CN113153963A - Quasi-zero stiffness vibration isolator containing nonlinear damping - Google Patents
Quasi-zero stiffness vibration isolator containing nonlinear damping Download PDFInfo
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- CN113153963A CN113153963A CN202110182160.2A CN202110182160A CN113153963A CN 113153963 A CN113153963 A CN 113153963A CN 202110182160 A CN202110182160 A CN 202110182160A CN 113153963 A CN113153963 A CN 113153963A
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- vibration isolator
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- zero
- beam spring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/022—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using dampers and springs in combination
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—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
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
- F16F2228/063—Negative 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
- F16F2230/00—Purpose; Design features
- F16F2230/0005—Attachment, e.g. to facilitate mounting onto confer adjustability
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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
- F16F2238/00—Type of springs or dampers
- F16F2238/02—Springs
- F16F2238/026—Springs wound- or coil-like
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- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention discloses a quasi-zero stiffness vibration isolator containing horizontal damping, which is formed by using a cam-roller-beam spring as a negative stiffness mechanism, adding a horizontal damper in the middle of the beam spring and then connecting the horizontal damper and a vertical spring in parallel. The negative stiffness mechanism plays a role in offsetting the positive stiffness of the vertical spring, so that the inherent frequency of the vibration isolator is reduced to be close to zero, low-frequency vibration isolation is realized, and the horizontal damping force greatly weakens the transmission rate formant. After matlab numerical simulation, the vibration isolator has a lower transmission rate peak value compared with the traditional nonlinear vibration isolator, and has lower vibration isolation frequency than the linear vibration isolator, which is equivalent to overcoming the defect of large transmission rate peak value of the traditional nonlinear vibration isolator and the defect of high vibration isolation frequency of the linear vibration isolator. In conclusion, the vibration isolator has good low-frequency vibration isolation performance.
Description
Technical Field
The invention designs a quasi-zero stiffness vibration isolator used in the field of low-frequency vibration attenuation, which can be used for precision instruments, spacecrafts and other equipment needing low-frequency vibration attenuation.
Background
In most engineering equipment, vibration becomes an important factor that impairs the life of the mechanical equipment. Therefore, the vibration isolation technique is known as a hot field of research. Compared with active control, the passive vibration isolation technology has the advantages of no need of external power supply equipment and nodeSimple structure, low price and the like. The requirements for low frequency vibration isolators appear in many scientific and industrial fields, ranging from vibration isolation of precision instruments for gravitational wave detection to the design of motor seat suspensions, and vibration isolation of lightweight robots. For a traditional linear vibration isolator, the vibration isolation range can only be that the excitation frequency is greater than the natural frequency
Doubling can only be realized.
If the vibration isolation range needs to be widened, the stiffness of the vibration isolator needs to be reduced to achieve a small natural frequency, but this results in a large static displacement. There is then a trade-off between the vibration isolation performance and static deflection of the linear vibration isolator. If the vibration isolator needs to obtain large static rigidity and can reduce the vibration inherent frequency of the vibration isolator, only a negative rigidity mechanism is connected in parallel on the basis of the original linear vibration isolator to introduce rigidity nonlinearity, so that the dynamic rigidity of the vibration isolator system is reduced, the static rigidity still keeps the original level, and the vibration isolator is called as a high static low dynamic vibration isolator. When the balance position reaches zero rigidity, the vibration isolator is called as a quasi-zero rigidity vibration isolator. The cam-roller design concept is preferably utilized by the Zhou of university in Hunan to realize the quasi-zero stiffness design of the vibration isolation system. It was found that the peak transmissivity and isolation frequency of the isolator never exceeded the peak transmissivity and isolation frequency of the linear isolator, regardless of the excitation amplitude. It can only reduce the system formants by adjusting the vertical damping. Dong et al propose a new design of geometric nonlinear damping composed of semi-active electromagnetic parallel damping in order to improve the low frequency vibration isolation performance of high static and low dynamic vibration isolators. However, the need for active control elements increases the design difficulty and cost of the isolator.
Disclosure of Invention
The invention aims to provide a quasi-zero stiffness vibration isolator which uses a cam-roller-beam spring as a negative stiffness mechanism, adds a horizontal damper in the middle of the beam spring and is connected with a vertical spring in parallel, aiming at the defects that a linear vibration isolator has poor vibration isolation performance in the aspect of low frequency, and the traditional nonlinear vibration isolator only has vertical damping has higher transmission peak value and the like. The vibration isolator has the characteristics of good low-frequency vibration isolation performance, low peak value transmission rate and the like, and after matlab numerical simulation, the vibration isolator can be known to have a lower transmission rate peak value compared with the traditional nonlinear vibration isolator, and the vibration isolator can bear wider load due to the adjustability of the vertical spring.
The invention adopts the following technical scheme:
a quasi-zero stiffness vibration isolator containing horizontal damping mainly comprises an upper bearing platform with an annular cam, a lower base with a hollow pillar, a vertical spring, a beam spring, a fixed support and a damper;
the concrete structure and the connection mode are as follows:
go up plummer central part and stretched out a big hollow cylinder, hollow cylinder's bottom has a radius to be 12 cm's semicircle annular cam, has four pillars top to have the screw thread simultaneously in four corners in the below of plummer.
The negative stiffness mechanism comprises four beam springs which are symmetrically arranged, a rolling ball is arranged in the middle of each beam spring, the other end of the middle of each beam spring is connected with one end of a damper, and the beam springs are fixed with the fixed support through screws. The other end of the damper is connected with the fixed supports, and all the fixed supports are respectively connected with the lower base platform through bolts.
Four hollow pillars extend out of four symmetrical corners of the lower base platform, the hollow pillars are matched with pillars of the upper bearing platform, linear springs are surrounded around the hollow pillars, the tops of the linear springs are in contact with the annular regulators, the annular regulators are in threaded connection with the pillars of the upper bearing platform, and the compression amount of the linear springs can be regulated by screwing the annular regulators.
Compared with the prior art, the quasi-zero stiffness vibration isolator has the following advantages:
the quasi-zero stiffness vibration isolator adopts a passive control scheme, and is low in energy consumption and cost. And the quasi-zero rigidity can be realized by screwing the position of the adjuster to enable the vibration isolator to bear loads with different weights. In addition, the additional horizontal damper can better inhibit a resonance peak when the quasi-zero stiffness vibration isolator works, and better vibration isolation performance than that of the traditional quasi-zero stiffness vibration isolator is achieved.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
fig. 1 is a schematic structural diagram of the quasi-zero stiffness vibration isolator according to the invention;
FIG. 2 is a structural oblique view of the quasi-zero stiffness vibration isolator according to the invention;
FIG. 3 is a diagram of a beam spring according to the present invention;
FIG. 4 is a perspective view of the support member of the present invention;
labeled as: 1-upper load-bearing platform, 2-ring adjuster, 3-vertical mechanical spring, 4-threaded strut, 5-support, 6-hollow strut, 7-bolt, 8-lower base, 9-beam spring, 10-large hollow strut, 11-semi-circular ring cam, 12-ball, 13-ball loading piece, 14-screw, 15-damper.
Detailed Description
The technical scheme of the invention is further described by combining the drawings and the embodiment:
as shown in fig. 1 to 4, the quasi-zero stiffness vibration isolator mainly comprises an upper bearing platform (1), a linear spring (3), a pillar with a cam (10), a beam with a ball (9) and a damper (15).
Go up plummer (1) central part and stretched out a big hollow cylinder (6), hollow cylinder's bottom has a radius to be 12 cm's semicircle annular cam (11), has four pillars (4) simultaneously in four corners in the below of plummer, and the pillar top has the screw thread.
The negative stiffness mechanism comprises a beam spring (9) and a ball (12) arranged in the middle of the beam spring (9), the beam spring (9) is fixedly connected with the supporting piece (5) through a screw, and the other end of the center of the beam spring (9) is connected with the damper (15). The supporting piece (5) is connected with the lower base (8) through bolts, and the four groups of negative stiffness mechanisms are symmetrically distributed at 90 degrees.
The lower base (8) comprises four hollow struts (6), linear springs (3) are wound outside the hollow struts (6), the upper ends of the linear springs (3) are in contact with the annular regulator (2), and the annular regulator (2) is internally threaded so that the linear springs can move up and down on the struts (4) of the upper bearing platform (1) to regulate the compression amount of the linear spiral springs.
Principle and process of operation
When the vibration isolator bears load M, the vertical spring is compressed to a proper position by adjusting the annular regulator, and the cam and the center of the rolling ball are on the same straight line, namely a quasi-zero rigidity static balance position. When the vibration isolator is excited by vertical downward force f ═ f0cos (ω t), the roller moves back and forth along the cam profile, the beam is continuously compressed, the damper also continuously moves back and forth, and the horizontal force generated by the beam and the damper is transmitted to the large circular pillar of the upper bearing table through the contact between the rolling ball and the cam, so that the vertical force is generated. Because the four groups of negative stiffness mechanisms are symmetrically arranged, the force in the vertical direction is formed by mutually superposing the forces of the four groups of negative stiffness mechanisms. The negative stiffness mechanism plays a role in offsetting the positive stiffness of the vertical spring, so that the inherent frequency of the vibration isolator is reduced to be close to zero, low-frequency vibration isolation is realized, and the horizontal damping force greatly weakens the transmission rate formant. Thereby achieving excellent low-frequency vibration isolation effect.
Claims (4)
1. The utility model provides a quasi-zero rigidity isolator that contains nonlinear damping which characterized in that: by last plummer (1) of taking the cam, take hollow pillar's lower base, vertical spring, burden rigidity mechanism, fixing support and attenuator to constitute:
a hollow cylinder (6) extends out of the center of the upper bearing table (1), a semicircular annular cam (11) is arranged at the bottom end of the hollow cylinder (6), four pillars (4) are arranged at four corners below the upper bearing table (1), and threads are arranged above the pillars (4);
the negative stiffness mechanism comprises a beam spring (9), a ball (12) is arranged in the middle of the beam spring (9), the beam spring (9) is fixedly connected with the support piece (5) through a screw, and the other end of the center of the beam spring (9) is connected with the damper (15); the supporting piece (5) is connected with the lower base (8) through bolts, and the four groups of negative stiffness mechanisms are symmetrically distributed at 90 degrees;
the lower base (8) comprises four hollow struts (6), linear springs (3) are wound outside the hollow struts (6), the upper ends of the linear springs (3) are in contact with the annular regulator (2), and the annular regulator (2) is internally threaded to enable the annular regulator to move up and down on the struts (4) of the upper bearing platform (1) to regulate the compression amount of the linear spiral springs.
2. The quasi-zero stiffness vibration isolator with nonlinear damping of claim 1 wherein: the negative stiffness mechanisms are symmetrically arranged at a 90 degree distance from each other.
3. The quasi-zero stiffness vibration isolator with nonlinear damping of claim 1 wherein: the annular regulator is connected with the upper end pillar through threads, and the compression amount of the vertical spiral spring is adjusted.
4. The quasi-zero stiffness vibration isolator with horizontal damping of claim 1 wherein: the damper is horizontally arranged and is positioned in the center of the beam spring, and the compression amount of the beam spring is the damping movement amount.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110182160.2A CN113153963A (en) | 2021-02-09 | 2021-02-09 | Quasi-zero stiffness vibration isolator containing nonlinear damping |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202110182160.2A CN113153963A (en) | 2021-02-09 | 2021-02-09 | Quasi-zero stiffness vibration isolator containing nonlinear damping |
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| CN113153963A true CN113153963A (en) | 2021-07-23 |
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| CN202110182160.2A Pending CN113153963A (en) | 2021-02-09 | 2021-02-09 | Quasi-zero stiffness vibration isolator containing nonlinear damping |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
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| CN203641365U (en) * | 2014-01-07 | 2014-06-11 | 湖南大学 | Quasi zero stiffness vibration isolator |
| CN205780563U (en) * | 2016-05-23 | 2016-12-07 | 福州大学 | Drawing quasi-zero stiffness vibration isolators |
| CN107740843A (en) * | 2017-11-17 | 2018-02-27 | 北京市劳动保护科学研究所 | A kind of cam bawl negative stiffness structure low frequency vibration isolation device |
| US20190186587A1 (en) * | 2017-12-14 | 2019-06-20 | Toyoto Motor Engineering & Manufacturing North America, Inc. | Vibration isolator mechanism with adjustable force application mechanism |
| CN109973571A (en) * | 2017-12-28 | 2019-07-05 | 北京市劳动保护科学研究所 | A kind of quasi-zero stiffness vibration isolators with horizontal damping |
| CN110107632A (en) * | 2019-06-03 | 2019-08-09 | 江南大学 | A kind of positive and negative Stiffness low frequency vibration isolation device coupling dynamic vibration absorber |
| CN210034259U (en) * | 2019-05-10 | 2020-02-07 | 北京工业大学 | Quasi-zero stiffness low-frequency vibration isolator with piezoelectric energy harvesting function |
| CN111216607A (en) * | 2019-12-31 | 2020-06-02 | 北京市劳动保护科学研究所 | Seat with low-frequency vibration isolation and energy harvesting coupling |
| WO2020151617A1 (en) * | 2019-01-25 | 2020-07-30 | 石家庄铁道大学 | Negative rigidity shock reduction and isolation device for continuous beam |
| CN111927912A (en) * | 2020-07-15 | 2020-11-13 | 江苏大学 | Quasi-zero rigidity vertical vibration isolator capable of realizing balance position adjustment |
-
2021
- 2021-02-09 CN CN202110182160.2A patent/CN113153963A/en active Pending
Patent Citations (10)
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|---|---|---|---|---|
| CN203641365U (en) * | 2014-01-07 | 2014-06-11 | 湖南大学 | Quasi zero stiffness vibration isolator |
| CN205780563U (en) * | 2016-05-23 | 2016-12-07 | 福州大学 | Drawing quasi-zero stiffness vibration isolators |
| CN107740843A (en) * | 2017-11-17 | 2018-02-27 | 北京市劳动保护科学研究所 | A kind of cam bawl negative stiffness structure low frequency vibration isolation device |
| US20190186587A1 (en) * | 2017-12-14 | 2019-06-20 | Toyoto Motor Engineering & Manufacturing North America, Inc. | Vibration isolator mechanism with adjustable force application mechanism |
| CN109973571A (en) * | 2017-12-28 | 2019-07-05 | 北京市劳动保护科学研究所 | A kind of quasi-zero stiffness vibration isolators with horizontal damping |
| WO2020151617A1 (en) * | 2019-01-25 | 2020-07-30 | 石家庄铁道大学 | Negative rigidity shock reduction and isolation device for continuous beam |
| CN210034259U (en) * | 2019-05-10 | 2020-02-07 | 北京工业大学 | Quasi-zero stiffness low-frequency vibration isolator with piezoelectric energy harvesting function |
| CN110107632A (en) * | 2019-06-03 | 2019-08-09 | 江南大学 | A kind of positive and negative Stiffness low frequency vibration isolation device coupling dynamic vibration absorber |
| CN111216607A (en) * | 2019-12-31 | 2020-06-02 | 北京市劳动保护科学研究所 | Seat with low-frequency vibration isolation and energy harvesting coupling |
| CN111927912A (en) * | 2020-07-15 | 2020-11-13 | 江苏大学 | Quasi-zero rigidity vertical vibration isolator capable of realizing balance position adjustment |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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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