditions, the load is placed on a support platform. Under the influence of gravity, relative motion occurs between the inner and outer magnetic groups. The weight of the load is borne by the elastic force generated by the air spring, the supporting force of the linear spring, and the magnetic force generated by the relative motion between the inner and outer magnetic groups. The air pressure of the air spring is adjusted to the optimal state (constant air spring internal gas volume). At this time, the dynamic stiffness of the variable load magnetic three-dimensional high static low dynamic stiffness vibration isolator is minimal. When the base or support platform is subjected to external dynamic load excitation, the variable load magnetic three-dimensional high static low dynamic stiffness vibration isolator deforms under the load, causing the support column to move laterally, vertically, and longitudinally, so that the variable load magnetic three-dimensional high static low dynamic stiffness vibration isolator reaches a low dynamic stiffness state. In this state, the variable load magnetic three-dimensional high static low dynamic stiffness vibration isolator has strong three-dimensional vibration isolation capability. Under this condition, the variable load magnetic three-dimensional high static low dynamic stiffness vibration isolator is used independently of the air compressor and installed in a confined space.

[0017] When the load changes, the dynamic stiffness of the variable load magnetic triaxial high static low dynamic stiffness vibration isolator is no longer within the optimal stiffness range. It is necessary to start the air compressor to supply air to the air spring in real time (constant air spring pressure) to adjust the dynamic stiffness of the variable load magnetic triaxial high static low dynamic stiffness vibration isolator to the minimum value. When the base or bearing platform is subjected to external dynamic load excitation again, the variable load magnetic triaxial high static low dynamic stiffness vibration isolator will deform under the load, causing the support column to move laterally, vertically, and longitudinally, so that the variable load magnetic triaxial high static low dynamic stiffness vibration isolator reaches a low dynamic stiffness state. In this state, the variable load magnetic triaxial high static low dynamic stiffness vibration isolator has a strong triaxial vibration isolation capability. Under this working condition, the variable load magnetic triaxial high static low dynamic stiffness vibration isolator needs to be supplied with air for a long time to achieve real-time load adjustment.

[0018] The beneficial effects of this invention are as follows: The variable-load magnetic three-dimensional high static and low dynamic stiffness vibration isolator of this invention has a large static stiffness and a small dynamic stiffness. It utilizes the vertical force generated by the movement between the inner magnetic group and the outer magnetic reluctance to offset part of the vertical force generated by the air spring. The transverse and longitudinal forces generated by the offset of the inner magnetic group offset part of the transverse and longitudinal forces of the air spring itself, thereby achieving the effect of reducing stiffness. By adjusting the air pressure of the air spring, the variable-load magnetic three-dimensional high static and low dynamic stiffness vibration isolator can adapt to changes in load conditions, making it applicable to a wider range of scenarios and with better three-dimensional low-frequency vibration isolation performance. Moreover, it has a wide isolation bandwidth and stable operating performance, solving the difficulty of traditional linear vibration isolation systems being unable to isolate low-frequency or even ultra-low-frequency vibrations, and also overcoming the problem that traditional high static and low dynamic stiffness vibration isolators cannot simultaneously achieve three-dimensional vibration isolation. Attached Figure Description

[0019] Figure 1 This is a front cross-sectional view of a magnetic high static low dynamic stiffness vibration isolator;

[0020] Figure 2 It is the support component of a magnetic high static low dynamic stiffness vibration isolator;

[0021] Figure 3 It is the positive stiffness mechanism of a magnetic high static low dynamic stiffness vibration isolator;

[0022] Figure 4 This is a front cross-sectional view of the negative stiffness mechanism of a magnetic high static low dynamic stiffness vibration isolator.

[0023] Figure 5 This is a schematic diagram of the magnetization direction of the magnetic ring in the negative stiffness mechanism of a magnetic high static low dynamic stiffness vibration isolator.

[0024] Figure 6 This is a top view of the negative stiffness mechanism of a magnetic high static low dynamic stiffness vibration isolator;

[0025] Figure 7 This is a schematic diagram of the radial distribution of the magnetic ring in the negative stiffness mechanism of a magnetic high static low dynamic stiffness vibration isolator.

[0026] Figure 8 It is the load-displacement curve of a magnetic high static low dynamic stiffness vibration isolator;

[0027] In the diagram: 1 Support component, 2 Positive stiffness component, 3 Negative stiffness component, 11 Bearing platform, 12 Upper guide column, 13 Support column, 14 Lower guide column, 15 Base, 21 Air spring, 22 Linear spring, 31 Outer magnetic ring, 32 Outer aluminum ring, 33 Inner magnetic ring, 34 Inner aluminum ring, 35 Outer magnetic assembly bracket. Detailed Implementation

[0028] The specific embodiments of the present invention will be further described below with reference to the accompanying drawings and technical solutions.

[0029] like Figure 1 As shown, a variable-load magnetic three-dimensional high static and low dynamic stiffness vibration isolator includes a support assembly 1, a positive stiffness assembly 2, and a negative stiffness assembly 3. Vertically, the positive stiffness assembly 2, composed of an air spring 21 and a linear spring 22, provides static load-bearing capacity to the variable-load magnetic three-dimensional high static and low dynamic stiffness vibration isolator. The magnetic force generated by the lateral movement of the inner and outer magnetic groups is connected in parallel with the load-bearing capacity, thereby reducing the vertical stiffness. Laterally and longitudinally, the magnetic force generated by the lateral displacement of the inner magnetic group partially counteracts the lateral and longitudinal forces of the air springs, thereby reducing the lateral and longitudinal stiffness. When the variable-load magnetic three-dimensional high static and low dynamic stiffness vibration isolator reaches a low dynamic stiffness at its equilibrium position, causing the isolated object to vibrate slightly near the equilibrium position, it can effectively reduce the natural frequency of the variable-load magnetic three-dimensional high static and low dynamic stiffness vibration isolator, achieving wide-range low-starting-frequency vibration isolation and enhancing low-frequency vibration isolation capability.

[0030] The support component 1 includes four guide columns and a load-bearing platform 11, such as Figure 2 As shown, the material is high-strength structural steel or 42CrMo. The length, width and height of the bearing platform 11 are 200mm×200mm×3mm. When in use, the object to be isolated is placed on the bearing platform 11. The upper end of the upper guide column 12 is fastened to the bearing platform 11 by bolts and moves synchronously with the bearing platform 11 when excited. The length, width and height of the base 15 are 200mm×200mm×3mm. When in use, it is placed on the foundation or fixed surface. The lower end of the lower guide column 14 is fastened to the base 15 by bolts. The upper guide column 12 and the lower guide column 14 are used to install and place the linear spring 22, which provides compression force to the linear spring 22 and restricts its radial position.

[0031] The aforementioned positive stiffness component 2 provides positive stiffness, such as Figure 3 As shown. The air spring 21 has an initial height of 65mm when uninflated, a maximum height of 70mm under rated air pressure, a rated air pressure of 5 bar, and a rated load capacity of 50kg. The top of the air spring 21 contacts the bottom of the support column 13. When a vibration-isolated object is placed on the bearing platform 11, the bottom of the support column 13 will press against the top of the air spring 21, thus performing its load-bearing and vibration-isolation functions. The linear spring 22 has an original length of 25mm, is made of 45# steel, has an inner diameter of 15mm, and a wire diameter of 2.1mm.

[0032] The negative stiffness component 3 provides negative stiffness, such as Figure 4As shown. The inner magnetic ring 33 and inner aluminum ring 34 have the same inner and outer diameters, 29.6mm and 39.6mm respectively, and heights of 5mm and 0.5mm respectively; the outer magnetic ring 31 and outer aluminum ring 32 have the same inner and outer diameters, 46mm and 56mm respectively, and heights of 5mm and 0.5mm respectively. The inner magnetic ring 33 and inner aluminum ring 34, and the outer magnetic ring 31 and outer aluminum ring 32 are coaxially mounted. The outer magnetic ring 31 and outer aluminum ring 32 are spaced apart on the outer magnetic assembly bracket 35 and fixed together with glue. The inner magnetic ring 33 and inner aluminum ring 34 are spaced apart on the support column 13 and fixed together with glue. Figure 7 As shown, the outer magnetic ring 31 and inner magnetic ring 33 of each layer are magnetized in the same direction, and there is an air gap between the outer magnetic ring 31 and inner magnetic ring 33. Looking from top to bottom, the outer magnetic ring 31 and inner magnetic ring 33 of the first layer are magnetized towards the center, the outer magnetic ring 31 and inner magnetic ring 33 of the second layer are magnetized away from the center, the outer magnetic ring 31 and inner magnetic ring 33 of the third layer are magnetized towards the center, the outer magnetic ring 31 and inner magnetic ring 33 of the fourth layer are magnetized away from the center, the outer magnetic ring 31 and inner magnetic ring 33 of the fifth layer are magnetized towards the center, and so on.

[0033] like Figure 5 and 6 As shown, each inner magnetic ring 33 and each outer magnetic ring 31 are divided into 6 equal parts around the circumference, and each part is connected with glue.

[0034] A method for using a variable-load magnetic triaxial high static and low dynamic stiffness vibration isolator is disclosed. This isolator is suitable for variable load conditions and reduces the variable load transmitted from the base to the isolated object. It meets the vibration isolation requirements of various load conditions. During use, the object to be isolated must be placed horizontally or fixed on the supporting platform 11, and an appropriate working air pressure must be selected according to the requirements. The load-displacement curves of this variable-load magnetic triaxial high static and low dynamic stiffness vibration isolator under different air pressures are shown in the graph. The appropriate working air pressure can be selected based on this graph. The specific steps are as follows:

[0035] For fixed load conditions, the load is placed on the bearing platform 11. Under the action of gravity, relative motion occurs between the inner and outer magnetic groups. The weight of the load is jointly borne by the elastic force generated by the air spring 21, the supporting force of the linear spring 22, and the magnetic force generated by the relative motion between the magnetic groups. The air pressure of the air spring 21 is adjusted to the optimal state (constant air spring internal gas volume). At this time, the dynamic stiffness of the variable load magnetic three-dimensional high static low dynamic stiffness vibration isolator is minimal. When the base 15 or the bearing platform 11 is subjected to external... When subjected to dynamic load excitation, the variable load magnetic triaxial high static low dynamic stiffness vibration isolator deforms under the load, causing the support column 13 to move laterally, vertically, and longitudinally, so that the variable load magnetic triaxial high static low dynamic stiffness vibration isolator reaches a low dynamic stiffness state. In this state, the variable load magnetic triaxial high static low dynamic stiffness vibration isolator has a strong triaxial vibration isolation capability. Under this working condition, the variable load magnetic triaxial high static low dynamic stiffness vibration isolator is used independently of the air compressor and installed in a confined space.

[0036] When the load changes, the dynamic stiffness of the variable load magnetic triaxial high static low dynamic stiffness vibration isolator is no longer within the optimal stiffness range. It is necessary to start the air compressor to supply air to the air spring 21 in real time (constant air spring pressure) to adjust the dynamic stiffness of the variable load magnetic triaxial high static low dynamic stiffness vibration isolator to the minimum value. When the base 15 or the bearing platform 11 is subjected to external dynamic load excitation again, the variable load magnetic triaxial high static low dynamic stiffness vibration isolator will deform under the load, causing the support column 13 to move laterally, vertically, and longitudinally, so that the variable load magnetic triaxial high static low dynamic stiffness vibration isolator reaches a low dynamic stiffness state. In this state, the variable load magnetic triaxial high static low dynamic stiffness vibration isolator has a strong triaxial vibration isolation capability. Under this working condition, the variable load magnetic triaxial high static low dynamic stiffness vibration isolator needs to be supplied with air for a long time to achieve real-time load adjustment.

[0037] When the load changes under two operating conditions, the air pressure of the air spring 21 controls the magnitude of the system's restoring force. The variable load magnetic triaxial high static and low dynamic stiffness vibration isolator provided by this invention has low manufacturing cost, high operational stability, and is not prone to instability. While possessing variable load capability, it also has excellent low-frequency vibration isolation performance and can be used for vibration reduction of precision instruments, vibration isolation of electromechanical equipment, etc., making it a vibration control equipment with excellent performance.

[0038] In order to avoid mutual magnetization between structures, in the variable load magnetic three-dimensional high static and low dynamic stiffness vibration isolator, in addition to the inner magnetic ring 33, inner aluminum ring 34, outer magnetic ring 31, and outer aluminum ring 32, the structural components near the inner magnetic group and the outer magnetic reluctance may be affected by the magnetic field. Therefore, non-ferromagnetic materials should be used as much as possible.

[0039] A universal testing machine was used to conduct tensile and compressive tests on a magnetic triaxial vibration isolator with variable load and high static and low dynamic stiffness. The experimental results are as follows: Figure 8 As shown in the figure, the region with stable force-displacement changes is the low stiffness region. The above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit the scope of protection of this application. Although this application has been described in detail with reference to the embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of this application without departing from the substance and scope of the technical solutions of this application.

Claims

1. A variable load magnetic- aerostatic three- directional high static low dynamic stiffness vibration isolator, characterized in that, The variable load magnetic triaxial high static low dynamic stiffness vibration isolator includes a support assembly (1), a positive stiffness assembly (2), and a negative stiffness assembly (3). The vertical direction of the variable load magnetic triaxial high static low dynamic stiffness vibration isolator is defined as vertical Z, the plane formed by horizontal X and longitudinal Y is parallel to the bearing platform (11), and the angle between horizontal X and vertical Y is 90°. The support assembly (1) includes a bearing platform (11), four upper guide columns (12), a support column (13), four lower guide columns (14), and a base (15). The upper guide columns (12) and lower guide columns (14) are cylindrical structures with through holes in the middle. One end of the upper guide column (12) is fixed to the lower surface of the bearing platform (11), and one end of the lower guide column (14) is fixed to the upper surface of the base (15). The support column (13) is a hollow cylindrical structure. Its upper end is fixed to the lower surface of the bearing platform (11), its outer surface is in contact with the inner surface of the inner magnetic ring (33) of the negative stiffness assembly (3), and its lower end is in contact with the air spring (21) of the positive stiffness assembly (2) to transmit triaxial loads. The base (15) has a mounting stop at the bottom to position the air spring (21). The positive stiffness component (2) includes an air spring (21) and four linear springs (22). The air spring (21) is installed and fixed on the base (15). The two ends of the linear springs (22) are nested at the other ends of the upper guide post (12) and the lower guide post (14) respectively, and are used to bear part of the vertical load. The air spring (21) and the linear springs (22) are synchronously compressed after being loaded, providing vertical bearing capacity. The negative stiffness component (3) includes an outer magnetic ring (31), an outer aluminum ring (32), an inner magnetic ring (33), an inner aluminum ring (34), and an outer magnetic assembly bracket (35). The outer magnetic ring (31), outer aluminum ring (32), inner magnetic ring (33), and inner aluminum ring (34) are located inside the outer magnetic assembly bracket (35). The outer magnetic ring (31) and the inner magnetic ring (33) are magnetized in the same direction in the same layer and in opposite directions in opposite layers, with the inner aluminum ring (34) arranged between the inner magnetic rings (33). The inner magnetic rings (33) and the inner aluminum rings (34) are nested within each other. On the support column (13), the inner magnetic ring (33) and the inner aluminum ring (34) are fixed with glue; an outer aluminum ring (32) is provided between the outer magnetic rings (31), and the outer magnetic rings (31) and the outer aluminum rings (32) are nested outside the inner magnetic rings (33) and the inner aluminum rings (34). The positions of the outer magnetic rings (31) and the inner magnetic rings (33), and the outer aluminum rings (32) and the inner aluminum rings (34) are respectively corresponding; the outer magnetic rings (31) and the outer aluminum rings (32) are fixed with glue; the bottom of the outer magnetic assembly bracket (35) is connected to the air spring (21) and the base (15).

2. The variable load magnetic-levitation three-dimensional high-static-low-dynamic-stiffness vibration isolator according to claim 1, characterized in that, The inner magnetic ring (33), inner aluminum ring (34), outer magnetic ring (31), and outer aluminum ring (32) are coaxially mounted. The outer magnetic ring (31) and outer aluminum ring (32) are installed alternately on the outer magnetic assembly bracket (35). The n layers of outer magnetic rings (31) and the n+1 layers of outer aluminum rings (32) form the outer magnetic assembly. The inner magnetic ring (33) and inner aluminum ring (34) are installed alternately on the support column (13). The n layers of inner magnetic rings (33) and the n+1 layers of inner aluminum rings (34) form the inner magnetic assembly. The magnetization direction of each layer of outer magnetic ring (31) and inner magnetic ring (33) is the same. There is an air gap between (31) and the inner magnetic ring (33); viewed from the top, the magnetization direction of the outer magnetic ring (31) and the inner magnetic ring (33) of the first layer is towards the center, the magnetization direction of the outer magnetic ring (31) and the inner magnetic ring (33) of the second layer is away from the center, the magnetization direction of the outer magnetic ring (31) and the inner magnetic ring (33) of the third layer is towards the center, the magnetization direction of the outer magnetic ring (31) and the inner magnetic ring (33) of the fourth layer is away from the center, the magnetization direction of the outer magnetic ring (31) and the inner magnetic ring (33) of the fifth layer is towards the center, and so on.

3. The variable load magnetic-levitation three degrees of freedom high-static-low-dynamic-stiffness vibration isolator of claim 1, wherein, The material of the support component (1) is high-strength structural steel.

4. The variable load magnetic-levitation three translational high-static-low-dynamic-stiffness isolator of claim 1, wherein, The material of the outer magnetic assembly bracket (35) is 42CrMo.

5. The variable-load magnetic triaxial high static and low dynamic stiffness vibration isolator according to claim 1, characterized in that, The outer magnetic ring (31) and the inner magnetic ring (33) are made of neodymium iron boron N35.

6. A method of using a variable-load magnetic triaxial high static and low dynamic stiffness vibration isolator as described in claim 1, characterized in that, The steps are as follows: For fixed load conditions; the load is placed on the bearing platform (11). At this time, under the action of gravity, the inner magnetic group and the outer magnetic group will generate relative motion. The weight of the load is jointly borne by the elastic force generated by the air spring (21), the supporting force of the linear spring (22) and the magnetic force generated by the relative motion between the inner magnetic group and the outer magnetic group. Adjust the air pressure of the air spring (21) to the optimal state. At this time, the dynamic stiffness of the variable load magnetic three-way high static low dynamic stiffness vibration isolator is the minimum. When the load changes, the dynamic stiffness of the variable load magnetic triaxial high static low dynamic stiffness vibration isolator is no longer within the optimal stiffness range. It is necessary to start the air compressor to supply air to the air spring (21) in real time and adjust the dynamic stiffness of the variable load magnetic triaxial high static low dynamic stiffness vibration isolator to the minimum value. When the base (15) or the bearing platform (11) is subjected to external dynamic load excitation, the variable load magnetic triaxial high static low dynamic stiffness vibration isolator deforms under the load, causing the support column (13) to move laterally, vertically, and longitudinally, so that the variable load magnetic triaxial high static low dynamic stiffness vibration isolator reaches a lower dynamic stiffness state. Under this state, the variable load magnetic triaxial high static low dynamic stiffness vibration isolator has a strong triaxial vibration isolation capability. Under this working condition, the variable load magnetic triaxial high static low dynamic stiffness vibration isolator needs to be supplied with air for a long time in order to achieve real-time load adjustment.

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