CN109973571A - A kind of quasi-zero stiffness vibration isolators with horizontal damping - Google Patents
A kind of quasi-zero stiffness vibration isolators with horizontal damping Download PDFInfo
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- CN109973571A CN109973571A CN201711457068.2A CN201711457068A CN109973571A CN 109973571 A CN109973571 A CN 109973571A CN 201711457068 A CN201711457068 A CN 201711457068A CN 109973571 A CN109973571 A CN 109973571A
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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
- F16F7/00—Vibration-dampers; Shock-absorbers
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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)
- Vibration Prevention Devices (AREA)
Abstract
The invention discloses a kind of quasi-zero stiffness vibration isolators with horizontal damping, using two groups of cam-idler wheels-spring mechanism horizontal symmetrical arrangement as negative stiffness structure, and horizontal damping device is added, then in parallel with the positive rigid spring structure arranged vertically, collectively constitute a quasi- zero stiffness vibration isolating mechanism.Choose the stiffness coefficient of matched uprighting spring and horizontal spring, according to by the rigidity of vibration isolation weight and uprighting spring, the height of cam and the pre compressed magnitude of horizontal spring are adjusted, keeps cam concordant with idler wheel central horizontal, makes system that there is quasi- zero stiffness characteristic in the equilibrium position.On the basis of vertical damping is certain, system level damping is rationally designed, can inhibit the covibration for the system of even being eliminated.The vibration isolator has high quiet low dynamic stiffness feature, it can be achieved that low frequency vibration isolation, and structure is simple, easy to maintain, can be widely applied in low-frequency vibration harnessing project.
Description
Technical field
The present invention relates to a kind of low frequency or ultralow frequency nonlinear isolation devices, have in terms of power excitation, displacement excitation
Good vibration isolating effect can be widely applied to ambient vibration, precision instrument, large-sized power unit, ship, submarine, space flight and aviation
And in the low frequency vibration isolation system of flexible structure etc..
Background technique
In engineering field, vibration be cause failure an important factor for one of, traditional linear rigidity vibration isolator is to medium, high frequency
The isolation effect of vibration is good, but undesirable to the isolation effect of low-frequency vibration.Only when driving frequency is greater than the intrinsic frequency of system
RateTimes when just there is vibration isolating effect.Therefore, vibrating isolation system, which need to reduce itself intrinsic frequency just, has low frequency vibration isolation performance, leads to
Normal method is to reduce system stiffness, but rigidity is too small can reduce bearing capacity, cause Static Correction is excessive, system stability not
Foot, linear vibrating isolation system cannot take into account high bearing capacity and low frequency vibration isolation performance.In order to improve the low frequency vibration isolation effect of vibration isolator,
Researchers propose a large amount of novel isolation mountings.Some correlative studys are as follows:
Publication No. CN 104455181 B, it is entitled " it is a kind of using annular permanent magnet generate the quasi- zero stiffness of negative stiffness every
The patent of invention of vibration device " proposes a kind of quasi-zero stiffness vibration isolators that negative stiffness is generated using annular permanent magnet, in vibration processes
In, set interior permanent magnet is opposite with outer permanent magnet, generates negative stiffness to reduce the global stiffness of system, which has Gao Jing
The characteristics of state rigidity and low dynamic rate, the basic excitation of higher magnitude can be isolated, nonlinear effect is weaker, and structure is simple,
It is convenient for disassembly and assembly.However, the invention only analyzes the stiffness characteristics of system, analytic explanation is not carried out to the anti-vibration performance of system,
And the vibrating isolation system is interfered vulnerable to external magnetic field present in practical application.
Publication No. CN 204852123 U, entitled the quasi- zero stiffness vibration reduction platform of flexible modulation " a kind of's can " be practical new
Type patent, the utility model are made of fixed platform, moving platform, damping assembly and thrust assemblies, and damping assembly is with moving platform and calmly
Platform connection, thrust assemblies are arranged on fixed platform, and for applying thrust to moving platform, thrust assemblies are arranged around moving platform
It is multiple.When the utility model can solve the problems, such as conventional linear vibrating isolation system isolation low frequency or superlow frequency vibrating.
205824020 U of Publication No. CN, the utility model patent of entitled " a kind of scissors quasi-zero stiffness vibration isolators " are public
A kind of scissors quasi-zero stiffness vibration isolators are opened, principle of the vibration isolator based on positive and negative stiffness structure parallel connection has high Static stiffness low
Dynamic stiffness characteristic, structure is simple, effective travel is big, the lesser low frequency of excitation amplitude or superlow frequency vibrating can be isolated, but for width
It is worth biggish basic excitation, the displacement transport amplitude in resonance region of system is larger, and covibration is more apparent.
The present invention is the principle based on positive and negative Stiffness, proposes a kind of quasi-zero stiffness vibration isolators with horizontal damping,
The system of being meant to ensure that has high bearing capacity and low frequency vibration isolation performance concurrently, and the increase of horizontal damping, which can further suppress even to be eliminated, is
System covibration, enhances the low frequency or superlow frequency vibration isolating effect of system.
Summary of the invention
The technical problem to be solved by the present invention is to linear vibration isolators can not have high bearing capacity and excellent low frequency concurrently
The shortcomings that anti-vibration performance, proposes a kind of quasi-zero stiffness vibration isolators with horizontal damping.
In order to solve the above technical problems, the technical scheme adopted by the invention is that: a kind of quasi- zero stiffness with horizontal damping
Vibration isolator, including support platform are equipped with vertical direction in the middle part of support platform and are used to provide the uprighting spring of support force, vertically
The bottom end of spring is fixed on the upper surface of pedestal, is arranged with sunpender in support platform, is fixed with band straight line in the bottom end of sunpender
The level board of guide rail；Fixed block is arranged close to the side of support platform in linear guide, and linear guide is close to one end of uprighting spring
Equipped with can be contacted along the sliding shoe that linear guide moves horizontally, the bottom surface of linear guide with the top surface of sliding shoe；Horizontal spring
Both ends are connect with fixed block and sliding shoe by spring fastenings respectively, and horizontal damping is equipped between fixed block and sliding shoe
Device；Sliding shoe is equipped with connecting rod close to the side of uprighting spring, and idler wheel is housed in the other end of connecting rod；At left and right sides of uprighting spring
Baffle is installed, the lower surface of baffle is fixed on pedestal upper surface；Baffle is equipped with vertical straight line guide rail far from the side of uprighting spring,
The vertical slide plate structure for the strap cam that can slide up and down is installed on vertical straight line guide rail；Four are arranged altogether in baffle upper and lower ends
Vertical adjustment axis；The outer surface of cam is contacted with idler wheel；Symmetrical configuration arrangement at left and right sides of uprighting spring.
The fixed block is distinguished with the opposite spring fastenings in position, horizontal spring both ends are respectively fixed on sliding shoe
It is connect with two spring fastenings, so that fixed block and sliding shoe be connected.
The support platform faces and installs Level tune axis at the position at fixed block center, the right end of Level tune axis with
Fixed block contact；Fixed block and sliding shoe are installed on the horizontal guide rail.
The middle position of the vibration-isolating platform is placed with by vibration isolator；Two sides are equipped with vertical adjustment axis to the cam up and down,
Two vertical adjustment axis are all fixed on baffle, and are contacted with the upper and lower end face of vertical slide plate.
Compared with prior art, advantage of the invention are as follows: a kind of quasi-zero stiffness vibration isolators with horizontal damping have enough
Big quiet load-bearing rigidity is supported by vibration isolator, meanwhile, system has low-down dynamic stiffness near equipoise, separately
Outside, the increment of horizontal damping can effectively inhibit system resonance.The present invention has high quiet low dynamic stiffness characteristic, and suppressor system
Resonance, and structure is simple, easy to maintain, is widely used.Therefore, the present invention is suitable for low frequency, even superlow frequency vibration isolating.
Detailed description of the invention
Fig. 1 is the present invention-embodiment composed structure schematic diagram；
Fig. 2 is the theory structure schematic diagram after vibrating isolation system is loaded；
Fig. 3 quasi- zero stiffness system dimensionless rigidity and displacement when being the present invention-embodiment horizontal spring pre compressed magnitude difference
Relation curve；
Fig. 4 is the relationship of quasi- zero stiffness system transmissibility and frequency ratio under the present invention-embodiment different level damping ratio
Curve；
Fig. 5 compares figure for the displacement transport of vibration isolator and equivalent linear system of the present invention for displacement excitation；
Specific embodiment
As depicted in figs. 1 and 2, one embodiment of the invention includes support platform 1, and support platform 1 is by pedestal 19 by erecting
Straight spring 20 supports, and support platform 1 is connect with 20 upper end of uprighting spring, and the lower end of uprighting spring 20 is fixed on the upper table of pedestal 16
Face；Vertical damper 21 is provided between pedestal 16 and support platform 1；It is arranged with sunpender 2 in support platform 1, in sunpender 2
Bottom end be fixed with the level board 3 with linear guide 4；Fixed block 10 is arranged from the closer one end of support platform 1 in linear guide 4；
Linear guide 4 is equipped with close to one end of uprighting spring 20 can be along the sliding shoe 5 that linear guide 4 moves horizontally；Fixed block 10 and cunning
It is connected between motion block 5 by horizontal spring 7 and damper 11；The right side of sliding shoe 5 is equipped with connecting rod 12；Connecting rod 12 is close to vertical bullet
The side of spring 20 is equipped with idler wheel 13；Baffle 17 is installed in the left side of uprighting spring 20, the lower surface of baffle 17 is fixed on pedestal
19 upper surfaces；It is equipped with vertical straight line guide rail 16 on the left of baffle 17, vertical sliding plate 15 is installed on the left of vertical straight line guide rail 16；It is perpendicular
Cam 14 is fixed on the left of straight sliding panel 15；Vertical adjustment axis 18 and vertical adjustment axis is respectively set in 17 upper and lower ends of baffle
23；The symmetrical configuration of the left and right sides is arranged.
Fixed block 10 and sliding shoe 5 are set on horizontal guide rail 4；A bullet is respectively fixed on sliding shoe 5 and fixed block 10
Spring connector 6 and spring fastenings 8, spring fastenings 6 are opposite with 8 position of spring fastenings, connect respectively with 7 both ends of horizontal spring
It connects.
Support platform 1, which faces, installs Level tune axis 9, the right end of Level tune axis 9 at the position at 10 center of fixed block
It is contacted with fixed block 10；Two vertical adjustment axis 18 and 23 are symmetrical arranged on baffle 17, vertical adjustment axis is fixed on baffle 17
On, and contacted with the end face of vertical slide plate 15.
In the present embodiment, there are two horizontal damping devices 11 altogether for the left and right sides, and parameter is identical；Share two parameter phases
Same horizontal spring 7.
In the present embodiment, the position of cam 14 can be adjusted with the decrement of horizontal spring 7, it is ensured that system is in balance position
Vibration nearby is set, high quiet low dynamic stiffness characteristic is made it have.
The rigidity of uprighting spring 20 is kv, the arc groove radius being arranged on 14 curved surface of cam is r1, 13 radius of idler wheel is r2,
Idler wheel 13 is fixed on sliding shoe 5, and cam 14 is mounted in vertical slide plate 15, and cam 14 will be adjusted at the beginning with 13 center of idler wheel
It saves in same horizontal line.When being placed in support platform 1 by vibration isolator 22, uprighting spring 20 is compressed, and decrement is Δ x
=Mg/kv, support platform pushing rolling wheels 13 and sliding shoe 5 are slided to 4 both sides of horizontal linear guide rail.Using vertical adjustment axis 18,
It adjusts vertical sliding plate 15 to move up and down in vertical straight line guide rail 16, makes the center of cam 14 and idler wheel 13 in same horizontal line
On, which is exactly the equipoise of vibrating isolation system, at this point, negative stiffness structure is zero to the resultant force of system, by vibration isolator 22
Weight provided completely by uprighting spring 20, as shown in Figure 2.
When carrying different weight, the decrement of uprighting spring 20 is not also identical, and the center of cam 14 and idler wheel 13 is not
In the same horizontal line, it at this moment needs to rise or fall cam by adjusting vertical adjustment axis 18, guarantees cam 14 and idler wheel
13 center is concordant in the horizontal direction.
By vibration isolator 22 the center for being placed on vibration-isolating platform when, uprighting spring 20 is by by the gravity quilt of vibration isolator 22
It is compressed to certain length, support platform 1 also declines therewith, and idler wheel 13 is the arc along the curved surface of cam 14 during the decline
Shape trough roller is dynamic, pushes sliding shoe 5 close to fixed block 10, horizontal spring 7 is further compressed.At this moment, it needs to adjust system and arrive
Equilbrium position: firstly, adjusting vertical adjustment axis 18, make the center of cam 14 and idler wheel 13 in the same horizontal line；Secondly, being
It when system is in equilbrium position, is supported entirely by uprighting spring 20 by the weight of vibration isolator 22, as long as spring parameter selection is closed in system
It is suitable, the pre compressed magnitude of required horizontal spring can be obtained by adjusting Level tune axis 9, so that the system global stiffness at this position
It is zero.
Meet when being displaced X by vibration isolator 22When, idler wheel 13 remains contact in cam 14,
When the excitation of system stress or displacement excitation, vibratory response is forced by vibration isolator 22 and entire vibration-isolating platform 1, cam 14 is by erecting
Directly adjustment axis 18 is fixed on motionless on vertical straight line guide rail 16, and sliding shoe 5 can only left and right be transported in the horizontal direction in linear guide 4
Dynamic, stretching motion occurs in the horizontal direction for horizontal spring 7, and idler wheel 13 is driven to scroll up and down in 14 curved surface arc groove of cam.It is convex
It takes turns and cancels out each other in the horizontal direction with the interaction force of idler wheel, only system vertical direction is effectively acted on, plays reduction system
The effect of global stiffness.It is vibrated near equilbrium position by vibration isolator 22, system frequency is low, has high bearing capacity and low frequency concurrently
Anti-vibration performance, so can achieve the purpose that low frequency vibration isolation；On the basis of existing vertical damping, horizontal damping, Neng Goujin are added
One step reduces system resonance peak value, inhibits system resonance, improves the low frequency vibration isolation effect of system.
The rigidity ratio for enabling the horizontal spring 7 and the uprighting spring 20 is α, can be horizontal by adjusting when α takes definite value
Pre compressed magnitude δ (δ=δ of spring 70/(r1+r2)), change system global stiffness；When α and δ are met certain condition, system is being balanced
There is zero stiffness characteristic at position.
Such as Fig. 3, when mono- timing of α, with the increase of 7 pre compressed magnitude δ of horizontal spring, the rigidity of system is gradually reduced；When pre-
When decrement is smaller, positive rigid spring 20 plays a leading role, and system global stiffness is positive；Conversely, negative stiffness structure plays a leading role,
The rigidity of system is negative.
When being placed on vibration-isolating platform 1 by vibration isolator 22, uprighting spring 20 generates quiet deformation, and system to be made to be in balance position
It sets, can be realized by adjusting the decrement of 14 position of cam and horizontal spring 7.Therefore, for any quality by vibration isolation
Body 22 can rationally design system parameter, so that system is had the characteristic of quasi- zero stiffness, to realize low frequency vibration isolation.
Vibration isolation the purpose is to reduce vibrating machine to basis effect or reduce the vibration of foundation caused by by vibration isolation object
Vibratory response.The evaluation index of vibration isolating effect includes transmissibility and displacement transport.The definition of transmissibility is to be transmitted to
The power of pedestal and the ratio of exciting force；And being displaced transport is the response displacement amplitude by vibration isolator and the ratio for motivating displacement amplitude
Value.
As harmonic excitation power (amplitude F0) when acting on by vibration isolator 22, mass block bears uprighting spring elastic force, resistance
The collective effect of Buddhist nun's power, negative stiffness structure and exciting force moves up and down in equilbrium position.
Enabling excitation amplitude is f=F0/kv(r1+r2), vertical damping ratio ξ1=c1/(2Mω0), horizontal damping ratio is ξ2=c2/
(2Mω0),c1, c2Respectively vertical damped coefficient and horizontal damping coefficient.
Fig. 4 is the transmissibility comparison diagram of the present embodiment transmissibility and equivalent linear system.Parameter selection are as follows: vertical resistance
Buddhist nun's ratio is ξ1=0.1, amplitude of exciting force f=0.03, rigidity ratio are α=1.
As can be seen from Figure 4, the rigidity of horizontal spring and uprighting spring is more suitable than choosing, and adjusting horizontal spring decrement makes system
With quasi- zero stiffness.Under certain exciting force, present invention starting isolation frequency is more much lower than Hookean spring, ξ2It is bigger after
Effect of shaking is better, and the amplitude of transport is also more much lower than equivalent linear system.In addition, suppressor system is compared in horizontal damping
Resonance, and the transmissibility in off-resonance area is influenced little；Horizontal damping ratio is bigger, and the transmissibility of resonance region is smaller, standard zero
Stiffness system vibration isolating effect is more excellent.
Similarly, under simple harmonic quantity basic excitation (amplitude B) effect, the effect of the vibration isolator is reduced by the vibration of vibration isolator
Dynamic amplitude.
As vertical damping ratio ξ1=0.1, displacement excitation amplitude isRigidity ratio is α=1,
The displacement transport of the vibrating isolation system and the comparison diagram of linear vibrating isolation system are as shown in Figure 5
From figure 5 it can be seen that being displaced transport without peak value, system is without covibration for basic excitation；The present invention can
Realize low frequency vibration isolation, and displacement transport is more much lower than corresponding linear system, has achieved the purpose that motion isolation, effect
It is superior.
Above content is the exemplary description carried out in conjunction with attached drawing to the present invention, and the present invention should not be limited to the embodiment
With attached drawing disclosure of that.All various unsubstantialities carried out using the inventive concept and technical scheme of the present invention are changed
Into or it is not improved directly applying to other occasions, it is within the scope of the present invention.
Claims (5)
1. a kind of quasi-zero stiffness vibration isolators with horizontal damping, it is characterised in that: including support platform, support platform (1) be by
Pedestal (19) is supported by uprighting spring (20), and support platform (1) is connect with uprighting spring (20) upper end, uprighting spring (20)
Lower end is fixed on the upper surface of pedestal (16)；Vertical damper (21) are provided between pedestal (16) and support platform (1)；?
Support platform (1) is internally provided with sunpender (2), is fixed with the level board (3) with linear guide (4) in the bottom end of sunpender (2)；Directly
Line guide rail (4) is from closer one end setting fixed block (10) of support platform (1), and linear guide (4) is close to uprighting spring (20)
One end is equipped with can be along the sliding shoe (5) that linear guide (4) move horizontally；Pass through level between fixed block (10) and sliding shoe (5)
Spring (7) and horizontal damping device (11) connection；The right side of sliding shoe (5) is equipped with connecting rod (12)；Connecting rod (12) is close to uprighting spring
(20) one end is equipped with idler wheel (13)；Baffle (17) are installed in the left side of uprighting spring (20), the lower surface of baffle (17) is solid
It is scheduled on pedestal (19) upper surface；Vertical straight line guide rail (16) are equipped on the left of baffle (17), are pacified on the left of vertical straight line guide rail (16)
It fills vertical sliding plate (15), is fixed with cam (14) on the left of vertical sliding plate (15)；In baffle (17), upper and lower ends are respectively set
Vertical adjustment axis (18) and vertical adjustment axis (23)；Symmetrical configuration arrangement at left and right sides of uprighting spring (20).
2. a kind of quasi-zero stiffness vibration isolators with horizontal damping according to claim 1, it is characterised in that: the cam
(14) curved surface offers arc groove；A spring fastenings (6) is fixed on sliding shoe (5), fixed block (10) is fixed with one
A spring fastenings (8), spring fastenings (6) are opposite with spring fastenings (8) position；Horizontal spring (7) both ends respectively with bullet
Spring connector (6) and (8) connection.
3. a kind of quasi-zero stiffness vibration isolators with horizontal damping according to claim 1, it is characterised in that: the support is flat
It is provided with Level tune axis (9) on platform (1) in the center position for facing fixed block (10), the right end of Level tune axis (9)
With the left contact of fixed block (10).
4. a kind of quasi-zero stiffness vibration isolators with horizontal damping according to claim 1, it is characterised in that: the sliding shoe
(5) it is contacted with the top surface of fixed block (10) with the bottom surface of horizontal linear guide rail (4).
5. a kind of quasi-zero stiffness vibration isolators with horizontal damping according to claim 1, it is characterised in that: the vibration isolation is flat
The middle position of platform (1) is placed with by vibration isolator (22)；Vertical adjustment axis (18) is contacted with the bottom end of vertical slide plate (15), vertically
The tip contact of adjustment axis (23) and vertical slide plate (15).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711457068.2A CN109973571A (en) | 2017-12-28 | 2017-12-28 | A kind of quasi-zero stiffness vibration isolators with horizontal damping |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711457068.2A CN109973571A (en) | 2017-12-28 | 2017-12-28 | A kind of quasi-zero stiffness vibration isolators with horizontal damping |
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Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110285180A (en) * | 2019-07-12 | 2019-09-27 | 中国铁道科学研究院集团有限公司铁道建筑研究所 | The vibration isolator of high quiet low dynamic stiffness characteristic and rail system with it |
| CN110848313A (en) * | 2019-10-09 | 2020-02-28 | 东北大学 | Semi-circular slide rail type quasi-zero stiffness vibration isolator |
| CN110953279A (en) * | 2019-11-22 | 2020-04-03 | 郑州轻工业大学 | Multistage vibration isolation platform based on cam-roller mechanical principle |
| CN111022545A (en) * | 2019-12-06 | 2020-04-17 | 中国民航大学 | Cylinder type high static low dynamic low frequency passive vibration isolator |
| CN111550522A (en) * | 2020-05-19 | 2020-08-18 | 集美大学 | Ship propulsion shafting with high static and low dynamic stiffness oscillator periodic structure |
| CN112377549A (en) * | 2020-11-03 | 2021-02-19 | 同济大学 | Multi-direction quasi-zero rigidity vibration isolation platform |
| CN112963497A (en) * | 2021-02-22 | 2021-06-15 | 江苏大学 | Adjustable quasi-zero stiffness vibration isolator |
| CN113074205A (en) * | 2021-03-23 | 2021-07-06 | 常州大学 | Metal vibration isolator with unidirectional motion damping |
| CN113153963A (en) * | 2021-02-09 | 2021-07-23 | 北京工业大学 | Quasi-zero stiffness vibration isolator containing nonlinear damping |
| CN113639146A (en) * | 2021-07-12 | 2021-11-12 | 浙江工业大学 | Semi-actively controlled quasi-zero stiffness parallel mechanism vibration isolation device and control method |
| CN113669405A (en) * | 2021-08-20 | 2021-11-19 | 内蒙古工业大学 | Variable damping vibration isolation device |
| CN114151507A (en) * | 2021-12-10 | 2022-03-08 | 中国人民解放军海军工程大学 | Quasi-zero stiffness vibration isolator capable of adjusting electromagnetic negative stiffness and vertical eddy current damping |
| CN114278699A (en) * | 2021-11-16 | 2022-04-05 | 中国石油大学(华东) | Two-dimensional plane negative stiffness device |
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- 2017-12-28 CN CN201711457068.2A patent/CN109973571A/en active Pending
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110285180B (en) * | 2019-07-12 | 2024-04-09 | 中国铁道科学研究院集团有限公司铁道建筑研究所 | Vibration isolator with high static and low dynamic stiffness characteristics and track system with vibration isolator |
| CN110285180A (en) * | 2019-07-12 | 2019-09-27 | 中国铁道科学研究院集团有限公司铁道建筑研究所 | The vibration isolator of high quiet low dynamic stiffness characteristic and rail system with it |
| CN110848313A (en) * | 2019-10-09 | 2020-02-28 | 东北大学 | Semi-circular slide rail type quasi-zero stiffness vibration isolator |
| CN110953279B (en) * | 2019-11-22 | 2021-08-13 | 郑州轻工业大学 | Multistage vibration isolation platform based on cam-roller mechanical principle |
| CN110953279A (en) * | 2019-11-22 | 2020-04-03 | 郑州轻工业大学 | Multistage vibration isolation platform based on cam-roller mechanical principle |
| CN111022545A (en) * | 2019-12-06 | 2020-04-17 | 中国民航大学 | Cylinder type high static low dynamic low frequency passive vibration isolator |
| CN111550522A (en) * | 2020-05-19 | 2020-08-18 | 集美大学 | Ship propulsion shafting with high static and low dynamic stiffness oscillator periodic structure |
| CN111550522B (en) * | 2020-05-19 | 2022-08-12 | 集美大学 | Ship propulsion shafting with high static and low dynamic stiffness oscillator periodic structure |
| CN112377549A (en) * | 2020-11-03 | 2021-02-19 | 同济大学 | Multi-direction quasi-zero rigidity vibration isolation platform |
| CN113153963A (en) * | 2021-02-09 | 2021-07-23 | 北京工业大学 | Quasi-zero stiffness vibration isolator containing nonlinear damping |
| CN112963497A (en) * | 2021-02-22 | 2021-06-15 | 江苏大学 | Adjustable quasi-zero stiffness vibration isolator |
| CN113074205B (en) * | 2021-03-23 | 2022-02-22 | 常州大学 | Metal vibration isolator with unidirectional motion damping |
| CN113074205A (en) * | 2021-03-23 | 2021-07-06 | 常州大学 | Metal vibration isolator with unidirectional motion damping |
| CN113639146A (en) * | 2021-07-12 | 2021-11-12 | 浙江工业大学 | Semi-actively controlled quasi-zero stiffness parallel mechanism vibration isolation device and control method |
| CN113669405A (en) * | 2021-08-20 | 2021-11-19 | 内蒙古工业大学 | Variable damping vibration isolation device |
| CN114278699A (en) * | 2021-11-16 | 2022-04-05 | 中国石油大学(华东) | Two-dimensional plane negative stiffness device |
| CN114278699B (en) * | 2021-11-16 | 2024-03-05 | 中国石油大学(华东) | Two-dimensional plane negative stiffness device |
| CN114151507A (en) * | 2021-12-10 | 2022-03-08 | 中国人民解放军海军工程大学 | Quasi-zero stiffness vibration isolator capable of adjusting electromagnetic negative stiffness and vertical eddy current damping |
| CN114151507B (en) * | 2021-12-10 | 2023-07-25 | 中国人民解放军海军工程大学 | Quasi-zero stiffness vibration isolator with adjustable electromagnetic negative stiffness and vertical eddy current damping |
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