CN111219443B - Quasi-zero stiffness vibration isolator based on magnetorheological elastomer - Google Patents

Quasi-zero stiffness vibration isolator based on magnetorheological elastomer Download PDF

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Publication number
CN111219443B
CN111219443B CN202010170122.0A CN202010170122A CN111219443B CN 111219443 B CN111219443 B CN 111219443B CN 202010170122 A CN202010170122 A CN 202010170122A CN 111219443 B CN111219443 B CN 111219443B
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magnetorheological elastomer
excitation
vibration isolation
vibration
isolation mechanism
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CN111219443A (en
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白先旭
王经常
陈根
王金桥
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Chery New Energy Automobile Co Ltd
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Chery New Energy Automobile Co Ltd
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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
    • F16F15/08—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with rubber springs ; with springs made of rubber and metal
    • F16F15/085—Use of both rubber and metal springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/002—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion characterised by the control method or circuitry
    • 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
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/3605—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by their material
    • F16F1/361—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by their material comprising magneto-rheological elastomers [MR]
    • 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
    • F16F2224/00—Materials; Material properties
    • F16F2224/02—Materials; Material properties solids
    • F16F2224/025—Elastomers
    • 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
    • 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
    • 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
    • F16F2230/0011—Balancing, e.g. counterbalancing to produce static balance
    • 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
    • F16F2230/08—Sensor arrangement
    • 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
    • F16F2238/022—Springs leaf-like, e.g. of thin, planar-like metal

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

The invention discloses a quasi-zero stiffness vibration isolator based on a magnetorheological elastomer, which consists of a magnetorheological elastomer assembly, a disc spring, a current source, an acceleration sensor, a controller and a vibration isolator base, wherein the disc spring is arranged on the magnetorheological elastomer assembly; the magnetorheological elastomer assembly comprises an excitation coil, a magnetorheological elastomer base, a cylindrical excitation carrier and an outer cylinder body, wherein the left end of the assembly is connected with the vibration isolation mechanism through a flexible plate, and the right end of the assembly is connected with a third fixing table through a fixing bolt to provide horizontal force; the upper end of the disk spring is connected with the vertical direction of the vibration isolation mechanism through a connecting bolt, and the lower end of the disk spring is connected with the base through a disk spring supporting table to provide vertical supporting force. The invention can realize high static rigidity and low dynamic rigidity near the balance position of the vibration isolation mechanism, and has high response speed and wide variation range.

Description

Quasi-zero stiffness vibration isolator based on magnetorheological elastomer
Technical Field
The invention relates to a dynamic negative stiffness adjustment quasi-zero stiffness vibration isolator, in particular to a quasi-zero stiffness vibration isolator based on a magnetorheological elastomer.
Background
Vibration is common in all areas of engineering applications, but under most precision instrument operating conditions, vibration is a harmful condition to avoid. For example, excessive vibration can impair the functioning of the device, increasing the rate of ageing of the instrument, and thus leading to a reduction in the life cycle thereof. With the continuous development of the vibration isolation technology, the current vibration isolation problem of higher frequency is better solved, but under the classic linear vibration isolation theory, a classic vibration isolation system such as a double-layer vibration isolator cannot play an effective vibration isolation effect when the vibration frequency is equal to or less than the resonance frequency of the system, so that the low-frequency vibration isolation is still the problem to be solved by the engineering technology. The wide application of vibration isolation technology in high precision engineering technology requires the adoption of a small resonant frequency system to isolate the wide frequency signal of the external environment.
The quasi-zero stiffness vibration isolation technology is an emerging representative low-frequency vibration isolation technology. The basic idea is as follows: the combination of positive and negative rigidity is utilized to obtain high static rigidity and low dynamic rigidity. The combined stiffness area of the quasi-zero stiffness vibration isolator at the balance position is zero, and the static stiffness of the system is not reduced, so that the system has the characteristics of high static stiffness and low dynamic stiffness under small amplitude vibration, and belongs to the category of nonlinear vibration isolators. The high static rigidity enables the static deformation of the system to be small; the low dynamic stiffness can reduce the natural frequency of the system, thereby expanding the vibration isolation interval; therefore, the system has the vibration isolation advantage of the soft spring and has smaller natural frequency, and the contradiction between the static displacement and the vibration isolation effect is balanced. At present, a large number of negative stiffness structures exist in reality, and the dynamic stiffness of the system is far less than the static stiffness of the system through the device. However, in many quasi-zero stiffness vibration isolation mechanisms, stiffness cannot be adjusted or the adjustment reaction speed is too slow, and the adjustment range is too small, so that the expected vibration isolation effect cannot be achieved.
Disclosure of Invention
The invention aims to overcome the defects in the prior art, and provides a quasi-zero stiffness vibration isolator based on a magnetorheological elastomer, so that the aims of high stiffness adjusting speed and wide stiffness change range of the quasi-zero stiffness vibration isolator can be fulfilled.
The invention adopts the following technical scheme for solving the technical problems:
the invention relates to a quasi-zero stiffness vibration isolator based on a magnetorheological elastomer, which is characterized in that a first fixing table, a second fixing table and a third fixing table are sequentially fixed on a vibration isolator base;
two layers of flexible plates are arranged between the first fixing table and the second fixing table; a vibration isolation mechanism is arranged between the two layers of flexible plates through a connecting bolt; an acceleration sensor is arranged on one side of the vibration isolation mechanism;
a disc spring support table is arranged below the two layers of flexible plates and on the vibration isolator base; a disc spring is arranged on the disc spring support platform; the disc spring is abutted against the tail end of the connecting bolt and provides vertical supporting force for the vibration isolation mechanism;
a connecting key plate penetrates through the second fixing table and is of a slidable structure in the second fixing table; one end of the connecting key plate is fixed between the two layers of flexible plates, and the other end of the connecting key plate is fixedly connected with one end of the magnetorheological elastomer assembly; the other end of the magnetorheological elastomer assembly is fixedly connected to the side face of the third fixing table.
The quasi-zero stiffness vibration isolator is also characterized in that:
the magnetorheological elastomer assembly is characterized in that an excitation outer cylinder body is coaxially assembled on a magnetorheological elastomer base; two cylindrical excitation carriers are coaxially arranged in the excitation outer cylinder body; a magnetorheological elastomer is arranged between the two cylindrical excitation carriers, and a gap is reserved between the two cylindrical excitation carriers; the excitation coils are wound on the grooves of the two cylindrical excitation carriers and do not exceed the depth of the grooves;
a magnetorheological elastic connector is arranged on the top of the cylindrical excitation carrier and penetrates through the excitation outer cylinder body; the magnetorheological elastic connector is connected with the connecting key plate;
the acceleration sensor acquires a vibration signal of the vibration isolation mechanism and transmits the vibration signal to the controller; the controller controls the current source to provide opposite output currents to the excitation coils on the two cylindrical excitation carriers, so that the cylindrical excitation carriers and the excitation outer cylinder body form a closed magnetic conduction loop; the rigidity of the magnetorheological elastomer is correspondingly changed under the action of a magnetic field, and the changed rigidity of the magnetorheological elastomer assembly is synchronously transmitted to the two layers of flexible plates through the connecting key plate, so that the changed rigidity acts on the vibration isolation mechanism.
Compared with the prior art, the invention has the beneficial effects that:
1. the magneto-rheological elastomer used in the invention is a rigidity-adjustable mechanism, the controller receives a signal of the acceleration sensor, controls the current output by the current source to the excitation coil, and changes the rigidity of the magneto-rheological elastomer by changing the excitation current introduced into the coil, so that the system has higher static rigidity and lower dynamic rigidity near a balance position, the contradiction between static displacement and vibration isolation effect is balanced, and the problem of low-frequency vibration isolation in engineering technology which cannot be solved by a classical linear vibration isolation theory is solved.
2. The magneto-rheological elastomer used in the invention has the advantages of wide stiffness adjusting range and sensitive stiffness adjusting speed based on the capability of quick response of the magneto-rheological fluid, and realizes large expansion and high sensitivity of stiffness adjustment.
3. The implementation method of the invention is relatively simple, has small volume and low cost, and is more beneficial to engineering application.
Drawings
FIG. 1 is a schematic diagram of a quasi-zero stiffness actuator of a magnetorheological elastomer of the present invention;
FIG. 2 is a diagram of a magnetorheological elastomer quasi-zero stiffness actuator prototype of the present invention;
FIG. 3 is a top view of the belleville springs of the magnetorheological elastomer quasi-zero stiffness vibration isolator of the present invention;
FIG. 4 is a schematic view of a magnetorheological elastomer assembly according to the present invention;
reference numbers in the figures: the device comprises a first fixing table 1, a flexible plate 2, a connecting bolt 3, a second fixing table 4, a connecting key plate 5, a magnetorheological elastomer assembly 6, a third fixing table 7, a vibration isolation mechanism 8, a disk spring 9, a disk spring supporting table 10, an acceleration sensor 11, a fixing bolt 12, a vibration isolator base 13, a current source 14, a controller 15, a magnetorheological elastic connecting head 16, a magnet exciting coil 17, a magnetorheological elastomer 18, a magnetorheological elastomer base 19, a cylindrical excitation carrier 20 and an outer cylinder body 21.
Detailed Description
In the embodiment, as shown in fig. 2, a quasi-zero stiffness vibration isolator based on a magnetorheological elastomer is characterized in that a first fixed table 1, a second fixed table 4 and a third fixed table 7 are sequentially fixed on a vibration isolator base 13;
two layers of flexible plates 2 are arranged between the first fixed table 1 and the second fixed table 4; a vibration isolation mechanism 8 is arranged between the two layers of flexible plates 2 through a connecting bolt 3; an acceleration sensor 11 is provided on one side of the vibration-isolated mechanism 8;
a disc spring support table 10 is arranged below the two layers of flexible plates 2 and on the vibration isolator base 13; a disc spring 9 shown in fig. 3 is provided on the disc spring support base 10; the disc spring 9 is abutted against the tail end of the connecting bolt 3 and provides vertical supporting force for the vibration isolation mechanism 8;
a connecting key plate 5 penetrates through the second fixed table 4, and the connecting key plate 5 is of a slidable structure in the second fixed table 4; one end of the connecting key plate 5 is fixed between the two layers of flexible plates 2, and the other end of the connecting key plate is fixedly connected with one end of the magnetorheological elastomer assembly 6; the other end of the magnetorheological elastomer assembly 6 is fixedly connected with the side part of the third fixing table 7.
As shown in fig. 4, the magnetorheological elastomer assembly 6 is coaxially assembled with an excitation external cylinder 21 on the magnetorheological elastomer base 19; two cylindrical excitation carriers 20 are coaxially arranged in the excitation external cylinder 21; a magnetorheological elastomer 18 is arranged between the two cylindrical excitation carriers 20, and a gap is reserved between the two cylindrical excitation carriers 20; the excitation coils 17 are wound on the grooves of the two cylindrical excitation carriers 20, and the depth of the coil windings does not exceed the depth of the grooves;
a magnetorheological elastic connector 16 is arranged on the top of the cylindrical excitation carrier 20 and penetrates through the excitation external cylinder 21; the magnetorheological elastic connector 16 is connected with the connecting key plate 5;
the acceleration sensor 11 acquires a vibration signal of the vibration isolation mechanism 8 and transmits the vibration signal to the controller 15; the controller 15 controls the current source 14 to provide opposite output currents to the excitation coils 17 on the two cylindrical excitation carriers 20, so that the cylindrical excitation carriers 20 and the excitation external cylinder 21 form a closed magnetic conduction loop; the rigidity of the magnetorheological elastomer 18 is correspondingly changed under the action of a magnetic field, and the changed rigidity of the magnetorheological elastomer assembly 6 is synchronously transmitted to the two layers of flexible plates 2 through the connecting key plate 5, so that the changed rigidity acts on the vibration isolation mechanism 8.
In this embodiment, as shown in fig. 1, k is a schematic diagram of a quasi-zero stiffness vibration isolator1Is the equivalent spring rate, k, of the disk spring 92Is the equivalent stiffness of the magnetorheological elastomer assembly 6. When no vibration excitation is input, the vibration isolation mechanism 8 is in a balanced state under the combined action of the belleville spring 9 and the slave magnetorheological elastomer 6; when vibration excitation input is available, when the vibration isolation mechanism 8 is located below the balance position, the butterfly spring 9 provides upward supporting force to be increased, the controller 15 reduces power supply current of the magnetorheological elastomer assembly 6, and upward pulling force provided by the magnetorheological elastomer assembly 6 is reducedThe external force applied by the vibration isolation mechanism 8 is not changed; when the vibration isolation mechanism 8 is positioned above the balance position, the upward supporting force provided by the belleville spring 9 is reduced, the power supply current of the magnetorheological elastomer assembly 6 is increased by the controller 15, the upward pulling force provided by the magnetorheological elastomer assembly 6 is increased, and the external force borne by the vibration isolation mechanism 8 is unchanged; therefore, the rigidity of the magnetorheological elastomer assembly 6 is changed, so that the vibration isolation mechanism 8 has high static rigidity and low dynamic rigidity near the balance position.

Claims (2)

1. A quasi-zero stiffness vibration isolator based on a magnetorheological elastomer is characterized in that a first fixing table (1), a second fixing table (4) and a third fixing table (7) are sequentially fixed on a vibration isolator base (13);
two layers of flexible plates (2) are arranged between the first fixed table (1) and the second fixed table (4); a vibration isolation mechanism (8) is arranged between the two layers of flexible plates (2) through a connecting bolt (3); an acceleration sensor (11) is arranged on one side of the vibration isolation mechanism (8);
a disc spring support table (10) is arranged below the two layers of flexible plates (2) and on the vibration isolator base (13); a disc spring (9) is arranged on the disc spring support platform (10); the disc spring (9) is abutted against the tail end of the connecting bolt (3) and provides vertical supporting force for the vibration isolation mechanism (8);
a connecting key plate (5) penetrates through the second fixing table (4), and the connecting key plate (5) is of a slidable structure in the second fixing table (4); one end of the connecting key plate (5) is fixed between the two layers of flexible plates (2), and the other end of the connecting key plate is fixedly connected with one end of the magnetorheological elastomer assembly (6); the other end of the magnetorheological elastomer assembly (6) is fixedly connected with the side surface of the third fixing table (7).
2. The quasi-zero stiffness vibration isolator of claim 1 wherein:
the magnetorheological elastomer assembly (6) is characterized in that an excitation outer cylinder body (21) is coaxially assembled on a magnetorheological elastomer base (19); two cylindrical excitation carriers (20) are coaxially arranged in the excitation external cylinder body (21); a magnetorheological elastomer (18) is arranged between the two cylindrical excitation carriers (20), and a gap is reserved between the two cylindrical excitation carriers (20); the excitation coils (17) are wound on the grooves of the two cylindrical excitation carriers (20) and do not exceed the depth of the grooves;
a magnetorheological elastic connector (16) is arranged on the top of the cylindrical excitation carrier (20) and penetrates through the excitation external cylinder body (21); the magnetorheological elastic connector (16) is connected with the connecting key plate (5);
the acceleration sensor (11) acquires a vibration signal of the vibration isolation mechanism (8) and transmits the vibration signal to the controller (15); the controller (15) controls the current source (14) to provide opposite output currents to the exciting coils (17) on the two cylindrical exciting carriers (20), so that the cylindrical exciting carriers (20) and the exciting outer cylinder body (21) form a closed magnetic conduction loop; the rigidity of the magnetorheological elastomer (18) is correspondingly changed under the action of a magnetic field, and the changed rigidity of the magnetorheological elastomer assembly (6) is synchronously transmitted to the two layers of flexible plates (2) through the connecting key plate (5), so that the changed rigidity acts on the vibration isolation mechanism (8).
CN202010170122.0A 2020-03-12 2020-03-12 Quasi-zero stiffness vibration isolator based on magnetorheological elastomer Active CN111219443B (en)

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Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103363010B (en) * 2013-08-01 2015-02-25 湖南大学 Buckling plate type quasi-zero stiffness vibration isolator
CN108980246B (en) * 2018-09-10 2019-12-27 东北大学 Vibration isolator based on quasi-zero rigidity
KR102073385B1 (en) * 2018-09-21 2020-02-04 인하대학교 산학협력단 Vibration isolation bush for vehicle suspension using multi-layer coil srructured core member and magneto-rheological elastomer
CN109578483A (en) * 2018-12-07 2019-04-05 沈阳远大装备科技有限公司 Quasi- zero stiffness isolation mounting
CN109540493B (en) * 2018-12-21 2019-10-25 东北大学 A kind of experimental rig of quasi-zero stiffness vibration isolators

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