CN106090115B - High linearity quasi-zero stiffness vibration isolators - Google Patents
High linearity quasi-zero stiffness vibration isolators Download PDFInfo
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- CN106090115B CN106090115B CN201610423635.1A CN201610423635A CN106090115B CN 106090115 B CN106090115 B CN 106090115B CN 201610423635 A CN201610423635 A CN 201610423635A CN 106090115 B CN106090115 B CN 106090115B
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- 230000007246 mechanism Effects 0.000 claims abstract description 36
- 238000009434 installation Methods 0.000 claims description 13
- 238000005096 rolling process Methods 0.000 claims description 6
- 230000001105 regulatory effect Effects 0.000 claims description 5
- 230000005389 magnetism Effects 0.000 claims description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims 2
- 238000002955 isolation Methods 0.000 description 11
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 239000010963 304 stainless steel Substances 0.000 description 2
- 229910000589 SAE 304 stainless steel Inorganic materials 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000002360 explosive Substances 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000002153 concerted effect Effects 0.000 description 1
- 230000003750 conditioning effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 238000013139 quantization Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
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
- 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
-
- 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
-
- 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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Electromagnetism (AREA)
- Vibration Prevention Devices (AREA)
Abstract
It is an object of the invention to provide high linearity quasi-zero stiffness vibration isolators, including supporting plate, upper and lower frames, eight groups of horizontal spring mechanisms, eight groups of linkages, one group of three permanent magnet mechanism, four groups vertical supporting mechanism and base, mounting hole is machined with supporting plate, upper framework is provided with four groups of horizontal spring mechanisms, is connected by screw bolts between supporting plate；Four groups of horizontal spring mechanisms are installed on underframe, are connected by four groups of vertical supporting mechanisms with base；It is connected by screw bolts between upper and lower frames；Linkage is installed between eight groups of horizontal spring mechanisms and three permanent magnet mechanism, using pin connection；Design is fluted in the middle part of upper and lower frames junction, to the middle permanent magnet of fixed three permanent magnet mechanism.The present invention realizes the counteracting of predominant non-linearity stiffness term, it is ensured that the high linearity of quasi-zero stiffness vibration isolators, the realization of high linearity make it that the dynamic behavior of quasi- zero stiffness is more stable, and anti-vibration performance is more excellent, can preferably be used for the control of vibration.
Description
Technical field
The present invention relates to a kind of isolation mounting, the specifically isolation mounting available for low frequency vibration isolation field.
Background technology
In recent years, quasi-zero stiffness vibration isolators had been obtained increasingly because of its excellent high static rigidity, low dynamic rate characteristic
More concerns, realize that the mode of quasi- zero stiffness is also varied, wherein more typical method has：Mechanical spring type, permanent magnet
Formula, rubber spring type and electromagnet type ([1] R.A.Ibrahim. " Recent advances in nonlinear
passive vibration isolators.”J.Sound Vib,2008).However, the standard zero that these above-mentioned schemes are realized
Often there is the problem of poor linearity in stiffness characteristics, in other words, it has to add one while quasi- zero stiffness characteristic is realized
A little non-linear rigidities, and it is sometimes attached non-linear very strong.
The patent for being disclosed as the B of CN 102606673 gives a kind of standard that negative stiffness is realized using compression horizontal spring
Zero stiffness spring vibration-isolator structure, it is indicated that the structure has the nonadjustable shortcoming of load-bearing, and gives one kind and utilize electromagnetic spring
The load-bearing of technology can harmonize zero stiffness electromagnetism vibration isolator and its control method.Analyze theory deduction given by the patent and rigidity is bent
Line can be seen that：The patent can substantially add some non-linear rigidities while quasi- zero stiffness is realized, and attached non-thread
Property characteristic deviate equipoise it is larger when become apparent.
The B of Publication No. CN 104033535 patent comprehensive utilization mechanical spring type and the quasi- zero stiffness skill of permanent magnet type
It is subject to auxiliary conditioning unit while art, it is proposed that a three-dimensional vibration isolating device suitable for low-frequency vibration.It is involved horizontal single
The quasi- zero stiffness structure of permanent magnet type is equally arranged on the same line including three on one direction, and middle slip magnet with
In the arrangement that attracts each other between upper and lower fixed magnet.Study and pointed out, the quasi- zero stiffness technology of this kind of permanent magnet type is in realization
Nonlinear Cubic rigidity can be introduced simultaneously, more complicated ([2] A.Carrella. " the On the design of of its dynamic behavior
a high-static–low-dynamic stiffness isolator using linear mechanical springs
and magnets.”J.Sound Vib,2008)。
In summary, the presence of non-linear (especially strong nonlinearity) can not only produce very to the dynamics of system
Big influence, and make it in the extremely difficult control in active control field.
The content of the invention
It is an object of the invention to provide realize the quasi- zero stiffness of high linearity that predominant non-linearity stiffness term is cancelled out each other every
Shake device.
The object of the present invention is achieved like this：
High linearity quasi-zero stiffness vibration isolators of the present invention, it is characterized in that：Including supporting plate, upper framework, underframe, base,
Central shaft, horizontal spring mechanism, upper framework and underframe are fixed together, and supporting plate is fixed on above framework, and base is set
Below underframe, spring is set, upper framework installs lid and upper permanent magnetism centrally through upper permanent magnet between underframe and base
Body mounting seat installs permanent magnet, and underframe installs the lower permanent magnet of lid and bottom seat installation, upper framework centrally through lower permanent magnet
With fixed at underframe cooperation in permanent magnet, central shaft lower end is fixed on base, central shaft upper end sequentially pass through lower permanent magnet,
Middle permanent magnet, upper permanent magnet, central shaft are fixed with lower permanent magnet and upper permanent magnet, passed through between central shaft and middle permanent magnet respectively
Bearing fit, mechanical spring and lower mechanical spring is cased with central shaft, upper mechanical spring is arranged on permanent magnet and middle permanent magnetism
Between body, lower mechanical spring is arranged between middle permanent magnet and lower permanent magnet；
The first-the four upper cantilever beam is stretched out centered on upper framework above permanent magnet, is stretched centered on the following permanent magnet of underframe
Going out the first-the four Analysis of A Cantilever Beam Under, the horizontal spring mechanism includes first level spring unit and the second horizontal spring unit, the
One horizontal spring unit includes spring mounting seat, sliding block, line slideway, linkage, and horizontal spring is installed in spring mounting seat,
Horizontal spring connection sliding block, sliding block are arranged on line slideway, and linkage includes first connecting rod, second connecting rod and is arranged on
Two rolling bearings between first connecting rod and second connecting rod, the first bearing pin and the second bearing pin both pass through first connecting rod and second and connected
Bar, and be engaged respectively with a rolling bearing, the second horizontal spring unit is identical with first level spring unit structure；First
First level spring unit is installed, on the spring mounting seat and line slideway of first level spring unit and first on upper cantilever beam
Cantilever beam is connected, and the first bearing pin is arranged on sliding block, and the second bearing pin is arranged in upper permanent magnet mounting seat, first connecting rod and second
Connecting rod is withstood on sliding block and promotes sliding block to move, and first level spring unit is also installed on the second-the four upper cantilever beam, and it is installed
Mode is identical with the first upper cantilever beam；Second horizontal spring unit is installed on the first Analysis of A Cantilever Beam Under, the second horizontal spring unit
Spring mounting seat and line slideway are connected with the first Analysis of A Cantilever Beam Under, and the first bearing pin is arranged on sliding block, and the second bearing pin is arranged on bottom
On seat, first connecting rod and second connecting rod are withstood on sliding block and promote sliding block to move, and second is also installed on the second-the four Analysis of A Cantilever Beam Under
Horizontal spring unit, its mounting means are identical with the first Analysis of A Cantilever Beam Under.
The present invention can also include：
The 1st, guide groove is set in spring mounting seat, installation and adjustment nut in guide groove, adjusting nut is connected with horizontal spring, adjusts
Installation and adjustment bolt in nut, installed thrust bearing between regulating bolt external part and spring mounting seat.
2nd, middle permanent magnet and upper permanent magnet and lower permanent magnet are all in the attracting arrangement of polarity.
3rd, the spring inner between underframe and base is equipped with the axis of guide, and lower end and the base of the axis of guide are fixed, the axis of guide
Upper end coordinate through underframe and with underframe, linear bearing is installed at the axis of guide and underframe cooperation.
Advantage of the invention is that：The present invention has to draw for existing quasi-zero stiffness vibration isolators when realizing quasi- zero stiffness
Enter non-linear rigidity item this technical problem, mechanical spring type quasi- zero stiffness structure of the comprehensive utilization with gradually hard stiffness characteristics with
And the quasi- zero stiffness structure of permanent magnet type with gradually soft stiffness characteristics, Reasonable adjustment structural parameters, realize predominant non-linearity rigidity
Cancelling out each other for item, finally provides a kind of high linearity quasi-zero stiffness vibration isolators, while give its mechanism parameter to need to meet
Some necessary conditions, realize broader vibration isolation frequency band, strengthen low frequency vibration isolation ability and dynamic stability.
Present invention firstly provides a kind of comprehensive utilization to have the gradually standard firmly with the quasi- zero stiffness structure of gradually software feature respectively
Zero-rigidity vibration isolator, and by Reasonable adjustment structural parameters, realize the counteracting of predominant non-linearity stiffness term, it is ensured that standard zero is firm
The high linearity of vibration isolator is spent, this point is that existing invention is not accomplished.The realization of high linearity causes the dynamic of quasi- zero stiffness
Mechanical behavior is more stable, and anti-vibration performance is more excellent, can preferably be used for the control in vibration problem (especially low-frequency vibration field).
Brief description of the drawings
Fig. 1 is the structure principle chart of the present invention；
Fig. 2 is equal axes axonometric drawing of the present invention；
Fig. 3 is sectional view of the present invention；
Fig. 4 is upper framework trimetric drawing；
Fig. 5 is underframe trimetric drawing；
Fig. 6 is horizontal spring mechanism trimetric drawing；
Fig. 7 is linkage explosive view；
Fig. 8 is three permanent magnet mechanism trimetric drawing；
Fig. 9 is vertical supporting mechanism semi-cutaway；
Figure 10 is the force-displacement curve figure under Different structural parameters；
Figure 11 is rigidity-displacement curve figure under Different structural parameters.
Embodiment
Illustrate below in conjunction with the accompanying drawings and the present invention is described in more detail：
With reference to Fig. 1-11, high linearity quasi-zero stiffness vibration isolators of the present invention, including supporting plate 1, upper and lower frames, eight groups of levels
Spring mechanism, eight groups of linkages, one group of three permanent magnet mechanism, four groups vertical supporting mechanism and base 22.Add in supporting plate 1
Work has installation through-hole, is connected for supporting by vibration isolation object, and by bolt with upper framework 14.Eight groups of horizontal spring mechanism difference
Be installed on the cantilever beam that upper and lower frames is stretched out, respectively four groups of the installation of upper framework 14 and underframe 21, horizontal spring mechanism with
Linkage is designed between three permanent magnet mechanism, passes through pin connection.Fixed between upper framework 14 and underframe 21 using bolt,
Design is fluted at both cooperations, to the middle permanent magnet 17 of fixed three permanent magnet mechanism.In addition, underframe 21 and base 22 it
Between be designed with four groups of vertical supporting mechanisms, to provide the support of positive rigidity.It should be noted that upper framework 14 and underframe 21 are all
Using non-magnetic 304 stainless steel processing and fabricating, the Distribution of Magnetic Field of centering permanent magnet 17 is avoided to have an impact.
Fig. 6 is the trimetric drawing of horizontal spring mechanism in high linearity quasi-zero stiffness vibration isolators of the present invention.The level
Spring mechanism include spring mounting seat 2, adjustment bolt 10, thrust bearing 11, adjusting nut 12, mechanical spring 9, sliding block 15 and
Line slideway 16.Mechanical spring 9 is in compressive state all the time at work, and its one end is fixed in the neck of spring mounting seat 2
On adjusting nut 12, the other end unidirectionally moves freely with sliding block 15 along line slideway 16.Spring mounting seat 2 and straight line are led
Rail 16 is all connected by bolt with the cantilever beam of upper and lower frames.In addition, to realize that the artificial of the position fixed ends of mechanical spring 9 can
Regulation, the indoor design of spring mounting seat 2 have the parts such as adjustment bolt 10, thrust bearing 11 and adjusting nut 12, adjusting nut
12 are stuck among the guide groove of spring mounting seat 2, to prop up mechanical spring 9, while are matched somebody with somebody between regulating bolt 10 by screw thread
Close；Thrust bearing 11 is installed, to reduce frictional force between the two between regulating bolt 10 and spring mounting seat 2；Regulation
Cross-hole is machined with bolt 10, when regulating bolt 10 rotates, drives the change of the horizontal level of adjusting nut 12, Jin Erke
Realize the adjustable of the position fixed ends of mechanical spring 9.
Fig. 7 is the explosive view of linkage in high linearity quasi-zero stiffness vibration isolators of the present invention.The linkage includes
First connecting rod 6, rolling bearing 7 and second connecting rod 8.It is close to connect side by side between first connecting rod 6 and second connecting rod 8, Liang Zhetong
Bolt is crossed to be fixed；Rolling bearing 7 is installed within the groove between first connecting rod 6 and second connecting rod 8, to subtract as far as possible
Frictional force during few connecting rod work between pin.
Fig. 8 is the trimetric drawing of three permanent magnet mechanism in high linearity quasi-zero stiffness vibration isolators of the present invention.Described three forever
Magnet mechanism include upper permanent magnet 3, upper permanent magnet installation lid 4, upper permanent magnet mounting seat 5, central shaft 13, mechanical spring 18, in
Permanent magnet 17, lower permanent magnet 19, lower permanent magnet installation lid 20 and base 22.Upper permanent magnet installation lid 4 is installed with upper permanent magnet
It is bolted between seat 5, to fixed upper permanent magnet 3；Connected between lower permanent magnet installation lid 20 and base 22 by bolt
Connect, to fixed lower permanent magnet 19；Middle permanent magnet 17 is fixed within the groove between upper and lower frames, is all in upper and lower permanent magnet
Polarity is attracting to arrange and copper mechanical spring 18 is provided between.Central shaft 13 sequentially passes through above-mentioned part from top to bottom, with
Upper permanent magnet installation lid 4 and base 22 are bolted and fixed.It should be noted that permanent magnet contacts zero up and down
Part all uses non-magnetic 304 stainless steel processing and fabricating, avoids having an impact its Distribution of Magnetic Field.
Fig. 9 is the semi-cutaway of vertical supporting mechanism in high linearity quasi-zero stiffness vibration isolators of the present invention.The vertical support
Mechanism includes linear bearing 24, the axis of guide 25 and mechanical spring 23.Mechanical spring 23 is installed on underframe 21 by spring base
Between base 22, for supporting by vibration isolation object；The axis of guide 25 is installed, to ensure that vibration isolator exists inside mechanical spring 23
Using when lateral deviation will not occur；The lower end of the axis of guide 25 is fixed by bolt and base 22, and its upper end is passed through on underframe 21
Through hole；Underframe 21 is provided with linear bearing 24 with the junction of the axis of guide 25, to reduce frictional force between the two.
As shown in Figure 1, 2, it is placed in by vibration isolation object in supporting plate 1, upper framework 14 and underframe 21 produce displacement, mechanical elastic
Spring 23 produces cushioning effect, and upper permanent magnet 3 and the lower position of permanent magnet 19 are constant, and middle permanent magnet 17 is with upper framework 14 and underframe 21
Moved along central shaft 13, the spring 18 between upper permanent magnet 3, middle permanent magnet 17, lower permanent magnet 19 is compressed or stretched, and first connects
Bar 6 and second connecting rod 8 produce rotation around the first bearing pin and the second bearing pin, so as to produce the effect of power to horizontal spring.
The determination method of high linearity quasi-zero stiffness vibration isolators structural parameters is：
1st, force analysis is carried out to the high linearity quasi-zero stiffness vibration isolators model shown in Fig. 1, system resilience restoring force is closed
Power f is：
Wherein, f represents that system resilience restoring force is made a concerted effort, and x represents system with respect to the offset of equipoise, kv1Represent to hang down
The rigidity size of mechanical spring, k into supporting constructionv2Represent the rigidity size of mechanical spring in three permanent magnet mechanism, khRepresent
The rigidity size of mechanical spring in horizontal spring mechanism, b represent connecting rod and three permanent magnet mechanism connection end to horizontal spring mechanism
The distance of the fixing end of middle mechanical spring, loThe raw footage of mechanical spring in horizontal spring mechanism is represented, a represents that connecting rod is effectively long
Degree, the distance of permanent magnet and upper and lower permanent magnet during d is represented when system be in equipoise, CmExpression can be by the magnetic of measuring
Constant.
2nd, for ease of subsequent analysis, it is specified that the rigidity size of all vertical springs is all kv, i.e. kv1=kv2=kv, and to bullet
Property restoring force f expression formula carry out nondimensionalization processing, dimensionless restoring force can be obtainedFor：
Wherein,
It should be noted thatμ、λ and δ represents no quantization parameter, xsVibration isolation system when being in former long for spring
System deviates the distance of equipoise.
3rd, using Taylor expansion to dimensionless restoring forceIn equipoisePlace's expansion, can be obtained：
Wherein,
4th, obtained by quasi- zero stiffness condition (α=0)：
When vibration isolator structure parameter determines according to the formula, vibrating isolation system has quasi- zero stiffness characteristic.
5th, obtained by high linearity condition (β=0)：
When vibration isolator structure parameter determines according to the formula, vibrating isolation system can realize the high linearity.
6th, consider step 4 and step 5, it is determined that when realizing quasi- zero stiffness and high linearity vibration isolator structural parameters it
Between the relation that should meet.
Figure 10, Figure 11 be respectively force characteristic curve of the high linearity quasi-zero stiffness vibration isolators under Different structural parameters δ with
Load-deflection curve.Preset parameter is μ=1, λ=0.5,Meet quasi- zero stiffness condition as shown in step 4.Pass through figure
10th, Figure 11 can be seen that (i.e. δ=0.5, such as the reality in two figures when high linearity condition determined by vibration isolator meets step 5
Shown in line) when, mission nonlinear has obtained great reduction, and the quasi- zero stiffness characteristic of High Linear can be achieved；Otherwise, mission nonlinear
It can not be eliminated.
Claims (5)
1. high linearity quasi-zero stiffness vibration isolators, it is characterized in that：Including supporting plate, upper framework, underframe, base, central shaft, water
Coach spring mechanism, upper framework and underframe are fixed together, and supporting plate is fixed on above framework, and base is arranged under underframe
Side, sets spring between underframe and base, upper framework installs lid and upper permanent magnet mounting seat peace centrally through upper permanent magnet
Permanent magnet is loaded onto, underframe installs the lower permanent magnet of lid and bottom seat installation centrally through lower permanent magnet, and upper framework and underframe are matched somebody with somebody
Permanent magnet in being fixed at conjunction, central shaft lower end is fixed on base, central shaft upper end sequentially pass through lower permanent magnet, middle permanent magnet,
Upper permanent magnet, central shaft are fixed with lower permanent magnet and upper permanent magnet respectively, by bearing fit between central shaft and middle permanent magnet,
Mechanical spring and lower mechanical spring are cased with central shaft, upper mechanical spring is arranged between permanent magnet and middle permanent magnet, under
Mechanical spring is arranged between middle permanent magnet and lower permanent magnet；
The first-the four upper cantilever beam is stretched out centered on upper framework above permanent magnet, the is stretched out centered on the following permanent magnet of underframe
One-the four Analysis of A Cantilever Beam Under, the horizontal spring mechanism include first level spring unit and the second horizontal spring unit, the first water
Coach spring unit includes spring mounting seat, sliding block, line slideway, linkage, and horizontal spring is installed in spring mounting seat, horizontal
Spring connection sliding block, sliding block are arranged on line slideway, and linkage includes first connecting rod, second connecting rod and installed in first
Two rolling bearings between connecting rod and second connecting rod, the first bearing pin and the second bearing pin both pass through first connecting rod and second connecting rod,
And be engaged respectively with a rolling bearing, the second horizontal spring unit is identical with first level spring unit structure；On first
First level spring unit is installed on cantilever beam, the spring mounting seat and line slideway of first level spring unit with first
Cantilever beam is connected, and the first bearing pin is arranged on sliding block, and the second bearing pin is arranged in upper permanent magnet mounting seat, first connecting rod and second
Connecting rod is withstood on sliding block and promotes sliding block to move, and first level spring unit is also installed on the second-the four upper cantilever beam, and it is installed
Mode is identical with the first upper cantilever beam；Second horizontal spring unit is installed on the first Analysis of A Cantilever Beam Under, the second horizontal spring unit
Spring mounting seat and line slideway are connected with the first Analysis of A Cantilever Beam Under, and the first bearing pin is arranged on sliding block, and the second bearing pin is arranged on
On base, first connecting rod and second connecting rod are withstood on sliding block and promote sliding block to move, and is also installed on the second-the four Analysis of A Cantilever Beam Under
Two horizontal spring units, its mounting means are identical with the first Analysis of A Cantilever Beam Under.
2. high linearity quasi-zero stiffness vibration isolators according to claim 1, it is characterized in that：Set and lead in spring mounting seat
Groove, installation and adjustment nut in guide groove, adjusting nut are connected with horizontal spring, installation and adjustment bolt in adjusting nut, regulating bolt
Installed thrust bearing between external part and spring mounting seat.
3. high linearity quasi-zero stiffness vibration isolators according to claim 1 or 2, it is characterized in that：Middle permanent magnet and upper permanent magnetism
Body and lower permanent magnet are all in the attracting arrangement of polarity.
4. high linearity quasi-zero stiffness vibration isolators according to claim 1 or 2, it is characterized in that：Between underframe and base
Spring inner the axis of guide is housed, lower end and the base of the axis of guide are fixed, and the upper end of the axis of guide is through underframe and and underframe
Coordinate, the axis of guide is with installing linear bearing at underframe cooperation.
5. high linearity quasi-zero stiffness vibration isolators according to claim 3, it is characterized in that：Bullet between underframe and base
The axis of guide is housed inside spring, lower end and the base of the axis of guide are fixed, and the upper end of the axis of guide coordinates through underframe and with underframe,
The axis of guide is with installing linear bearing at underframe cooperation.
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| CN104455189A (en) * | 2014-10-30 | 2015-03-25 | 东南大学 | Three-dimensional isolation support |
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| Publication number | Priority date | Publication date | Assignee | Title |
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|---|---|---|---|---|
| CN101055014A (en) * | 2006-04-14 | 2007-10-17 | 爱信精机株式会社 | Vibration damping apparatus |
| KR100918646B1 (en) * | 2008-07-11 | 2009-09-28 | 주식회사 져스텍 | Vibration isolator have the low flexure |
| CN102606673A (en) * | 2012-03-26 | 2012-07-25 | 湖南大学 | Load-bearing adjustable zero-stiffness electromagnetic vibration isolator and control method thereof |
| CN104455189A (en) * | 2014-10-30 | 2015-03-25 | 东南大学 | Three-dimensional isolation support |
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| CN106090115A (en) | 2016-11-09 |
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