CN109681573A - A kind of quasi-zero stiffness vibration isolators - Google Patents
A kind of quasi-zero stiffness vibration isolators Download PDFInfo
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- CN109681573A CN109681573A CN201811608877.3A CN201811608877A CN109681573A CN 109681573 A CN109681573 A CN 109681573A CN 201811608877 A CN201811608877 A CN 201811608877A CN 109681573 A CN109681573 A CN 109681573A
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- spring
- quasi
- zero stiffness
- vibration isolators
- magnet ring
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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
- 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
Abstract
The invention discloses a kind of quasi-zero stiffness vibration isolators.It include: central axis, fine-tuning nut, the first spring, electromagnetic spring, second spring and spring fixed ring.One end of central axis is load end, and the other end is free end, and fine-tuning nut, the first spring, electromagnetic spring, second spring and spring fixed ring are successively arranged with from load end to free end, on central axis.It includes the annular hot-wire coil being set in outside central axis and the center magnet ring being set in outside annular hot-wire coil that electromagnetic spring, which includes: in first end magnet ring, intermediate electromagnetism ring and the second end magnet ring, the intermediate electromagnetism ring that center shaft axis direction is successively arranged,.Quasi-zero stiffness vibration isolators provided by the invention can be realized the quasi- zero stiffness in longer stroke, can in the case where guaranteeing bearing capacity extremely efficient vibration isolation frequency band, and it can be adapted under large amplitude, and the anti-vibration performance of quasi-zero stiffness vibration isolators can be further increased by the rigidity of control electric current on-line control vibration isolator.
Description
Technical field
The present invention relates to vibration control fields, more particularly to the adjustable quasi-zero stiffness vibration isolators under a kind of long stroke.
Background technique
Traditional linear vibration isolator has vibration isolation capability when external driving frequency is higher than about 1.4 times of its intrinsic frequency, generally
The quality of load cannot change, it is clear that reducing rigidity is the effective ways for expanding vibration isolation frequency band.It will lead to however, rigidity is too low
Quiet deformation is excessive, and traditional vibration isolator is caused to there are problems that effective vibration isolation frequency band is limited by bearing capacity, in order to solve this
One problem generally can design quasi-zero stiffness vibration isolators using positive Negative stiffness spring parallel connection.Negative stiffness and common positive rigidity phase
It is right, refer to the load increment characteristic contrary with incremental deformation.There is quasi-zero stiffness vibration isolators the guarantee of high static rigidity to hold greatly
Loading capability and low dynamic rate widen the characteristic of vibration isolation frequency band, can be realized the low frequency even vibration isolation of ultralow frequency.But it is existing
Quasi- zero stiffness can only generally realize quasi- zero stiffness in shorter stroke, and linear Stiffness is stronger, vibration amplitude it is excessive or compared with
It can cause the non-linear behaviors such as jump, multistable when big stroke, deteriorate anti-vibration performance.Quasi-zero stiffness vibration isolators in the prior art
It is difficult to realize real zero stiffness, so still having low-frequency resonance problem, which also limits anti-vibration performances.
Summary of the invention
The object of the present invention is to provide a kind of quasi-zero stiffness vibration isolators, the quasi- zero stiffness in longer stroke can be realized, it can
With the extremely efficient vibration isolation frequency band in the case where guaranteeing that bearing capacity does not reduce, and can be in use under large amplitude without generating
Non-linear behavior, and quasi-zero stiffness vibration isolators can be further increased by the rigidity of control electric current on-line control vibration isolator
Anti-vibration performance.
To achieve the above object, the present invention provides following schemes:
A kind of quasi-zero stiffness vibration isolators, comprising: central axis, fine-tuning nut, the first spring, electromagnetic spring, second spring and
Spring fixed ring；
One end of the central axis is load end, and the other end is free end, described from the load end to the free end
Fine-tuning nut, the first spring, electromagnetic spring, second spring and spring fixed ring are successively arranged on central axis；
The electromagnetic spring includes: first end magnet ring, the intermediate electricity being successively arranged in the center shaft axis direction
Magnet ring and the second end magnet ring, the intermediate electromagnetism ring include be set in annular hot-wire coil outside the central axis and
The center magnet ring being set in outside the annular hot-wire coil.
Optionally, the quasi-zero stiffness vibration isolators further include: first bearing seat, retainer, second bearing seat, support base,
Bottom plate, first straight line bearing and second straight line bearing；The center magnet ring is fixed in the retainer；Two bearing blocks point
The both ends of the retainer are not symmetrically mounted on by bolt；The first end magnet ring is fixed on the first bearing seat
Interior, the second end magnet ring is fixed in the second bearing seat；Described first, the second end magnet ring is about in described
Between magnet ring be symmetrical arranged；The both ends of the support base are bolted to connection bottom plate and second bearing seat respectively；The branch
Support seat is hollow structure inside, and the free end of central axis is vacantly inserted into the support base；The first straight line bearing, second are directly
Spool holds the both ends for being respectively arranged in the electromagnetic spring, and the first straight line bearing is fixed in the first bearing seat, institute
Second straight line bearing is stated to be fixed in the second bearing seat.
Optionally, the center magnet ring is equal with the annular axial height of hot-wire coil.
Optionally, the quasi-zero stiffness vibration isolators further include: load and locking nut；The locking nut precession central axis
The thread segment of load end, and the locking nut is used to lock the load.
Optionally, the quasi-zero stiffness vibration isolators further include: two described for the annular hot-wire coil to be fixed to
Coil fixed ring on central axis.
Optionally, first spring and second spring are helical spring.
Optionally, the load is threadedly coupled with the load end of the central axis.
Optionally, the spring fixed ring and the fine-tuning nut could be used for adjusting the electromagnetic spring and described
One, the specific location of second spring.
The specific embodiment provided according to the present invention, the invention discloses following technical effects: provided by the invention quasi- zero
Rigidity vibration isolator, comprising: central axis, fine-tuning nut, the first spring, electromagnetic spring, second spring and spring fixed ring.Using
One, the electromagnetic spring that the second end magnet ring, center magnet ring and annular hot-wire coil are constituted, can be in annular hot-wire coil
Linear negative stiffness is generated when energization, the first and second common helical springs generate linear positive rigidity.Also, by electromagnetic spring with
Helical spring is set as parallel-connection structure, so that it may the quasi- zero stiffness under long stroke is realized, to not reduce in guarantee bearing capacity
In the case where extremely efficient vibration isolation frequency band, anti-vibration performance is improved, and since the rigidity linearity can use well under large amplitude
Do not generate non-linear behavior.In addition, the electric current of electromagnetic spring is closed when quasi-zero stiffness vibration isolators generate low-frequency resonance
Negative stiffness is set 0, quasi- zero stiffness is switched to the higher positive rigidity of helical spring generation to avoid low-frequency resonance, with further
Improve the anti-vibration performance of vibration isolator.In addition, the quasi-zero stiffness vibration isolators in the present invention can pass through spring fixed ring and fine tuning spiral shell
Mother changes spring position to adjust the position of central axis under non-power-up state, so that when carrying different loads, center magnet ring
It can adjust to annular hot-wire coil and be in same axial position, such electromagnetic spring is in equilbrium position, at vibration isolator
In ideal operation state, optimal anti-vibration performance, and then the further expansion scope of application can achieve.
Detailed description of the invention
It in order to more clearly explain the embodiment of the invention or the technical proposal in the existing technology, below will be to institute in embodiment
Attached drawing to be used is needed to be briefly described, it should be apparent that, the accompanying drawings in the following description is only some implementations of the invention
Example, for those of ordinary skill in the art, without creative efforts, can also obtain according to these attached drawings
Obtain other attached drawings.
Fig. 1 is the cross-sectional view of quasi-zero stiffness vibration isolators of the embodiment of the present invention；
Fig. 2 is that the right angle of quasi-zero stiffness vibration isolators of the embodiment of the present invention cuts open structural schematic diagram.
Wherein, 1 is bottom plate, and 2 be spring fixed ring, and 3 be support base, and 4 be second straight line bearing, and 5 be second bearing seat, 6
It is retainer for coil fixed ring, 7,8 be locking nut, and 9 be load, and 10 be fine-tuning nut, and 11 be center magnet ring, and 12 be ring
Shape hot-wire coil, 13 be end magnets ring, and 14 be second spring, and 15 be center axis
Specific embodiment
Following will be combined with the drawings in the embodiments of the present invention, and technical solution in the embodiment of the present invention carries out clear, complete
Site preparation description, it is clear that described embodiments are only a part of the embodiments of the present invention, instead of all the embodiments.It is based on
Embodiment in the present invention, it is obtained by those of ordinary skill in the art without making creative efforts every other
Embodiment shall fall within the protection scope of the present invention.
The object of the present invention is to provide a kind of quasi-zero stiffness vibration isolators, and linear negative stiffness can be generated by electromagnetic spring,
In turn with common linear positive Stiffness, the quasi- zero stiffness in longer stroke is realized, can not reduce guaranteeing bearing capacity
In the case where extremely efficient vibration isolation frequency band, and and can lead in use under large amplitude without generating non-linear behavior
The rigidity for crossing control electric current on-line control vibration isolator, further increases the anti-vibration performance of quasi-zero stiffness vibration isolators.
In order to make the foregoing objectives, features and advantages of the present invention clearer and more comprehensible, with reference to the accompanying drawing and specific real
Applying mode, the present invention is described in further detail.
Fig. 1 is the structural schematic diagram of quasi-zero stiffness vibration isolators of the embodiment of the present invention, as shown in Figure 1, standard provided by the invention
Zero-rigidity vibration isolator includes: bottom plate, spring fixed ring, second spring, support base, second straight line bearing, second bearing seat, and second
End magnets ring, retainer, center magnet ring, annular hot-wire coil, first end magnet ring, coil fixed ring, first bearing
Seat, first straight line bearing, the first spring, fine-tuning nut, locking nut, load and central axis.
Load is threadedly coupled with the load end of central axis, and the locking nut by being sheathed on central axis is locked
Tightly, the stability of load is had an impact to avoid vibration.
One end of central axis is load end, and the other end is free end, from load end to free end, is successively arranged on central axis
There are fine-tuning nut, the first spring, electromagnetic spring, second spring and spring fixed ring.
First end magnet ring, annular hot-wire coil, center magnet ring and the second end magnet ring are sequentially sleeved at center
On axis axis direction, and center magnet ring is coaxial with annular hot-wire coil and is set in outside annular hot-wire coil, and annular is powered
Coil is fixed on center shaft by two coil fixed rings.Center magnet ring is fixed on middle position on the inside of retainer, and with
The axial height of annular hot-wire coil is equal.First end magnet ring is fixed in first bearing seat, and the second end magnet ring is solid
It is scheduled in second bearing seat, two bearing blocks pass through the both ends that bolt is symmetrically mounted on retainer, the first and second ends respectively
Magnet ring is symmetrical about center magnet ring, and three magnet ring relative positions are fixed, and annular hot-wire coil can be with opposed magnet annulate shaft
To movement.
The both ends of support base are bolted to connection bottom plate and second bearing seat respectively, and support base is inner hollow knot
The free end of structure, central axis is vacantly inserted into support base.First straight line bearing, second straight line bearing are located at electromagnetic spring
Both ends, first straight line bearing are fixed in first bearing seat, and second straight line bearing is fixed in second bearing seat.Two linear axis
Holding can only axially move for limiting central axis.
Bottom plate is for being mounted on provided quasi-zero stiffness vibration isolators using pedestal.
First, second spring generates positive rigidity, and spring is directed toward intermediate equilbrium position to the power of central axis, that is to say, that
The power of spring makes central axis be maintained at equilbrium position.
Further, the state on quasi-zero stiffness vibration isolators plus control electric current illogical after load is as quasi- zero stiffness vibration isolation
The non-power-up state of device, non-power-up state quasi-zero stiffness vibration isolators central axis when equilbrium position, guarantee electromagnetism
Spring is also at equilbrium position, is realized by coarse adjustment or fine tuning spring fixed ring and fine-tuning nut.
When annular hot-wire coil and center magnet ring are in sustained height, since electromagnetic field is symmetrical, intermediate annular is logical
Electromagnetic force suffered by electric coil is 0.This position is known as the equilbrium position of electromagnetic spring.The quality loaded at this time is all by positive rigidity
Spring, that is, the first spring and second spring carrying, the negative stiffness of electromagnetic spring will not influence the high-mechanic of positive rigid spring
Ability.Quasi-zero stiffness vibration isolators are in ideal operation state at this time, change electric current in the annular hot-wire coil of electromagnetic spring not
This ideal operation state can be changed.Annular hot-wire coil and periphery when pedestal drives bottom plate to vibrate, on central axis
Center magnet ring can generate relative displacement, annular hot-wire coil will receive the repulsive force that center magnet is directed toward both sides after being powered,
And two end magnets fourth fingers are to the attraction at both ends, that is to say, that at this time by two end magnets rings, center magnet ring and
Annular hot-wire coil is formed by electromagnetic spring, and when energization makes annular hot-wire coil far from equilbrium position, shows as negative stiffness.
Negative stiffness in parallel can reduce the integral stiffness of vibration isolator, to extend vibration isolation frequency band, improve anti-vibration performance.
Rigidity of the relative position of annular hot-wire coil and center magnet ring by the first and second springs under non-power-up state
It is influenced with the quality of position and load.Also, by changing spring fixed ring in the position of central axis, thus it is possible to vary spring position
The relative position of center magnet ring and annular hot-wire coil under non-power-up state is set and changes, then rotary fine adjustment nut can be to this
As soon as relative position is accurately finely tuned, this can allow quasi-zero stiffness vibration isolators under conditions of loading different loads,
Electromagnetic spring is adjustable to equilbrium position, so that vibration isolator is in ideal operation state, is optimal anti-vibration performance.Moreover, will
Fine-tuning nut is external, also facilitates user and is adjusted.
Quasi-zero stiffness vibration isolators provided by the present invention, by using the first, second end magnets ring, center magnet ring,
An electromagnetic spring is constituted with annular hot-wire coil, so that the electromagnetic force and relative displacement that generate when annular hot-wire coil is powered
It is linear, that is, linear negative stiffness is produced, the first and second common helical springs generate linear positive rigidity.By this
Electromagnetic spring and helical spring are set as parallel-connection structure, the quasi- zero stiffness under long stroke may be implemented, thus not reducing carrying
Extremely efficient vibration isolation frequency band in the case where ability, and since this quasi- zero stiffness linearity is good, can be used under large amplitude without
Generate non-linear behavior.In addition, On-line Control can will bear electric current closing when low-frequency resonance occurs for quasi-zero stiffness vibration isolators
Rigidity is cancelled, and quasi- zero stiffness is switched to the higher positive rigidity of helical spring generation so as to avoid low-frequency resonance, this is into one
Step improves the anti-vibration performance of vibration isolator.
Each embodiment in this specification is described in a progressive manner, the highlights of each of the examples are with other
The difference of embodiment, the same or similar parts in each embodiment may refer to each other.
Used herein a specific example illustrates the principle and implementation of the invention, and above embodiments are said
It is bright to be merely used to help understand method and its core concept of the invention；At the same time, for those skilled in the art, foundation
Thought of the invention, there will be changes in the specific implementation manner and application range.In conclusion the content of the present specification is not
It is interpreted as limitation of the present invention.
Claims (9)
1. a kind of quasi-zero stiffness vibration isolators characterized by comprising central axis, fine-tuning nut, the first spring, electromagnetic spring,
Two springs and spring fixed ring；
One end of the central axis is load end, and the other end is free end, from the load end to the free end, the center
Fine-tuning nut, the first spring, electromagnetic spring, second spring and spring fixed ring are successively arranged on axis；
The electromagnetic spring includes: the first end magnet ring being successively arranged in the center shaft axis direction, intermediate electromagnetism ring
With the second end magnet ring, the intermediate electromagnetism ring includes the annular hot-wire coil being set in outside the central axis and is arranged
Center magnet ring outside the annular hot-wire coil.
2. a kind of quasi-zero stiffness vibration isolators according to claim 1, which is characterized in that the quasi-zero stiffness vibration isolators also wrap
It includes: first bearing seat, retainer, second bearing seat, support base, bottom plate, first straight line bearing and second straight line bearing；In described
Between magnet ring be fixed in the retainer；Two bearing blocks pass through the both ends that bolt is symmetrically mounted on the retainer respectively；
The first end magnet ring is fixed in the first bearing seat, and the second end magnet ring is fixed on the second bearing
In seat；Described first, the second end magnet ring is symmetrical arranged about the center magnet ring；The both ends of the support base lead to respectively
It crosses bolt and is fixedly connected with bottom plate and second bearing seat；The support base is hollow structure inside, and the free end of central axis is vacantly inserted
Enter in the support base；The first straight line bearing, second straight line bearing are respectively arranged in the both ends of the electromagnetic spring, described
First straight line bearing is fixed in the first bearing seat, and the second straight line bearing is fixed in the second bearing seat.
3. a kind of quasi-zero stiffness vibration isolators according to claim 1, which is characterized in that the center magnet ring and the ring
The axial height of shape hot-wire coil is equal.
4. a kind of quasi-zero stiffness vibration isolators according to claim 1, which is characterized in that the quasi-zero stiffness vibration isolators also wrap
It includes: load and locking nut；The thread segment at the locking nut precession central axial load end, and the locking nut is used for institute
State load locking.
5. a kind of quasi-zero stiffness vibration isolators according to claim 1, which is characterized in that the quasi-zero stiffness vibration isolators also wrap
It includes: two coil fixed rings for being fixed to the annular hot-wire coil on the central axis.
6. a kind of quasi-zero stiffness vibration isolators according to claim 1, which is characterized in that first spring and second spring
It is helical spring.
7. a kind of quasi-zero stiffness vibration isolators according to claim 1, which is characterized in that the load and the central axis
Load end is threadedly coupled.
8. a kind of quasi-zero stiffness vibration isolators according to claim 2, which is characterized in that the bottom plate is used for described quasi- zero
Rigidity vibration isolator is installed on using on pedestal.
9. a kind of quasi-zero stiffness vibration isolators according to claim 1, which is characterized in that the spring fixed ring and described micro-
Nut is adjusted to could be used for adjusting the specific location of the electromagnetic spring and first, second spring.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201811608877.3A CN109681573B (en) | 2018-12-27 | 2018-12-27 | Quasi-zero stiffness vibration isolator |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201811608877.3A CN109681573B (en) | 2018-12-27 | 2018-12-27 | Quasi-zero stiffness vibration isolator |
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| CN109681573A true CN109681573A (en) | 2019-04-26 |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110513419A (en) * | 2019-09-23 | 2019-11-29 | 上海大学 | A kind of adjustable quasi-zero stiffness vibration isolators based on magnetic Circuit Design |
| CN110645314A (en) * | 2019-10-17 | 2020-01-03 | 贵州詹阳动力重工有限公司 | Quasi-zero stiffness vibration isolator with low-frequency broadband characteristic |
| CN110645310A (en) * | 2019-09-23 | 2020-01-03 | 重庆大学 | Piezoelectric self-powered electromagnetic negative stiffness vibration isolation system and control method thereof |
| CN110646187A (en) * | 2019-10-09 | 2020-01-03 | 太原科技大学 | Negative stiffness characteristic testing device and method |
| CN110671459A (en) * | 2019-09-23 | 2020-01-10 | 重庆大学 | Quasi-zero stiffness vibration isolator with compact structure |
| CN111075873A (en) * | 2020-01-07 | 2020-04-28 | 长沙理工大学 | Load-variable ultralow frequency vibration isolator and design method thereof |
| CN112709781A (en) * | 2020-12-31 | 2021-04-27 | 山东大学 | Torsion quasi-zero stiffness vibration isolator with adjustable balance position and method |
| CN115727094A (en) * | 2022-11-29 | 2023-03-03 | 武汉理工大学 | Compact low-frequency vibration isolation device with parallel magnetic negative stiffness structure |
| CN115789164A (en) * | 2022-11-29 | 2023-03-14 | 武汉理工大学 | Rubber and electromagnetism parallel connection adjustable rigidity low-frequency vibration isolation device |
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| CN108571559A (en) * | 2018-07-25 | 2018-09-25 | 上海大学 | A kind of damper means of stiffness variable adaptive damping |
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| DE102010029910A1 (en) * | 2010-06-10 | 2011-12-15 | Bayerische Motoren Werke Aktiengesellschaft | Active oscillation damper for motor car, has single spring element units implemented in shape memory alloy of upper and lower spring elements |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110513419A (en) * | 2019-09-23 | 2019-11-29 | 上海大学 | A kind of adjustable quasi-zero stiffness vibration isolators based on magnetic Circuit Design |
| CN110645310A (en) * | 2019-09-23 | 2020-01-03 | 重庆大学 | Piezoelectric self-powered electromagnetic negative stiffness vibration isolation system and control method thereof |
| CN110671459A (en) * | 2019-09-23 | 2020-01-10 | 重庆大学 | Quasi-zero stiffness vibration isolator with compact structure |
| CN110513419B (en) * | 2019-09-23 | 2020-07-14 | 上海大学 | Adjustable quasi-zero stiffness vibration isolator based on magnetic circuit design |
| CN110646187A (en) * | 2019-10-09 | 2020-01-03 | 太原科技大学 | Negative stiffness characteristic testing device and method |
| CN110646187B (en) * | 2019-10-09 | 2022-03-15 | 太原科技大学 | Negative stiffness characteristic testing device and method |
| CN110645314A (en) * | 2019-10-17 | 2020-01-03 | 贵州詹阳动力重工有限公司 | Quasi-zero stiffness vibration isolator with low-frequency broadband characteristic |
| CN111075873A (en) * | 2020-01-07 | 2020-04-28 | 长沙理工大学 | Load-variable ultralow frequency vibration isolator and design method thereof |
| CN112709781A (en) * | 2020-12-31 | 2021-04-27 | 山东大学 | Torsion quasi-zero stiffness vibration isolator with adjustable balance position and method |
| CN115727094A (en) * | 2022-11-29 | 2023-03-03 | 武汉理工大学 | Compact low-frequency vibration isolation device with parallel magnetic negative stiffness structure |
| CN115789164A (en) * | 2022-11-29 | 2023-03-14 | 武汉理工大学 | Rubber and electromagnetism parallel connection adjustable rigidity low-frequency vibration isolation device |
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