CN109681573B - Quasi-zero stiffness vibration isolator - Google Patents
Quasi-zero stiffness vibration isolator Download PDFInfo
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- CN109681573B CN109681573B CN201811608877.3A CN201811608877A CN109681573B CN 109681573 B CN109681573 B CN 109681573B CN 201811608877 A CN201811608877 A CN 201811608877A CN 109681573 B CN109681573 B CN 109681573B
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- spring
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- vibration isolator
- central shaft
- zero stiffness
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/03—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using magnetic or electromagnetic means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
Abstract
The invention discloses a quasi-zero stiffness vibration isolator. The method comprises the following steps: center pin, fine setting nut, first spring, electromagnetism spring, second spring and spring fixing ring. One end of the central shaft is a load end, the other end of the central shaft is a free end, and a fine adjustment nut, a first spring, an electromagnetic spring, a second spring and a spring fixing ring are sequentially sleeved on the central shaft from the load end to the free end. The electromagnetic spring includes: the electromagnetic ring comprises a first end magnet ring, a middle electromagnetic ring and a second end magnet ring which are sequentially sleeved in the axis direction of the central shaft, wherein the middle electromagnetic ring comprises an annular energizing coil sleeved outside the central shaft and a middle magnet ring sleeved outside the annular energizing coil. The quasi-zero stiffness vibration isolator provided by the invention can realize quasi-zero stiffness in a longer stroke, can expand an effective vibration isolation frequency band under the condition of ensuring the bearing capacity, can be suitable for large amplitude, can adjust the stiffness of the vibration isolator on line by controlling current, and further improves the vibration isolation performance of the quasi-zero stiffness vibration isolator.
Description
Technical Field
The invention relates to the field of vibration control, in particular to a zero-stiffness vibration isolator capable of being adjusted under a long stroke.
Background
The conventional linear vibration isolator has vibration isolation capability when the external excitation frequency is about 1.4 times higher than the natural frequency, the mass of a common load cannot be changed, and obviously, the reduction of the rigidity is an effective method for expanding the vibration isolation frequency band. However, too low stiffness causes excessive static deformation, so that the conventional vibration isolator has the problem that the effective vibration isolation frequency band is limited by the bearing capacity. Negative stiffness, as opposed to the usual positive stiffness, refers to the characteristic of load increment being opposite in direction to the deformation increment. The quasi-zero stiffness vibration isolator has the characteristics of ensuring high bearing capacity by high static stiffness and widening vibration isolation frequency band by low dynamic stiffness, and can realize low-frequency or even ultra-low-frequency vibration isolation. However, the existing quasi-zero stiffness can only realize the quasi-zero stiffness in a short stroke generally, the stiffness nonlinearity is strong, and the vibration isolation performance is deteriorated due to the nonlinear behaviors such as jump and multi-stable state caused by an overlarge vibration amplitude or a large stroke. The quasi-zero stiffness vibration isolator in the prior art is difficult to realize real zero stiffness, so the problem of low-frequency resonance still exists, and the vibration isolation performance is limited.
Disclosure of Invention
The invention aims to provide a quasi-zero stiffness vibration isolator which can realize quasi-zero stiffness in a long stroke, can expand effective vibration isolation frequency band under the condition of ensuring that the bearing capacity is not reduced, can be used under large amplitude without generating nonlinear behavior, can adjust the stiffness of the vibration isolator on line by controlling current, and further improves the vibration isolation performance of the quasi-zero stiffness vibration isolator.
In order to achieve the purpose, the invention provides the following scheme:
a quasi-zero stiffness vibration isolator comprising: the device comprises a central shaft, a fine adjustment nut, a first spring, an electromagnetic spring, a second spring and a spring fixing ring;
one end of the central shaft is a load end, the other end of the central shaft is a free end, and a fine adjustment nut, a first spring, an electromagnetic spring, a second spring and a spring fixing ring are sequentially sleeved on the central shaft from the load end to the free end;
the electromagnetic spring includes: the electromagnetic ring comprises a first end magnet ring, a middle electromagnetic ring and a second end magnet ring, wherein the first end magnet ring, the middle electromagnetic ring and the second end magnet ring are sequentially sleeved in the axis direction of the central shaft, and the middle electromagnetic ring comprises an annular electrified coil and a middle magnet ring, the annular electrified coil is sleeved outside the central shaft, and the middle magnet ring is sleeved outside the annular electrified coil.
Optionally, the quasi-zero stiffness vibration isolator further comprises: the device comprises a first bearing seat, a retainer, a second bearing seat, a supporting seat, a bottom plate, a first linear bearing and a second linear bearing; the middle magnet ring is fixed in the retainer; the two bearing blocks are symmetrically arranged at the two ends of the retainer respectively through bolts; the first end magnet ring is fixed in the first bearing seat, and the second end magnet ring is fixed in the second bearing seat; the first and second end magnet rings are symmetrically disposed about the middle magnet ring; two ends of the supporting seat are fixedly connected with the bottom plate and the second bearing seat through bolts respectively; the supporting seat is of an internal hollow structure, and the free end of the central shaft is inserted into the supporting seat in a hanging manner; the first linear bearing and the second linear bearing are respectively arranged at two ends of the electromagnetic spring, the first linear bearing is fixed on the first bearing seat, and the second linear bearing is fixed on the second bearing seat.
Optionally, the axial height of the middle magnet ring is equal to that of the annular energizing coil.
Optionally, the quasi-zero stiffness vibration isolator further comprises: a load and lock nut; the locking nut is screwed into the thread section of the load end of the central shaft and is used for locking the load.
Optionally, the quasi-zero stiffness vibration isolator further comprises: two coil fixing rings for fixing the annular energizing coil to the central shaft.
Optionally, the first spring and the second spring are both coil springs.
Optionally, the load is threadedly connected to the load end of the central shaft.
Optionally, the spring fixing ring and the fine adjustment nut can be used for adjusting specific positions of the electromagnetic spring and the first and second springs.
According to the specific embodiment provided by the invention, the invention discloses the following technical effects: the invention provides a quasi-zero stiffness vibration isolator, which comprises: center pin, fine setting nut, first spring, electromagnetism spring, second spring and spring fixing ring. The electromagnetic spring formed by the first end magnet ring, the second end magnet ring, the middle magnet ring and the annular energizing coil can generate linear negative stiffness when the annular energizing coil is energized, and the common first spiral spring and the common second spiral spring generate linear positive stiffness. And the electromagnetic spring and the spiral spring are arranged into a parallel structure, so that the quasi-zero stiffness under a long stroke can be realized, the effective vibration isolation frequency band is expanded under the condition of ensuring that the bearing capacity is not reduced, the vibration isolation performance is improved, and the non-linear behavior can not be generated when the electromagnetic spring and the spiral spring are used under a large amplitude due to good stiffness linearity. In addition, when the quasi-zero stiffness vibration isolator generates low-frequency resonance, the negative stiffness can be set to be 0 by closing the current of the electromagnetic spring, and the quasi-zero stiffness is switched to be higher positive stiffness generated by the spiral spring so as to avoid the low-frequency resonance, so that the vibration isolation performance of the vibration isolator is further improved. In addition, the quasi-zero stiffness vibration isolator can change the position of the spring through the spring fixing ring and the fine tuning nut so as to adjust the position of the central shaft in the unpowered state, so that when different loads are borne, the middle magnet ring can be adjusted to be in the same axial position with the annular electrified coil, the electromagnetic spring is in a balance position, the vibration isolator is in an ideal working state, the optimal vibration isolation performance can be achieved, and the application range is further expanded.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.
Fig. 1 is a cross-sectional view of a quasi-zero stiffness vibration isolator in accordance with an embodiment of the present invention;
fig. 2 is a schematic diagram of a right-angle cross-sectional structure of the quasi-zero stiffness vibration isolator according to the embodiment of the invention.
Wherein, 1 is a bottom plate, 2 is a spring fixing ring, 3 is a supporting seat, 4 is a second linear bearing, 5 is a second bearing seat, 6 is a coil fixing ring, 7 is a retainer, 8 is a locking nut, 9 is a load, 10 is a fine adjustment nut, 11 is a middle magnet ring, 12 is an annular electrified coil, 13 is an end magnet ring, 14 is a second spring, 15 is a central shaft
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The invention aims to provide a quasi-zero stiffness vibration isolator which can generate linear negative stiffness through an electromagnetic spring, is further connected with common linear positive stiffness in parallel, realizes the quasi-zero stiffness in a longer stroke, can expand an effective vibration isolation frequency band under the condition of ensuring that the bearing capacity is not reduced, can be used under large amplitude without generating nonlinear behavior, can adjust the stiffness of the vibration isolator on line through controlling current, and further improves the vibration isolation performance of the quasi-zero stiffness vibration isolator.
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in further detail below.
Fig. 1 is a schematic structural view of a quasi-zero stiffness vibration isolator according to an embodiment of the present invention, and as shown in fig. 1, the quasi-zero stiffness vibration isolator provided by the present invention includes: the bearing comprises a bottom plate, a spring fixing ring, a second spring, a supporting seat, a second linear bearing, a second bearing seat, a second end magnet ring, a retainer, a middle magnet ring, an annular electrified coil, a first end magnet ring, a coil fixing ring, a first bearing seat, a first linear bearing, a first spring, a fine adjustment nut, a locking nut, a load and a central shaft.
The load is in threaded connection with the load end of the central shaft, and the locking nut sleeved on the central shaft is used for locking, so that the influence of vibration on the stability of the load is avoided.
One end of the central shaft is a load end, the other end of the central shaft is a free end, and a fine adjustment nut, a first spring, an electromagnetic spring, a second spring and a spring fixing ring are sequentially sleeved on the central shaft from the load end to the free end.
The first end magnet ring, the annular energizing coil, the middle magnet ring and the second end magnet ring are sequentially sleeved in the axis direction of the central shaft, the middle magnet ring and the annular energizing coil are coaxial and sleeved outside the annular energizing coil, and the annular energizing coil is fixed on the central shaft through the two coil fixing rings. The middle magnet ring is fixed at the middle position of the inner side of the retainer and is equal to the axial height of the annular energizing coil. The first end magnet ring is fixed in the first bearing seat, the second end magnet ring is fixed in the second bearing seat, the two bearing seats are symmetrically arranged at the two ends of the retainer respectively through bolts, the first end magnet ring and the second end magnet ring are symmetrical relative to the middle magnet ring, the relative positions of the three magnet rings are fixed, and the annular electrified coil can axially move relative to the magnet rings.
The two ends of the supporting seat are fixedly connected with the bottom plate and the second bearing seat through bolts respectively, the supporting seat is of an internal hollow structure, and the free end of the central shaft is inserted into the supporting seat in a hanging mode. The first linear bearing and the second linear bearing are respectively positioned at two ends of the electromagnetic spring, the first linear bearing is fixed on the first bearing seat, and the second linear bearing is fixed on the second bearing seat. The two linear bearings are used for limiting the central shaft to move only in the axial direction.
The bottom plate is used for mounting the provided quasi-zero stiffness vibration isolator on an application base.
First, the second spring generates a positive stiffness, the force of the spring on the central shaft being directed towards an intermediate equilibrium position, i.e. the force of the spring keeps the central shaft in an equilibrium position.
Further, the state that the control current is not conducted after the load is added on the quasi-zero stiffness vibration isolator is used as the non-electrified state of the quasi-zero stiffness vibration isolator, when the central shaft of the quasi-zero stiffness vibration isolator in the non-electrified state is in the balance position, the electromagnetic spring is ensured to be in the balance position, and the quasi-zero stiffness vibration isolator is achieved through roughly adjusting or finely adjusting the spring fixing ring and the fine adjusting nut.
When the annular electrified coil and the middle magnet ring are at the same height, the electromagnetic force borne by the middle annular electrified coil is 0 due to the symmetry of the electromagnetic field. This position is referred to as the equilibrium position of the electromagnetic spring. The mass of the load is then entirely carried by the positive rate springs, i.e. the first and second springs, and the negative rate of the electromagnetic spring does not affect the high carrying capacity of the positive rate springs. At the moment, the quasi-zero stiffness vibration isolator is in an ideal working state, and the ideal working state cannot be changed by changing the current in the annular electrified coil of the electromagnetic spring. When the base drives the bottom plate to vibrate, the annular energizing coil on the central shaft and the peripheral middle magnet ring can generate relative displacement, the annular energizing coil can be subjected to repulsive force of the middle magnet pointing to two sides and attractive force of the two end magnet rings pointing to two ends after being energized, namely, an electromagnetic spring formed by the two end magnet rings, the middle magnet ring and the annular energizing coil makes the annular energizing coil far away from a balance position during energization, and the negative stiffness is represented. The parallel negative stiffness can reduce the comprehensive stiffness of the vibration isolator, thereby expanding the vibration isolation frequency band and improving the vibration isolation performance.
The relative position of the annular energizing coil and the middle magnet ring in the unpowered state is influenced by the rigidity and the position of the first spring and the second spring and the mass of the load. And the position of the spring fixing ring on the central shaft is changed, the position of the spring can be changed, the relative position of the middle magnet ring and the annular electrified coil in the unpowered state is changed, and the fine adjustment nut is rotated to perform accurate fine adjustment on the relative position, so that the quasi-zero stiffness vibration isolator can adjust the electromagnetic spring to a balance position under the condition of loading different loads, the vibration isolator is in an ideal working state, and the optimal vibration isolation performance is achieved. And, will finely tune the nut externally, also made things convenient for the user to adjust.
According to the quasi-zero stiffness vibration isolator provided by the invention, the first end magnet ring, the second end magnet ring, the middle magnet ring and the annular electrified coil form the electromagnetic spring, so that the electromagnetic force generated when the annular electrified coil is electrified is in a linear relation with the relative displacement, namely linear negative stiffness is generated, and the common first spiral spring and the common second spiral spring generate linear positive stiffness. The electromagnetic spring and the spiral spring are arranged into a parallel structure, the quasi-zero stiffness under a long stroke can be realized, so that the effective vibration isolation frequency band is expanded under the condition of not reducing the bearing capacity, and the quasi-zero stiffness has good linearity and can be used under large amplitude without generating nonlinear behavior. In addition, when the quasi-zero stiffness vibration isolator generates low-frequency resonance, the negative stiffness can be cancelled by closing the current under the online control, and the quasi-zero stiffness is switched into higher positive stiffness generated by the spiral spring so as to avoid the low-frequency resonance, thereby further improving the vibration isolation performance of the vibration isolator.
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
The principles and embodiments of the present invention have been described herein using specific examples, which are provided only to help understand the method and the core concept of the present invention; meanwhile, for a person skilled in the art, according to the idea of the present invention, the specific embodiments and the application range may be changed. In view of the above, the present disclosure should not be construed as limiting the invention.
Claims (8)
1. A quasi-zero stiffness vibration isolator comprising: the device comprises a central shaft, a fine adjustment nut, a first spring, an electromagnetic spring, a second spring and a spring fixing ring;
one end of the central shaft is a load end, the other end of the central shaft is a free end, and a fine adjustment nut, a first spring, an electromagnetic spring, a second spring and a spring fixing ring are sequentially sleeved on the central shaft from the load end to the free end;
the electromagnetic spring includes: the electromagnetic ring comprises a first end magnet ring, a middle electromagnetic ring and a second end magnet ring which are sequentially sleeved in the axis direction of the central shaft, wherein the middle electromagnetic ring comprises an annular energizing coil sleeved outside the central shaft and a middle magnet ring sleeved outside the annular energizing coil;
the quasi-zero stiffness vibration isolator further comprises: the device comprises a first bearing seat, a retainer, a second bearing seat, a supporting seat, a bottom plate, a first linear bearing and a second linear bearing; the middle magnet ring is fixed in the retainer; the two bearing blocks are symmetrically arranged at the two ends of the retainer respectively through bolts; the first end magnet ring is fixed in the first bearing seat, and the second end magnet ring is fixed in the second bearing seat; the first and second end magnet rings are symmetrically disposed about the middle magnet ring; two ends of the supporting seat are fixedly connected with the bottom plate and the second bearing seat through bolts respectively; the supporting seat is of an internal hollow structure, and the free end of the central shaft is inserted into the supporting seat in a hanging manner; the first linear bearing and the second linear bearing are respectively arranged at two ends of the electromagnetic spring, the first linear bearing is fixed on the first bearing seat, and the second linear bearing is fixed on the second bearing seat.
2. The quasi-zero stiffness vibration isolator of claim 1 wherein the axial heights of the intermediate magnet ring and the annular electrical coil are equal.
3. The quasi-zero stiffness vibration isolator of claim 1 further comprising: a load and lock nut; the locking nut is screwed into the thread section of the load end of the central shaft and is used for locking the load.
4. The quasi-zero stiffness vibration isolator of claim 1 further comprising: two coil fixing rings for fixing the annular energizing coil to the central shaft.
5. The quasi-zero stiffness vibration isolator of claim 1 wherein the first and second springs are both coil springs.
6. The quasi-zero stiffness vibration isolator of claim 1 wherein the load is threadably connected to the load end of the central shaft.
7. The quasi-zero stiffness vibration isolator of claim 1 wherein the base plate is used to mount the quasi-zero stiffness vibration isolator to an application foundation.
8. The quasi-zero stiffness vibration isolator of claim 1 wherein the spring retainer ring and the trim nut are each operable to adjust the particular position of the electromagnetic spring and the first and second springs.
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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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| CN201811608877.3A CN109681573B (en) | 2018-12-27 | 2018-12-27 | Quasi-zero stiffness vibration isolator |
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| CN109681573A CN109681573A (en) | 2019-04-26 |
| CN109681573B true CN109681573B (en) | 2020-02-14 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110671459B (en) * | 2019-09-23 | 2020-06-26 | 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 |
| CN110645310B (en) * | 2019-09-23 | 2020-10-16 | 重庆大学 | Piezoelectric self-powered electromagnetic negative stiffness vibration isolation system and control method thereof |
| 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 |
| CN111075873B (en) * | 2020-01-07 | 2021-04-23 | 长沙理工大学 | Load-variable ultralow frequency vibration isolator and design method thereof |
| CN112709781B (en) * | 2020-12-31 | 2021-11-09 | 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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| 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 |
| CN104455181B (en) * | 2014-10-27 | 2016-05-25 | 西安交通大学 | A kind of accurate zero stiffness vibration isolator that adopts annular permanent magnet to produce negative stiffness |
| CN108591360A (en) * | 2018-04-24 | 2018-09-28 | 上海大学 | A kind of stiffness-adjustable electromagnetism isolation mounting |
| CN108547896B (en) * | 2018-06-15 | 2019-11-26 | 郑州大学 | A kind of electromagnetic spring intelligent vibration damper |
| CN108571559B (en) * | 2018-07-25 | 2019-06-04 | 上海大学 | A kind of damper means of stiffness variable adaptive damping |
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