CN2842078Y - Magnetic rheological elastomer frequency shift attenuator - Google Patents
Magnetic rheological elastomer frequency shift attenuator Download PDFInfo
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- CN2842078Y CN2842078Y CN 200520076452 CN200520076452U CN2842078Y CN 2842078 Y CN2842078 Y CN 2842078Y CN 200520076452 CN200520076452 CN 200520076452 CN 200520076452 U CN200520076452 U CN 200520076452U CN 2842078 Y CN2842078 Y CN 2842078Y
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Abstract
The utility model relates to a magnetically rheologic elastic body frequency shift vibration absorber which comprises an executing component, a control component and a sensor. The utility model is characterized in that the executing component is composed of a magnetism conducting piece, a coil, magnetically rheologic elastic bodies, a vibration absorbing quality block and a base, wherein the magnetism conducting piece is composed of an inner sleeve barrel and an outer sleeve barrel or a U-shaped iron core and an armature iron or an upper plate, a lower plate and a columnar iron core, and the magnetically rheologic elastic bodies are filled between the inner sleeve barrel and the outer sleeve barrel, or between the U-shaped iron core and the armature iron or between the upper plate and the lower plate; corresponding voltage of the coil is regulated so as to regulate the rigidity and the elasticity of the magnetically rheologic elastic bodies so that the vibration frequency of the magnetically rheologic elastic bodies are changed until the vibration frequency of the executing component of the vibration absorber is the same with the vibration frequency of a vibration damping object. The utility model has the advantages of good vibration absorption effect, large bandwidth of vibration damping frequency, small quality and volume, simple structure and easy control method, and the utility model can combine and use a plurality of vibration absorbers according to the vibration damping requirements of different frequency bands.
Description
(1) technical field:
The utility model relates to a kind of vibration damping equipment that is applied on machinery and the electric equipment.
(2) background technique:
In machinery and electric equipment in the past, owing to lack effective shock absorption system, cause machinery and electric equipment premature damage or cause noise pollution environment.
Existing vibration control method can be divided into ACTIVE CONTROL, Passive Control, half ACTIVE CONTROL.Passive Control does not have regulating power fully, and its narrow limitation is arranged, the vibration control of only suitable arrowband.ACTIVE CONTROL is better than Passive Control, can carry out active adjustment, is fit to wide-band vibration control.But ACTIVE CONTROL belongs to power control, and the energy of control force need directly be provided, and cost is higher, and technology is complicated.Half ACTIVE CONTROL belongs to parameter control, does not need to provide the energy of control force, and it is the reaction that the parameter that depends on the information real time altering structure of structural vibrations reaction or dynamic load reduces structure.Traditional bump leveller is a kind of main actuator of vibration passive control, has light weight, simple in structure, easy for installation and suppress characteristics such as single-frequency vibration and noise effects are remarkable.But there are a lot of shortcomings in traditional passive type bump leveller, as it is very narrow and non-adjustable to control frequency band, thus can only carry out vibration damping to the steady-state vibration of a fixing excited frequency, when excited frequency departs from a bit a little, effectiveness in vibration suppression is deterioration sharply, even it is poorer to become.To make it become clumsy etc. and increase bandwidth.
The shock-absorbing means of mentioning in the patent of invention of application number 96107066.8 adopts passive bump leveller principle design, because the vibration damping bandwidth is narrower, having only to adopt increases damping or vibration damper weight quality and adopts the mode of a plurality of vibration damping weights to solve, but increase the damping meeting and reduce effectiveness in vibration suppression, the quality and the number that increase the vibration damping weight can make vibration damper clumsy, this in addition method is very limited to the increase of vibration damping bandwidth, generally only has several hertz.A kind of active magnetorheological fluid damp type bump leveller and installation method have been mentioned in addition in the patent of invention of application number 02131043.2, can use linear motor, metal spring and magnetic rheological liquid damper initiatively to change parameters such as system's control force and damping and reach " optimal tuning " purpose, but this controlling method complexity, because need to promote linear motor, can consume more energy, and according to the bump leveller principle, it is not remarkable to the properties influence of bump leveller to change these parameters.
(3) summary of the invention:
The purpose of this utility model is to design a kind of magnetic flowing deformation elastomer frequency shift type attenuator and controlling method, it can be according to the principal oscillation frequency of vibration damping object, according to the controlling method of setting, characteristics such as rigidity by changing magnetic rheology elastic body and damping, automatically regulate the natural frequency of bump leveller self, in wider frequency, reach best shock attenuation result all the time.
The technical solution of the utility model: a kind of magnetic flowing deformation elastomer frequency shift type attenuator, comprise power unit, controlling component and sensor, the power unit that it is characterized in that it is to be made of magnetic conductive part, coil, magnetic rheology elastic body and absorbing mass block, pedestal; Said magnetic conductive part is made of inner sleeve and outer sleeve, and sleeve inner has cavity, a sidewall that opening is arranged, and its longitudinal section is a C shape, and the C shape opening of sidewall seals with annular magnetism resistent ring, positioned coil in the cavity; Inner sleeve and outer sleeve are coaxial to be nested, and the C shape opening of outer sleeve is positioned at madial wall, and the C shape opening of inner sleeve is positioned at outer side wall, and magnetic rheology elastic body in filling between inner and outer sleeves, is fixing the absorbing mass block on the inner sleeve, and pedestal is set on the outer sleeve; The joint of coil and the output terminal of controlling component join.
Above said inside and outside sleeve, coil and magnetic rheology elastic body can be straight-tube shape, also can be the awl tubular.
The alternative structure one of above-mentioned magnetic flowing deformation elastomer frequency shift type attenuator, the power unit that it is characterized in that it is to be made of magnetic conductive part, coil, magnetic rheology elastic body, absorbing mass block and pedestal, wherein magnetic conductive part is to be made of U-iron core and armature, U-iron core bottom is wound with coil, magnetic rheology elastic body in filling between armature and the U-iron core, fixing the absorbing mass block on the armature, on the U-iron core pedestal is being set; The joint of coil and the output terminal of controlling component join.
The alternative structure two of above-mentioned magnetic flowing deformation elastomer frequency shift type attenuator, the power unit that it is characterized in that it is to be made of magnetic conductive part, coil, magnetic rheology elastic body and absorbing mass block, pedestal, said magnetic conductive part is to be made of upper plate, lower plate and columnar iron core, columnar iron core is around with coil, be fixed between upper plate and the lower plate, magnetic rheology elastic body in filling between upper plate and the lower plate, one end of upper plate and lower plate is fixed on the pedestal, the other end is unsettled, constitute overhang, the unsettled end of beam is the absorbing mass block fixedly; The joint of coil and the output terminal of controlling component join.
In sum, the utility model uses elastic element and the damping member of intellectual material magnetic rheology elastic body as bump leveller, and the controlling method of employing shift frequency, form semi-actively controlled bump leveller, by the control voltage on the regulating winding, with regard to can regulate magnetic rheology elastic body rigidity and elasticity, thus the natural frequency of under the situation that does not change structure and size, regulating bump leveller, and the final goal of control is to make the absorbing frequency of bump leveller natural frequency and vibration damping object identical.If the vibration damping object comprises the principal vibration frequency of a plurality of needs controls, can adopt the combination of a plurality of bump levellers, control the vibration of each frequency respectively.Compare with traditional bump leveller, have following remarkable advantage:
1. shock attenuation result is good, under the basicly stable situation of the vibration frequency of vibration damping object, can effectively control the vibration of the various frequencies of low frequency and high frequency;
2. consumed energy is few, as long as the fundamental voltage that changes the bump leveller natural frequency is provided, not needing provides energy to offset vibrational energy;
3. the vibration damping frequency band is roomy, and by regulating the bump leveller natural frequency, the vibration frequency that can follow the tracks of the vibration damping object in relative broad range reaches best effectiveness in vibration suppression all the time;
4. because frequency adjustable is used the vibration damping bandwidth that less absorbing quality also can reach to be needed, so quality and volume are less;
5. simple in structure, controlling method is easy, so the system reliability height;
6. realize modularization easily, be easy to require to be used in combination a plurality of bump levellers according to the vibration damping of different frequency range.
(4) description of drawings
Accompanying drawing 1 is the power unit structural representation of shearing type magnetic flowing deformation elastomer frequency shift type attenuator.
Accompanying drawing 2 is the sectional arrangement drawing of Fig. 1.
Accompanying drawing 3 is the sectional arrangement drawing of the power unit structural representation of shearing-extruding composite magnetic flowing deformation elastomer frequency shift type attenuator.
Accompanying drawing 4 is the power unit structural representation of tension and compression type magnetic flowing deformation elastomer frequency shift type attenuator.
Accompanying drawing 5 is the power unit structural representation of the compound magnetic flowing deformation elastomer frequency shift type attenuator of twist and warping.
Accompanying drawing 6 is a principle schematic of the present utility model.
Wherein: 1. absorbing mass block; 2.U shape iron core, 3. inner sleeve, 4. outer sleeve; 5. coil; 6 magnetism resistent rings; 7 columnar iron cores, 8. magnetic rheology elastic body; 9. armature; 10 upper plates; 11. lower plate; 12. pedestal; 13. bump leveller power unit; 14 vibration damping objects; 15 sensors, 16. charge amplifiers; 17. controller; 18. power amplifier;
m
1, k
1, c
1Be equivalent mass, equivalent stiffness and the equivalent damping of vibration damping object; m
1Last effect has excitation force P
1Sin ω t, x
1Represent its displacement; m
2, k
2, c
2Be equivalent absorbing quality, equivalent stiffness and the equivalent damping of bump leveller, both have represented the characteristic of magnetic rheology elastic body, x the back
2Represent the displacement of absorbing mass block.
(5) embodiment:
Embodiment one: shearing type magnetic flowing deformation elastomer frequency shift type attenuator as shown in Figure 1 and Figure 2, be to constitute by inner sleeve 3 and outer sleeve 4, coil 5, magnetism resistent ring 6, magnetic rheology elastic body 8 and absorbing mass block 1, pedestal 12, sleeve and pedestal are made with electrical pure iron, magnetism resistent ring is made with brass, and the absorbing mass block is also made with brass.Outer sleeve 4 is cylindric, its half of sectional shape is a C shape, C shape opening inwardly, be that sleeve inner has cavity, madial wall has opening, positioned coil 5 just in time in the cavity, the C shape opening of madial wall seals with annular magnetism resistent ring 6, inner sleeve 3 is column or cylindric (being that its place, axle center can have longitudinal hole or not have longitudinal hole), its half of sectional shape also is a C shape, C shape opening outwardly, be that sleeve inner also has cavity, outer side wall has opening, positioned coil 5 just in time in the cavity, the C shape opening of outer side wall are with annular magnetism resistent ring 6 sealings, and the purpose of magnetism resistent ring is to limit the flow direction of the magnetic line of force, its overwhelming majority can only be passed from magnetic rheology elastic body, in, outer sleeve is coaxial to nest together, and magnetic rheology elastic body 8 in filling between inside and outside sleeve, makes magnetic rheology elastic body also form tubular, fixing absorbing mass block 1 with screw thread on the inner sleeve 3, whole bump leveller power unit is fixed to the vibration damping object with screw by the screw on the pedestal of outer sleeve bottom setting.The joint of coil and the output terminal of controlling component join.
Here said inside and outside sleeve, coil and magnetic rheology elastic body can be that (it is operated in shearing condition to above-mentioned straight-tube shape, can eliminate and the consistent straight-line oscillation of vibration damping object direction of vibration), it also can be awl tubular (as shown in Figure 3), the bus and the axis that are cylinder have angle, constitute the bump leveller of shearing-extruding composite.So not only on the direction parallel damping effect being arranged, simultaneously on the direction vertical certain effectiveness in vibration suppression being arranged also with the vibration of vibration damping object with the vibration of vibration damping object.
The design principle of said structure is: the needs according to the vibration damping frequency range of vibration damping object make the natural frequency of bump leveller power unit under no magnetic field than the frequency that needs vibration damping low about 20～50%.If f is the natural frequency of bump leveller power unit under no magnetic field,
Wherein k is that magnetic rheology elastic body does not have the rigidity under the magnetic field, and m is the quality of absorbing mass block.If the cylinder heights of magnetic rheology elastic body is h, thickness is t, girth is L, the elastomer shear modulus is G, k ≈ GLh/t then, the quality m of absorbing mass block is typically chosen in 5%～40% of vibration damping object quality, just can regulate the natural frequency of bump leveller power unit under no magnetic field according to the size that top said formula changes the magnetic rheology elastic body cylinder, makes the natural frequency of bump leveller power unit 13 under no magnetic field than the frequency that needs vibration damping low about 20%～50%.
The bump leveller working procedure is: as shown in Figure 6, the bonding upper sensor 15 of difference on vibration damping object 14 and the bump leveller power unit 13, signal of sensor is sent into controller 17 by charge amplifier 16, obtains the rumble spectrum characteristic of vibration damping object and the rumble spectrum characteristic of bump leveller power unit by fft analysis.Both compare, if the principal oscillation frequency of bump leveller power unit 13 is lower than the vibration frequency of vibration damping object 14, controller 17 provides "+" signal, power controlling amplifier 18 increases output voltage, the input end of the coil 5 (current direction in the coil 5 in the inside and outside sleeve is all identical) in the output terminal of controlling component (being the output terminal of power amplifier in this embodiment) and the bump leveller power unit links to each other, the voltage that increases has strengthened the internal magnetic field of bump leveller power unit 13, the rigidity of magnetic rheology elastic body 8 is increased, improved the natural frequency of bump leveller power unit 13, until identical with the vibration frequency of vibration damping object 14.Otherwise controller 17 provides "-" signal, reduces the voltage of coil 5, and the natural frequency that reduces bump leveller power unit 13 is up to identical with the vibration frequency of vibration damping object 14.
Perhaps natural frequency by measuring bump leveller power unit 13 in advance and the corresponding relation (promptly setting up the database of the pairing voltage of different natural frequencies) between its coil input voltage, as long as measure the principal oscillation frequency natural frequency of bump leveller power unit 13 (and need not to survey again) of vibration damping object during vibration damping, find its corresponding voltage by database, provide this voltage that is fit to and make the principal oscillation frequency of the natural frequency of bump leveller power unit 13 and vibration damping object identical.
The target of control is to make bump leveller power unit 13 identical with the vibration frequency of vibration damping object 14, reaches the purpose of the absorbing of the best.If vibration damping object 14 comprises the principal vibration frequency of a plurality of needs controls, can adopt the mode of a plurality of bump leveller parallel operations, each vibration frequency that need control can be controlled by a bump leveller, controlling the purpose of vibrating fully in the wide band very much thereby reach.
Above-mentioned magnetic rheology elastic body, it is a kind of novel intelligent material, generally be to obtain after elastomer (high molecular polymer such as rubber etc.) also solidifies by can embedding of micron-scale at the solid particle of magnetized soft iron magnetic under the magnetic field, it has many particular performances under the action of a magnetic field, can be controlled by magnetic field as the rigidity (comprising shear modulus and Young's modulus) and the damping of material.Because its particle is fixed in the matrix, there is not the particles settling problem, thereby compare with common magnetic flow liquid, magnetic rheology elastic body not only has controllability, reversibility, the rapid contour technical characteristics of response, unique advantage such as also have good stability, structural design is simple, preparation cost is low.Magnetic rheology elastic body can be buied by the Lord company of the U.S..
Embodiment two: tension and compression type magnetic flowing deformation elastomer frequency shift type attenuator as shown in Figure 4, constitute by U-iron core 2, magnetic rheology elastic body 8, armature 9, absorbing mass block 1, pedestal 12 and coil 5, wherein U-iron core 2 and armature 9 are made for ingot iron, U-iron core bottom is wound with coil 5, top traverse armature 9, armature are strip.Affixed sheet magnetic rheology elastic body 8 between armature 9 and the U-iron core 2, fixing absorbing mass block 1 with screw thread on the armature 9, whole bump leveller power unit 13 can be fixed to the vibration damping object by the screw on the pedestal 12 set below the columnar iron core with screw and get on, and other control mode is with embodiment one.It is operated in the tension and compression state, can eliminate and the consistent straight-line oscillation of vibration damping object direction of vibration.
Embodiment three: the compound magnetic flowing deformation elastomer frequency shift type attenuator of twist and warping as shown in Figure 5, by upper plate 10, lower plate 11, coil 5, columnar iron core 7, magnetic rheology elastic body 8, pedestal 12 and absorbing mass block 1 constitute, upper plate 10, lower plate 11 and columnar iron core 7 are made for ingot iron, pedestal 12 is formed from aluminium, columnar iron core 7 outer coilings 5, columnar iron core 7 is fixed on an end or the middle random position of upper plate 10 and lower plate 11 up and down with screw thread, all the other positions between the two boards affixed again block magnetic rheology elastic body 8, upper plate 10, lower plate 11, magnetic rheology elastic body 8 forms the sandwich beam integral body of a Layer cake dry type and the one end is weldingly fixed on the pedestal, constitute overhang, the other end of overhang is absorbing mass block 1 fixedly, bump leveller operate mainly in bending or the mode reversed under, whole bump leveller power unit 13 can be fixed to the vibration damping object by the screw on the pedestal with screw and get on, and other control mode is with embodiment one.It is operated in and reverses or bent state, can eliminate reversing or flexure vibrations of vibration damping object.
Claims (5)
1, a kind of magnetic flowing deformation elastomer frequency shift type attenuator comprises power unit, controlling component and sensor, it is characterized in that: its power unit is to be made of magnetic conductive part, coil, magnetic rheology elastic body and absorbing mass block, pedestal; Said magnetic conductive part is made of inner sleeve and outer sleeve, and sleeve inner has cavity, a sidewall that opening is arranged, and its longitudinal section is a C shape, and the C shape opening of sidewall seals with annular magnetism resistent ring, positioned coil in the cavity; Inner sleeve and outer sleeve are coaxial to be nested, and the C shape opening of outer sleeve is positioned at madial wall, and the C shape opening of inner sleeve is positioned at outer side wall, and magnetic rheology elastic body in filling between inner and outer sleeves, is fixing the absorbing mass block on the inner sleeve, and pedestal is set on the outer sleeve; The joint of coil and the output terminal of controlling component join.
2, as the said magnetic flowing deformation elastomer frequency shift type attenuator of claim 1, it is characterized in that: inside and outside sleeve, coil and magnetic rheology elastic body are straight-tube shapes.
3, as the said magnetic flowing deformation elastomer frequency shift type attenuator of claim 1, it is characterized in that: inside and outside sleeve, coil and magnetic rheology elastic body are the awl tubulars.
4, a kind of magnetic flowing deformation elastomer frequency shift type attenuator, comprise power unit, controlling component and sensor, it is characterized in that: its power unit is to be made of magnetic conductive part, coil, magnetic rheology elastic body, absorbing mass block and pedestal, wherein magnetic conductive part is to be made of U-iron core and armature, U-iron core bottom is wound with coil, magnetic rheology elastic body in filling between armature and the U-iron core, is fixing the absorbing mass block on the armature, on the U-iron core pedestal is set; The joint of coil and the output terminal of controlling component join.
5, a kind of magnetic flowing deformation elastomer frequency shift type attenuator, comprise power unit, controlling component and sensor, it is characterized in that: its power unit is to be made of magnetic conductive part, coil, magnetic rheology elastic body and absorbing mass block, pedestal, said magnetic conductive part is to be made of upper plate, lower plate and columnar iron core, columnar iron core is around with coil, be fixed between upper plate and the lower plate, magnetic rheology elastic body in filling between upper plate and the lower plate, one end of upper plate and lower plate is fixed on the pedestal, the other end is unsettled, constitute overhang, the unsettled end of beam is the absorbing mass block fixedly; The joint of coil and the output terminal of controlling component join.
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Cited By (23)
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| CN100507305C (en) * | 2005-10-15 | 2009-07-01 | 中国科学技术大学 | Magnetic flowing deformation elastomer frequency shift type attenuator and control method |
| CN100564932C (en) * | 2007-05-17 | 2009-12-02 | 中国科学技术大学 | Rigidity-variable full-automatic power vibration-absorber |
| CN101519111B (en) * | 2009-04-03 | 2010-12-01 | 哈尔滨工程大学 | Magneto-rheological elastomer intelligent damper for ship |
| CN102287465A (en) * | 2011-07-25 | 2011-12-21 | 重庆仪表材料研究所 | Magneto-rheological rigidity-adjustable helical spring |
| CN102606669A (en) * | 2012-03-22 | 2012-07-25 | 谢宁 | Three-dimensional swinging type magnetorheological damper |
| CN102878237A (en) * | 2012-10-23 | 2013-01-16 | 上海交通大学 | Combined intelligent magnetorheological elastomer vibration absorber for ship shafting longitudinal vibration |
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| CN104141723A (en) * | 2014-06-27 | 2014-11-12 | 长安大学 | Adjustable-inherent-frequency composite power vibration absorber and control method of adjustable-inherent-frequency composite power vibration absorber |
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| CN107191529A (en) * | 2017-03-27 | 2017-09-22 | 上海交通大学 | A kind of magnetic rheology elastic body thrust bearing pedestal dynamic vibration absorber and application method |
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| CN100507305C (en) * | 2005-10-15 | 2009-07-01 | 中国科学技术大学 | Magnetic flowing deformation elastomer frequency shift type attenuator and control method |
| CN100564932C (en) * | 2007-05-17 | 2009-12-02 | 中国科学技术大学 | Rigidity-variable full-automatic power vibration-absorber |
| CN101519111B (en) * | 2009-04-03 | 2010-12-01 | 哈尔滨工程大学 | Magneto-rheological elastomer intelligent damper for ship |
| CN102287465A (en) * | 2011-07-25 | 2011-12-21 | 重庆仪表材料研究所 | Magneto-rheological rigidity-adjustable helical spring |
| CN103129377A (en) * | 2011-11-23 | 2013-06-05 | 现代自动车株式会社 | Variable differential mount apparatus using magnetorheological elastomer |
| CN102606669A (en) * | 2012-03-22 | 2012-07-25 | 谢宁 | Three-dimensional swinging type magnetorheological damper |
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| CN102878237A (en) * | 2012-10-23 | 2013-01-16 | 上海交通大学 | Combined intelligent magnetorheological elastomer vibration absorber for ship shafting longitudinal vibration |
| CN103512624A (en) * | 2013-08-27 | 2014-01-15 | 黑龙江科技大学 | Coal cutter cutting resistance sensing method based on magnetorheological elastomer and sensor |
| CN103512624B (en) * | 2013-08-27 | 2016-04-27 | 黑龙江科技大学 | Based on coalcutter cutting resistance method for sensing and the sensor of magnetic rheology elastic body |
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| CN107191529B (en) * | 2017-03-27 | 2019-03-22 | 上海交通大学 | A kind of magnetic rheology elastic body thrust bearing pedestal dynamic vibration absorber and application method |
| CN107191529A (en) * | 2017-03-27 | 2017-09-22 | 上海交通大学 | A kind of magnetic rheology elastic body thrust bearing pedestal dynamic vibration absorber and application method |
| CN107152487B (en) * | 2017-04-20 | 2019-04-02 | 中国人民解放军63956部队 | A kind of symmetrical vehicle motor bump leveller of adjustable frequency |
| CN107152487A (en) * | 2017-04-20 | 2017-09-12 | 中国人民解放军63956部队 | A kind of symmetrical expression vehicle motor bump leveller of adjustable frequency |
| CN107606026A (en) * | 2017-08-16 | 2018-01-19 | 洛阳理工学院 | It is a kind of to open up frequency bump leveller and its control method based on intelligent stiffness elements |
| CN109606532A (en) * | 2018-12-19 | 2019-04-12 | 哈尔滨工程大学 | Fluid drag-reduction noise reduction intelligent skin structure based on magnetorheological elastic material |
| CN113757297A (en) * | 2021-09-09 | 2021-12-07 | 重庆交通大学 | Magnetorheological damper based on U-shaped coil |
| CN114251250A (en) * | 2021-12-02 | 2022-03-29 | 珠海格力节能环保制冷技术研究中心有限公司 | Damping ring, compressor assembly and air conditioner |
| CN114251250B (en) * | 2021-12-02 | 2023-10-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Vibration damping ring, compressor assembly and air conditioner |
| CN114536379A (en) * | 2022-04-25 | 2022-05-27 | 中国科学技术大学 | Exoskeleton |
| CN114536379B (en) * | 2022-04-25 | 2022-09-09 | 中国科学技术大学 | Exoskeleton |
| CN117167434A (en) * | 2023-11-03 | 2023-12-05 | 哈尔滨工程大学 | Multi-frequency adjustable-frequency dynamic vibration absorber |
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