CN115585213B - Modularized vibration isolator with quasi-zero stiffness characteristic and vibration reduction platform thereof - Google Patents
Modularized vibration isolator with quasi-zero stiffness characteristic and vibration reduction platform thereof Download PDFInfo
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- CN115585213B CN115585213B CN202211202197.8A CN202211202197A CN115585213B CN 115585213 B CN115585213 B CN 115585213B CN 202211202197 A CN202211202197 A CN 202211202197A CN 115585213 B CN115585213 B CN 115585213B
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- 230000009467 reduction Effects 0.000 title abstract description 12
- 238000013016 damping Methods 0.000 claims abstract description 35
- 239000002184 metal Substances 0.000 claims abstract description 27
- 238000009434 installation Methods 0.000 claims abstract description 11
- 238000002955 isolation Methods 0.000 claims abstract description 11
- 238000013461 design Methods 0.000 claims abstract description 10
- 238000004146 energy storage Methods 0.000 claims abstract description 10
- 230000005415 magnetization Effects 0.000 claims description 16
- 238000007667 floating Methods 0.000 claims description 14
- 239000007788 liquid Substances 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 5
- 230000003068 static effect Effects 0.000 claims description 4
- 230000036316 preload Effects 0.000 claims description 3
- 125000006850 spacer group Chemical group 0.000 claims description 2
- 230000000694 effects Effects 0.000 abstract description 5
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- 230000006835 compression Effects 0.000 description 6
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/005—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper
- F16F13/007—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper the damper being a fluid damper
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/022—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using dampers and springs in combination
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/03—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using magnetic or electromagnetic means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
- F16F15/067—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs using only wound springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F6/00—Magnetic springs; Fluid magnetic springs, i.e. magnetic spring combined with a fluid
- F16F6/005—Magnetic springs; Fluid magnetic springs, i.e. magnetic spring combined with a fluid using permanent magnets only
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Electromagnetism (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention belongs to the technical field related to vibration control equipment, and discloses a modularized vibration isolator with quasi-zero stiffness characteristic, which comprises a damping unit, a positive stiffness unit and a negative stiffness unit, wherein the damping unit comprises an external cylinder body and an end cover thereof, an internal piston rod and an end cover thereof, an energy storage element and the like; the negative stiffness unit comprises two groups of annular permanent magnets, one group of annular permanent magnets is in repulsive arrangement and is respectively fixed at the inner wall of the cylinder body and the middle part of the piston head, the other group of annular permanent magnets is in attractive arrangement and is respectively fixed at the two ends of the cylinder body and the two ends of the piston head, and the two annular permanent magnets generate negative stiffness through relative movement; the positive stiffness unit comprises a metal pressure spring and an adjusting nut. According to the invention, a wider and stable quasi-zero stiffness interval can be realized, a larger load is provided, and a better vibration isolation effect can be ensured to be provided; in addition, the compact structure can adapt to a narrow installation space, the application universality is improved through the modularized design, and the vibration reduction requirement of multiple degrees of freedom can be realized through arrangement and combination.
Description
Technical Field
The invention belongs to the technical field related to vibration control equipment, and particularly relates to a modularized vibration isolator with a quasi-zero stiffness characteristic and a vibration reduction platform thereof.
Background
The continuous periodic vibration in the flight process has great influence on the onboard equipment such as a map detector, stable aiming and the like, not only affects the operation precision of the onboard equipment, but also can deteriorate the overall operation environment of the equipment, and the damage of the structure is caused. The problem of vibration suppression of airborne equipment has long been a research hotspot of international academia, and most of the airborne equipment has the characteristics of large mass, limited installation space and the like, so that the design of related vibration isolators needs to simultaneously consider both the size and the performance.
For the existing large-mass airborne equipment with limited installation space, the current common vibration reduction means comprise three types: optimizing the structural form of the equipment, coating damping materials or installing vibration isolators and installing vibration absorber transfer equipment. The vibration isolator is mainly based on rubber materials and wire meshes for structural design, has a simple structure, can meet the requirement of large bearing and compact installation space, and has poor vibration isolation performance. The high static and low dynamic characteristics of the quasi-zero stiffness vibration isolator can provide large bearing, meanwhile, the vibration isolation bandwidth of the system can be effectively prolonged, and correspondingly, the vibration isolator has high vibration isolation performance.
However, further studies have shown that the quasi-zero stiffness vibration isolator of the prior art still suffers from the following drawbacks or deficiencies: the positive stiffness element is generally formed by connecting positive and negative stiffness mechanisms in parallel, wherein for the negative stiffness serving as a core technology, the positive stiffness element is mainly realized based on methods such as a buckling beam, a disc spring, a magnet, a cam roller and special materials, and the positive stiffness element is generally formed by adopting a metal spring which is connected in parallel in space. In fact, the parallel mechanism of the above type usually forms a cube, has a large volume and limited application scenes, and is difficult to meet the installation requirement of the vibration reduction system of the loading equipment of the machine.
Disclosure of Invention
In view of the above drawbacks or needs of the prior art, an object of the present invention is to provide a modular vibration isolator with quasi-zero stiffness characteristics and a vibration reduction platform thereof, wherein by redesigning the structural composition and spatial layout of the whole device, the combined magnetic negative stiffness is introduced into the damper, and positive stiffness elements are connected in parallel outside the cylinder, so that a wider and stable quasi-zero stiffness interval can be realized, a larger load can be provided, a better vibration isolation effect can be ensured, and the cost and the power consumption are low; in addition, the compact structure can adapt to a narrow installation space, the application universality can be improved through the modularized design, and the vibration reduction requirement of multiple degrees of freedom is realized through arrangement and combination.
To achieve the above object, according to one aspect of the present invention, there is provided a modular vibration isolator having a quasi-zero stiffness characteristic, the modular vibration isolator including a damping unit, a positive stiffness unit, and a negative stiffness unit arranged in parallel with each other, characterized in that:
The damping unit comprises a cylinder body, a piston rod, a floating piston plate and an energy storage spring, wherein damping liquid is filled in the cylinder body, a cylinder body end cover is arranged at the upper end of the cylinder body, and a static sealing ring is arranged between the cylinder body end cover and the cylinder body; the piston rod is coaxially inserted and arranged in the cylinder body, and a piston rod end cover is arranged at the lower end of the piston rod; the floating piston plate and the energy storage spring are sequentially arranged at the lower part of the piston rod end cover;
The positive stiffness unit comprises a metal pressure spring and an adjusting nut, wherein the metal pressure spring is integrally sleeved outside the cylinder body, one end of the metal pressure spring is contacted with the tail part of the piston rod, and the other end of the metal pressure spring is contacted with the adjusting nut; the adjusting nut is in threaded connection with the outer side of the cylinder body, and the preload of the metal pressure spring is changed by changing the position of the adjusting nut;
The negative stiffness unit comprises an attractive group upper end stator permanent magnet, an attractive group lower end stator permanent magnet, an attractive group upper end rotor permanent magnet, an attractive group lower end rotor permanent magnet, an repulsive group stator permanent magnet and a positioning sleeve, wherein the attractive group upper end stator permanent magnet is fixedly connected with the cylinder end cover, and the attractive group lower end stator permanent magnet is fixedly connected with the floating piston plate, so that a first magnet group which is mutually attracted in an up-down opposite manner is formed; the upper end rotor permanent magnet of the attraction group and the lower end rotor permanent magnet of the attraction group are fixedly connected to the head part of the piston rod, and also form a second magnet group which is oppositely arranged up and down and attracts each other; the repulsive group mover permanent magnet and the repulsive group stator permanent magnet are fixed in the middle of the second magnet group and form a third horizontally opposite repulsive magnet group; furthermore, the positioning sleeve is used for keeping the first to third magnet groups and the piston rod coaxially and annularly installed.
As a further preferred feature, the piston rod is preferably configured in a stepped configuration wherein the outer diameter of the step adjacent the head of the piston rod is greater than the inner diameter of the upper stator permanent magnet of the suction set and the outer diameter of the piston rod end cap is greater than the inner diameter of the lower stator permanent magnet of the suction set.
As a further preferred feature, there is preferably relative movement between the floating piston plate and the positioning sleeve and is connected by a dynamic seal ring; the energy storage spring is preferably compressed during installation, thereby increasing the damping hydraulic pressure inside the cylinder.
As a further preferred option, the first to third magnet groups are each separated from one another by a spacer, and each of the permanent magnets is preferably of hollow-cylindrical design.
As a further preferred aspect, the first and second magnet groups are preferably magnetized in the axial direction, and the upper and lower polarities of the permanent magnets are opposite, wherein the magnetization directions of the upper end stator permanent magnet of the attractive group and the upper end rotor permanent magnet of the attractive group are N up and S down, the magnetization directions of the lower end rotor permanent magnet of the attractive group and the lower end stator permanent magnet of the attractive group are S up and N down, and the outer ring of each permanent magnet is coated with a wear-resistant layer.
As a further preferred aspect, for the third magnet group, it is preferable that the height and the arrangement of the magnetic poles are the same, and radial magnetization with opposite inner and outer polarities is adopted, wherein the magnetization direction of the repulsive group mover permanent magnet is inner N and outer S, the outer ring thereof is plated with a wear-resistant layer, the magnetization direction of the repulsive group stator permanent magnet is inner S and outer N, and the inner ring is plated with a wear-resistant layer.
Further preferably, the tail parts of the piston rod and the cylinder body are respectively provided with external threads so as to be convenient for connecting with different types of adapters.
According to another aspect of the present invention, there is also provided a corresponding single degree of freedom vibration damping platform, wherein the single degree of freedom vibration damping platform is formed by four of the above-mentioned modular vibration isolators and is used for achieving vibration damping characteristics in a vertical direction.
According to another aspect of the present invention, a corresponding multi-degree of freedom vibration damping platform is provided, which is characterized in that the multi-degree of freedom vibration damping platform is jointly formed by the six modularized vibration isolators, and is constructed as a Stewart platform.
In general, compared with the prior art, the above technical solution conceived by the present invention mainly has the following technical advantages:
(1) The invention redesigns the structural composition and the space layout of the whole modularized vibration absorber, introduces the magnetic negative stiffness into the interior of the damper, and connects the positive stiffness spring in parallel on the shell of the cylinder body to realize the configuration of the quasi-zero stiffness vibration isolator, thereby having compact overall structure and being applicable to vibration absorbing environments with limited installation space; meanwhile, the vibration isolator adopts a purely passive design, and has the advantages of simple structure, low cost and low power consumption;
(2) The invention further carries out targeted improvement on the specific structure and the arrangement mode of a plurality of key components such as the negative stiffness units, wherein by adopting two groups of annular permanent magnets, one group is in repulsive arrangement and is respectively fixed at the inner wall of the cylinder body and the middle part of the piston head, the other group is in attractive arrangement and is respectively fixed at the end part of the cylinder body and the end part of the piston head, and the permanent magnets with different two groups of arrangement modes generate negative stiffness through relative motion;
(3) The vibration isolator adopts a modularized design, the joints at the two ends of the vibration isolator can be replaced, the vibration isolator can be suitable for different working scenes, meanwhile, various vibration reduction platforms are constructed through combination, the diversified vibration reduction requirements can be met, and the universality of the application of the vibration isolator is obviously improved.
Drawings
Figure 1 is a cross-sectional view of the overall construction of a modular vibration isolator having quasi-zero stiffness characteristics in accordance with the present invention;
Figure 2 is a schematic diagram showing the principle of the modular vibration isolator shown in figure 1;
figure 3 is a graph showing the negative stiffness of a modular vibration isolator according to the present invention as a function of displacement;
FIG. 4 is a single degree of freedom vibration damping platform constructed from four modular vibration isolators having quasi-zero stiffness characteristics in accordance with a preferred embodiment of the present invention;
figure 5 is a multi-degree of freedom vibration damping platform constructed from six modular vibration isolators with quasi-zero stiffness characteristics in accordance with another preferred embodiment of the present invention.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are some embodiments of the present invention, but not all embodiments of the present invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Figure 1 is a cross-sectional view of the overall structure of a modular vibration isolator having quasi-zero stiffness characteristics in accordance with the present invention. As shown in fig. 1, the device mainly includes a damping unit, a positive stiffness unit, a negative stiffness unit, and the like, which are arranged in parallel with each other, and will be explained in detail one by one.
Referring to fig. 2, a schematic diagram of a modular vibration isolator with quasi-zero stiffness is shown, a base is connected with the lower end of the vibration isolator, vibration displacement is expressed as x, equipment is connected with the upper end of the vibration isolator, vibration displacement is expressed as y, the vibration isolator mainly comprises three parts, namely a damping unit, a negative stiffness unit and a positive stiffness unit, and the damping force and quasi-zero stiffness characteristics are realized through the parallel connection of the three parts. The key negative stiffness unit adopts a combined magnetic negative stiffness structure and consists of a repulsive magnet group and an attractive magnet group, so that a wider stable negative stiffness interval can be realized.
For the damping unit, the damping unit comprises a cylinder body 12, a piston rod 1, a floating piston plate 14 and an energy storage spring 13, wherein the interior of the cylinder body 12 is filled with damping liquid 20, and the upper end of the cylinder body is provided with a cylinder body end cover 3; the piston rod 1 is coaxially inserted and arranged in the cylinder body 12, and a piston rod end cover 17 is arranged at the lower end of the piston rod; the floating piston plate 14 and the energy storage spring 13 are arranged in sequence at the lower part of the piston rod end cover 17.
For the positive rigidity unit, the device comprises a metal pressure spring 2 and an adjusting nut 19, wherein the metal pressure spring 2 is integrally sleeved outside the cylinder body 12, one end of the metal pressure spring 2 is contacted with the tail part of the piston rod 1, and the other end of the metal pressure spring is contacted with the adjusting nut 19; the adjusting nut 19 is screwed to the outside of the cylinder 12 and changes the preload force of the metal compression spring 2 by changing its position. More specifically, the metal compression spring 2 is used for providing positive rigidity, the inner diameter of the metal compression spring is larger than the outer diameter of the cylinder body 12, one end of the metal compression spring is contacted with the tail of the piston rod 1, the other end of the metal compression spring is contacted with the adjusting nut 19, and the pre-loading force of the metal compression spring 2 is changed by changing the position of the adjusting nut 19.
For the negative stiffness unit, the negative stiffness unit is used as one of key components of the invention, and comprises an attractive group upper end stator permanent magnet 4, an attractive group lower end stator permanent magnet 10, an attractive group upper end rotor permanent magnet 6, an attractive group lower end rotor permanent magnet 9, an repulsive group rotor permanent magnet 7, an repulsive group stator permanent magnet 8 and a positioning sleeve 11, wherein the attractive group upper end stator permanent magnet 4 is fixedly connected with the cylinder end cover 3, and the attractive group lower end stator permanent magnet is fixedly connected with the floating piston plate 14, so that a first magnet group which is mutually attracted in an up-down opposite manner is formed; the upper end rotor permanent magnet 6 and the lower end rotor permanent magnet 9 of the attraction group are fixedly connected to the head of the piston rod 1, and form a second magnet group which is oppositely attracted from top to bottom; the repulsive group mover permanent magnet 7 and the repulsive group stator permanent magnet 8 are fixed in the middle of the second magnet group and form a third horizontally opposite repulsive magnet group; furthermore, the positioning sleeve 11 is used for keeping the first to third magnet groups described above coaxially and annularly mounted with the piston rod.
More specifically, referring to fig. 1 and 2 simultaneously, the inside of the cylinder 12 is filled with damping fluid 20, the outside is connected with an adjusting nut 19 by screw threads, and a static sealing ring 21 is installed between the cylinder end cover 3 and the cylinder 12. The piston rod 1 is inserted into the cylinder 12, and leakage is prevented by the movable seal 15. The head of the piston rod 1 is mainly provided with a repulsive group rotor permanent magnet 7, an attractive group upper end rotor permanent magnet 6, a gasket 18, an attractive group lower end rotor permanent magnet 9 and a piston rod end cover 17, and a piston rod head element is fixedly connected with the piston rod 2 through a screw 16, the repulsive group stator permanent magnet 8 is fixed on the inner side of a cylinder body 12, the height of the repulsive group stator permanent magnet is preferably consistent with the height of the whole piston rod head, the axial position of the repulsive group stator permanent magnet is determined through a positioning sleeve 11, the repulsive group stator permanent magnet is coaxially arranged with the piston rod 2, and an annular gap is reserved between the repulsive group stator permanent magnet and the piston rod head as a damping liquid 20 flow channel. The positioning sleeve 11 is fixedly connected with the cylinder body 12, the floating piston plate 14 and the positioning sleeve 11 have relative movement, but the relative movement displacement is smaller, the floating piston plate and the positioning sleeve are connected through the movable sealing ring 15, the energy storage spring 13 compresses during installation, and the liquid pressure of damping liquid 20 in the cylinder body 12 is increased.
In addition, the upper end stator permanent magnet 4 of the attraction group is fixedly connected with the cylinder end cover 3, the lower end stator permanent magnet 10 of the attraction group is fixedly connected with the floating piston plate 14, the upper end rotor permanent magnet 6 of the attraction group and the lower end rotor permanent magnet 9 of the attraction group are fixed at the head of a piston rod, the middle part of the upper end rotor permanent magnet is fixed with the repulsive group rotor permanent magnet 7, and the upper end rotor permanent magnet 6 and the lower end rotor permanent magnet are separated through a gasket 18.
Through the design, when the piston rod 1 is subjected to pressure to move downwards relative to the cylinder body 12, the repulsive group rotor permanent magnet 7 positioned at the head of the piston rod generates the same-direction displacement relative to the repulsive group stator permanent magnet 8, so that the piston rod 1 is subjected to downward acting force, meanwhile, the attractive group lower end rotor permanent magnet 9 at the head of the piston rod is close to the attractive group lower end stator permanent magnet 10, and the attractive force generated between the attractive group lower end rotor permanent magnet 9 and the attractive group lower end stator permanent magnet is greater than the attractive force generated between the attractive group upper end rotor permanent magnet 6 and the upper end stator permanent magnet 4, so that the downward acting force is generated on the piston rod 1, and a negative stiffness effect is further generated; when the piston rod 1 is moved upwards relative to the cylinder 12 by a pulling force, the negative stiffness unit likewise generates a force which facilitates the movement of the piston rod 1. Similarly, when the piston rod 1 is moved upwards relative to the cylinder 12 by a pulling force, the negative stiffness unit likewise generates a force which facilitates the movement of the piston rod. In addition, the metal pressure spring is used for providing positive rigidity, the inner diameter of the metal pressure spring is larger than the outer diameter of the cylinder body, one end of the metal pressure spring is contacted with the tail part of the piston rod, the other end of the metal pressure spring is contacted with the adjusting nut, and the pre-loading force of the metal pressure spring is changed by changing the position of the adjusting nut.
According to a preferred embodiment of the invention, the permanent magnets for realizing the negative stiffness effect are hollow cylindrical, wherein the magnetization directions of the upper stator permanent magnet 4 of the suction group and the upper rotor permanent magnet 6 of the suction group are up N and down S, the magnetization directions of the lower rotor permanent magnet 9 of the suction group and the lower stator permanent magnet 10 of the suction group are up S and down N, and the outer ring is plated with a wear-resistant layer 5; the height and the magnetic pole arrangement mode of the repulsive group rotor permanent magnet 7 and the repulsive group stator permanent magnet 8 are the same, radial magnetization with opposite inner and outer polarities is adopted, wherein the magnetization direction of the repulsive group rotor permanent magnet 7 is inner N and outer S, the outer ring is plated with a wear-resistant layer 5, the magnetization direction of the repulsive group stator permanent magnet 8 is inner S and outer N, the inner ring is plated with a wear-resistant layer 5, and the wear degree caused by the flowing of damping fluid 20 is reduced.
According to another preferred embodiment of the present invention, the piston rod 1 may have a stepped configuration in which the outer diameter of the step near the head of the piston rod is larger than the inner diameter of the stator permanent magnet 4 at the upper end of the attractive group, and the outer diameter of the piston rod end cap 17 is larger than the inner diameter of the stator permanent magnet 10 at the lower end of the attractive group, so that the attractive group permanent magnet mover and the stator are prevented from being attracted together when the piston rod moves up and down.
Referring to fig. 3, a graph of the change of the negative stiffness of the modularized vibration isolator with quasi-zero stiffness along with displacement is shown, the graph is obtained through finite element simulation, and it can be known that the permanent magnet arrangement mode of the invention can ensure a wider stable negative stiffness interval, a specific negative stiffness value can be changed by adjusting structural parameters or residual magnetization intensity, and then the quasi-zero stiffness with a wider stroke can be realized by being connected with a matched positive stiffness unit in parallel, so that the vibration isolation performance of the invention can be effectively improved.
It should be noted that the modularized vibration isolator with the quasi-zero stiffness characteristic is not limited to single use, can be used in combination, has external threads on the cylinder platforms at the tail part of the piston rod and the tail part of the cylinder body, can be connected with different types of adapters, further constructs different types of vibration isolation platforms, and can meet the requirement of vibration reduction with multiple degrees of freedom.
Referring specifically to fig. 4, a single degree of freedom vibration damping platform constructed from four modular vibration isolators with quasi-zero stiffness characteristics is shown in accordance with a preferred embodiment of the present invention. As can be seen from fig. 4, by using multiple sets of modular vibration isolators a, a single degree of freedom vibration damping platform 23 is constructed that can provide greater load bearing while still maintaining good vertical vibration isolation characteristics.
Referring to fig. 5, a multiple degree of freedom vibration damping platform constructed from six modular vibration isolators with quasi-zero stiffness characteristics is shown in accordance with another preferred embodiment of the present invention. As can be seen from fig. 5, the adapter 22 is not limited to one form, and by changing the adapter to a spherical shape, it can be used to construct a Stewart platform 24, which is correspondingly well suited for multi-degree of freedom vibration damping.
In summary, according to the modularized vibration isolator, the combined magnetic negative rigidity is introduced into the damper, and the positive rigidity element is connected in parallel to the outer side of the cylinder body, so that a wider quasi-zero rigidity interval can be realized, a large bearing capacity is provided, and meanwhile, a good vibration isolation effect is ensured, and the modularized vibration isolator is simple in structure, low in cost and low in power consumption; the compact structure can meet the installation requirement of the vibration isolation system of the airborne heavy equipment; the application universality of the invention is improved by the modularized design, the vibration reduction requirement of multiple degrees of freedom can be realized by arrangement and combination, and the invention has wide application prospect.
It will be readily appreciated by those skilled in the art that the foregoing description is merely a preferred embodiment of the invention and is not intended to limit the invention, but any modifications, equivalents, improvements or alternatives falling within the spirit and principles of the invention are intended to be included within the scope of the invention.
Claims (7)
1. A modular vibration isolator having a quasi-zero stiffness characteristic, the modular vibration isolator comprising a damping unit, a positive stiffness unit and a negative stiffness unit arranged in parallel with each other, characterized in that:
The damping unit comprises a cylinder body (12), a piston rod (1), a floating piston plate (14) and an energy storage spring (13), wherein damping liquid (20) is filled in the cylinder body (12), a cylinder body end cover (3) is arranged at the upper end of the cylinder body, and a static sealing ring (21) is arranged between the cylinder body end cover (3) and the cylinder body (12); the piston rod (1) is coaxially inserted into the cylinder body (12), and a piston rod end cover (17) is arranged at the lower end of the piston rod; the floating piston plate (14) and the energy storage spring (13) are sequentially arranged at the lower part of the piston rod end cover (17);
The positive stiffness unit comprises a metal pressure spring (2) and an adjusting nut (19), wherein the metal pressure spring (2) is integrally sleeved outside the cylinder body (12), one end of the metal pressure spring is contacted with the tail part of the piston rod (1), and the other end of the metal pressure spring is contacted with the adjusting nut (19); the adjusting nut (19) is connected with the outer side of the cylinder body (12) in a threaded manner, and the preload of the metal pressure spring (2) is changed by changing the position of the adjusting nut;
The negative stiffness unit comprises an attractive group upper end stator permanent magnet (4), an attractive group lower end stator permanent magnet (10), an attractive group upper end rotor permanent magnet (6), an attractive group lower end rotor permanent magnet (9), an repulsive group rotor permanent magnet (7), an repulsive group stator permanent magnet (8) and a positioning sleeve (11), wherein the attractive group upper end stator permanent magnet (4) is fixedly connected with the cylinder end cover (3), and the attractive group lower end stator permanent magnet (10) is fixedly connected with the floating piston plate (14), so that a first magnet group which is mutually attracted in an up-down opposite mode is formed; the upper end rotor permanent magnet (6) and the lower end rotor permanent magnet (9) of the attraction group are fixedly connected to the head of the piston rod (1) and form a second magnet group which is oppositely attracted from top to bottom; the repulsive group mover permanent magnet (7) and the repulsive group stator permanent magnet (8) are fixed in the middle of the second magnet group and form a third horizontally opposite repulsive magnet group; furthermore, the positioning sleeve (11) is used for keeping the first to third magnet groups and the piston rod coaxially and annularly installed;
For the piston rod (1), a stepped configuration is adopted, wherein the outer diameter of a step close to the head of the piston rod is larger than the inner diameter of the stator permanent magnet (4) at the upper end of the suction group, and the outer diameter of the piston rod end cover (17) is larger than the inner diameter of the stator permanent magnet (10) at the lower end of the suction group; furthermore, the floating piston plate (14) and the positioning sleeve (11) have relative movement, and are connected through a movable sealing ring (15); the energy storage spring (13) compresses during installation, thereby increasing the damping hydraulic pressure inside the cylinder (12).
2. The modular vibration isolator according to claim 1, wherein the first to third magnet sets are each separated from each other by a spacer (18), and wherein each permanent magnet is of hollow cylindrical design.
3. The modular vibration isolator according to claim 2, wherein the first and second magnet groups are magnetized in the axial direction, and the upper and lower polarities of the permanent magnets are opposite, wherein the magnetization directions of the upper stator permanent magnet (4) and the upper rotor permanent magnet (6) of the attractive group are up-N and down-S, the magnetization directions of the lower rotor permanent magnet (9) and the lower stator permanent magnet (10) of the attractive group are up-S and down-N, and the outer ring of each permanent magnet is plated with a wear-resistant layer.
4. A modular vibration isolator according to claim 3, characterized in that for the third magnet group, the height and the arrangement of the magnetic poles are the same, and radial magnetization with opposite inner and outer polarities is adopted, wherein the magnetization direction of the repulsive group mover permanent magnet (7) is inner N and outer S, the outer ring is coated with a wear-resistant layer, the magnetization direction of the repulsive group stator permanent magnet (8) is inner S and outer N, and the inner ring is coated with a wear-resistant layer.
5. A modular vibration isolator according to any of claims 1-4, wherein the tail portions of the piston rod (1) and the cylinder (12) are provided with external threads for connection to different types of adapters (22).
6. A single degree of freedom vibration damping platform, characterized in that the single degree of freedom vibration damping platform is jointly formed by four modularized vibration isolators according to any one of claims 1-5 and is used for achieving vibration isolation characteristics in the vertical direction.
7. A multi-degree-of-freedom vibration-damping platform, which is formed by six modularized vibration isolators according to any one of claims 1-5, and is constructed as a Stewart platform.
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