CN1042974A - Continuous adjustable method for vibration of electromagnetic type spring rate and vibration absorber - Google Patents
Continuous adjustable method for vibration of electromagnetic type spring rate and vibration absorber Download PDFInfo
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- CN1042974A CN1042974A CN 88107926 CN88107926A CN1042974A CN 1042974 A CN1042974 A CN 1042974A CN 88107926 CN88107926 CN 88107926 CN 88107926 A CN88107926 A CN 88107926A CN 1042974 A CN1042974 A CN 1042974A
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- 239000006096 absorbing agent Substances 0.000 title claims abstract description 42
- 238000000034 method Methods 0.000 title claims abstract description 6
- 230000003313 weakening effect Effects 0.000 claims abstract description 17
- 230000000694 effects Effects 0.000 claims description 6
- 230000015572 biosynthetic process Effects 0.000 claims description 4
- 230000010355 oscillation Effects 0.000 claims description 3
- 230000007704 transition Effects 0.000 claims 1
- 238000006243 chemical reaction Methods 0.000 abstract description 3
- 230000005284 excitation Effects 0.000 description 2
- 238000005755 formation reaction Methods 0.000 description 2
- 230000000994 depressogenic effect Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 239000000696 magnetic material Substances 0.000 description 1
- 230000003071 parasitic effect Effects 0.000 description 1
- 230000035699 permeability Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
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Abstract
The present invention relates to continuously adjustable vibration absorber method of a kind of electromagnetic type spring rate and vibration absorber, it utilizes the mechanical spring in the electromagnetic spring replacement traditional power vibration absorber, vibration frequency according to vibrating object, regulate the field current in the electromagnetic spring, can change the spring rate of electromagnetic spring, reach the weakening purpose, the present invention is through enforcement, and the weakening effect under the frequency conversion condition makes us very satisfied.
Description
The invention belongs to vibration control and vibration absorber field.
As everyone knows, on vibrating object, install a parasitic vibration system undamped, that only form additional by spring and quality, as long as the natural frequency of this system equates with the vibration frequency of vibrating object, can eliminate the vibration (can make in theory its depressed fully) of oscillating body effectively.This spare system is exactly the dynamic damper (see figure 1) that people are familiar with.But traditional dynamic damper is unadjustable owing to its natural frequency immobilizes, and more can not carry out frequency-tracking control, and it can only be used for the changeless special occasions of vibration frequency.The occasion more common for those, that vibration frequency often changes, traditional dynamic damper does not only have good weakening effect, often can make vibration become more complicated on the contrary.This has just limited the using scope of traditional power vibration absorber greatly.
The objective of the invention is partly to replace mechanical spring in the traditional power vibration absorber with the continuously adjustable electromagnetic spring of a kind of its rigidity, regulate the electric current of field coil in the electromagnetic spring, can change the rigidity of electromagnetic spring, thereby obtain the required natural frequency identical, reach the purpose of weakening with frequency vibrating object.
Particular content of the present invention is, change traditional method for vibration, an additional mechanical spring and an electromagnetic spring on the weakening object, electromagnetic spring is by field coil, stator, mover is formed, after the field coil energising, produce magnetic pull between stator and the mover, the size of magnetic pull, direction and stator, offset direction between the mover, deviation distance is relevant, the effect of magnetic pull is to eliminate bias, make stator, mover returns to the equilibrium position, according to the frequency of vibrating object, regulates the field current in the electromagnetic spring, can change the rigidity of electromagnetic spring, reach the purpose of weakening.
Utilize new method for vibration, the present invention has designed a kind of new vibration absorber, and it is made up of mechanical spring, the electromagnetic spring that contains stator and mover and bearing.This vibration absorber (2) is formed frequency-tracking weakening system (Fig. 2) jointly with vibration detecting sensor (3), signal amplifier (4), frequency discriminator (5), voltage to frequency switching controller (7) and power amplifier (6).
Description of drawings:
Fig. 1: traditional vibration absorber
Fig. 2: frequency-tracking weakening system
Fig. 3: the continuous adjustable vibration absorber of electromagnetic type natural frequency
Fig. 4: the another kind of scheme of vibration absorber
Fig. 5: the vibration absorber of eliminating torsional vibration
Fig. 6: the another kind of scheme of eliminating the vibration absorber of torsional vibration
Fig. 7: the spring-loaded sheet of vibration absorber
Fig. 8: the mounting type of vibration absorber
Below in conjunction with accompanying drawing, introduce summary of the invention in detail.
The present invention forms (see figure 3) by stator, mover, field coil, spring and bearing.Stator 11 movably connects by means of two bearings 8 and two groups of springs 9 formations with mover 12.The magnetic circuit part of stator and mover is all made with good permeability magnetic material.Carry out excitation by field coil 13.Leave a small air gap between the working surface of stator and mover.Behind coil electricity, the magnetic line of force forms a loop by two air gaps between fixed, the mover.Owing to be distributed with the identical rectangle gear ring of the facewidth, tooth pitch and the number of teeth at stator with mover working surface upper edge axial direction, can produce magnetic pull between the flank of tooth of stator and mover.The size and Orientation of this magnetic pull is relevant with tooth deviation distance and offset direction fixed, mover.When the tooth of stator and mover fully on time, magnetic pull is zero, this position is called stable equilibrium position.In the scope of the bias △ of stator and mover tooth S less than ± 1/4 tooth pitch T, magnetic pull increases with the increase of bias △ S, the direction of magnetic pull is then opposite with offset direction fixed, the mover tooth, and its effect is to try hard to eliminate bias fixed, mover, makes it be returned to stable equilibrium position.This is just similar with the characteristic of mechanical spring, so claim electromagnetic spring.By regulating field current, can change the spring rate of electromagnetic spring easily.Field coil 13 can be fixed on the mover, also can be fixed on the stator.The effect of two rolling bearings 8 is to allow to do relative movement vertically and keep its crack size constant between mover and the stator, and can reduce the surface friction drag between stator and the mover.The effect of mechanical spring 9 has two: 1. when vibration absorber is not worked, make stator and mover be in stable equilibrium position mutually; 2. it is in parallel with electromagnetic spring, constitutes the total spring rate of vibration absorber.The spring rate of mechanical spring should be chosen like this, and when electromagnetic spring rigidity was zero (field current is zero), the natural frequency that mechanical spring and mover quality are constituted should be equal to or slightly less than the lowest vibration frequency of controlled device.Can reduce the adjustment range of electromagnetic spring rigidity like this, simplify the design of vibration absorber, dwindle the volume of vibration absorber.The effect of stop pin 10 is to prevent to relatively rotate between stator and the mover.Can also replace bearing, mechanical spring and stop pin in the vibration absorber with the spring-loaded sheet as Fig. 7, it integrates three's function, makes mover pass through the spring-loaded sheet and movably connects with the stator formation, as Fig. 4.The stator of vibration absorber and the position of mover can be changed mutually, are about to part 11 among Fig. 3 as mover, and with part 12 as stator.
When the present invention uses, stator should be connected together with being connected firmly by weakening object 1, different according to use occasion and service condition, the mounting type of vibration absorber can adopt suspension type, and (Fig. 8 is a), two vibration absorbers (Fig. 8 c) are promptly used in locating type (Fig. 8 b) or two-way weakening.
The present invention includes Fig. 3, straight-line oscillation vibration absorber shown in Figure 4 and Fig. 5, torsional vibration vibration absorber shown in Figure 6.The working principle of torsional vibration vibration absorber is identical with the straight-line oscillation vibration absorber, and only the tooth on its stator and the mover is circumferential, and spring is used torsion spring 15 and cancellation stop pin instead.
The concrete structure parameter of vibration absorber (as the size of the quality of mover, spring and quantity and distribution mode thereof, exciting watts or the like) all needs determine according to service condition, decides by dedicated calculation usually.
The present invention was implemented by the inventor, experimental results show that the weakening effect under the frequency conversion condition makes us very satisfied.
Electromagnetic type is reversed the vibration absorber embodiment:
1. utilizing one of a three-phase stepper motor to carry out the weakening of frequency conversion rate as the variable ratio frequency changer vibration absorber tests.
2. vibration absorber stator diameter (air gap place working surface diameter) Φ 20mm
40 of the stator numbers of teeth
9 ° of angular pitch
Stator tooth length 20mm
Air gap 0.1mm
Maximum exciting watts 350 ampere-turns
Maximum magnetic flux moment 1200 gram-centimeters
Do not add mechanical spring
Vibration absorber natural frequency adjustment range 0～27HZ
3. experimental result:
Original vibration when not adding vibration absorber (promptly vibration absorber not being carried out excitation): excited frequency by the scope of 0～27HZ in peak swing 72 μ (arc length of measuring point).
After adding vibration absorber, peak swing is in same frequency range: 6.5 μ.
Effectively the weakening rate is: 72-6.5/72 * %=91%
Claims (6)
1, a kind of on the weakening object method for vibration of an additional spring and mass block, the electromagnetic spring that the spring that it is characterized in that adding is made up of field coil, mover, stator.After the field coil energising, produce magnetic pull between stator and the mover, the size of magnetic pull, direction are relevant with offset direction, deviation distance between the stator mover, the effect of magnetic pull is to eliminate bias, make stator, mover return to the equilibrium position,, regulate the field current in the electromagnetic spring according to the vibration frequency of vibrating object, can change the spring rate of electromagnetic spring, reach the weakening purpose.
2, a kind of dynamic damper, it comprises mechanical spring, it is characterized in that also comprising electromagnetic spring, described electromagnetic spring is made up of stator, mover and field coil, and field coil is fixed on the stator, also can be fixed on the mover, be distributed with the identical rectangle gear ring of the facewidth, tooth pitch and the number of teeth on the working surface of stator mover, stay an air gap between the working surface, stator be fixedly connected by the weakening object, and movably connect with the mover formation by bearing and mechanical spring.
3, vibration absorber as claimed in claim 2 is characterized in that described vibration absorber and vibration detecting sensor, signal amplifier, and frequency discriminator, frequency-voltage transitions controller and power amplifier are formed a frequency-tracking weakening system.
4, vibration absorber as claimed in claim 2 is characterized in that stator movably connects with the mover formation by elastic support piece in the wherein said electromagnetic spring.
5, vibration absorber as claimed in claim 2 is characterized in that in the wherein said electromagnetic spring that the gear ring on stator and the mover working surface distributes vertically, is used to eliminate straight-line oscillation.
6, vibration absorber as claimed in claim 2 is characterized in that in the wherein said electromagnetic spring that the gear ring on stator and the mover working surface distributes vertically, and described mechanical spring is a torsion spring, is used to eliminate torsional vibration.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 88107926 CN1016983B (en) | 1988-11-24 | 1988-11-24 | Electromagnetic vibration damper with continuously-adjustable spring rigidity |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 88107926 CN1016983B (en) | 1988-11-24 | 1988-11-24 | Electromagnetic vibration damper with continuously-adjustable spring rigidity |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1042974A true CN1042974A (en) | 1990-06-13 |
| CN1016983B CN1016983B (en) | 1992-06-10 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 88107926 Expired CN1016983B (en) | 1988-11-24 | 1988-11-24 | Electromagnetic vibration damper with continuously-adjustable spring rigidity |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1016983B (en) |
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| CN101943243A (en) * | 2010-06-25 | 2011-01-12 | 哈尔滨工程大学 | Electromagnetic type two-degree-of-freedom semi-active vibration absorber |
| CN102364156A (en) * | 2011-11-07 | 2012-02-29 | 哈尔滨工程大学 | Coil built-in semiactive vibration absorber with closed structure |
| CN102410336A (en) * | 2011-11-07 | 2012-04-11 | 哈尔滨工程大学 | Coil external type semiactive vibration absorber in enclosed structure |
| CN103062375A (en) * | 2013-01-21 | 2013-04-24 | 北京理工大学 | Active control device for torsional vibration of gear pair |
| CN103464789A (en) * | 2013-07-05 | 2013-12-25 | 重庆望江工业有限公司 | Auxiliary vibration absorbing device for variable-diameter long shaft turning |
| CN103615488A (en) * | 2013-11-29 | 2014-03-05 | 哈尔滨工程大学 | Spring steel disc type dynamic vibration absorber with adjustable rigidity |
| CN105156532A (en) * | 2015-09-02 | 2015-12-16 | 西北工业大学 | Permanent magnet type eddy current energy-consumption dynamic vibration absorber |
| CN105317912A (en) * | 2015-11-13 | 2016-02-10 | 哈尔滨工程大学 | Wideband semi-active vibration absorber with adjustable rigidity and damping |
| CN105443635A (en) * | 2016-01-07 | 2016-03-30 | 南昌航空大学 | Frequency adjustable stair beam type dynamic vibration absorber based on piezoelectric feedback control |
| CN105587812A (en) * | 2016-03-15 | 2016-05-18 | 哈尔滨工程大学 | Electromagnetic spring with linear negative stiffness characteristic |
| CN105757153A (en) * | 2016-03-15 | 2016-07-13 | 哈尔滨工程大学 | Electromagnetic spring with linear stiffness characteristic |
| CN105909713A (en) * | 2016-05-12 | 2016-08-31 | 哈尔滨工程大学 | High-linearity electromagnetic type semi-active vibration absorber |
| CN106015420A (en) * | 2016-08-08 | 2016-10-12 | 河海大学 | Semi-active vibration control eddy current damper |
| CN107339352A (en) * | 2017-08-21 | 2017-11-10 | 哈尔滨工程大学 | A kind of electromagnetism Electromechanical Coupling Circuit tunes bump leveller |
| CN108602167A (en) * | 2016-02-16 | 2018-09-28 | 西门子股份公司 | The inhibition of machine vibration |
| CN109630582A (en) * | 2018-12-27 | 2019-04-16 | 上海大学 | A kind of electromagnetic spring of adjustable rigidity |
| CN109915519A (en) * | 2019-03-12 | 2019-06-21 | 上海交通大学 | Electromagnetism inhales vibrating isolation system |
| CN110686034A (en) * | 2019-10-11 | 2020-01-14 | 北京邮电大学 | Rotary electromagnetic damper with bidirectional torsion spring |
| CN114688204A (en) * | 2022-04-20 | 2022-07-01 | 西南交通大学 | Full-active vibration absorption system driven by electromagnetic force and gravity in combined mode and using method thereof |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101328946B (en) * | 2007-06-19 | 2011-11-09 | 刘新广 | Self-magnetic tuning vibrating absorber |
-
1988
- 1988-11-24 CN CN 88107926 patent/CN1016983B/en not_active Expired
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101943243A (en) * | 2010-06-25 | 2011-01-12 | 哈尔滨工程大学 | Electromagnetic type two-degree-of-freedom semi-active vibration absorber |
| CN101943243B (en) * | 2010-06-25 | 2012-02-01 | 哈尔滨工程大学 | Electromagnetic type two freedom degree semi-active vibration absorber |
| CN102364156A (en) * | 2011-11-07 | 2012-02-29 | 哈尔滨工程大学 | Coil built-in semiactive vibration absorber with closed structure |
| CN102410336A (en) * | 2011-11-07 | 2012-04-11 | 哈尔滨工程大学 | Coil external type semiactive vibration absorber in enclosed structure |
| CN103062375A (en) * | 2013-01-21 | 2013-04-24 | 北京理工大学 | Active control device for torsional vibration of gear pair |
| CN103464789A (en) * | 2013-07-05 | 2013-12-25 | 重庆望江工业有限公司 | Auxiliary vibration absorbing device for variable-diameter long shaft turning |
| CN103615488A (en) * | 2013-11-29 | 2014-03-05 | 哈尔滨工程大学 | Spring steel disc type dynamic vibration absorber with adjustable rigidity |
| CN103615488B (en) * | 2013-11-29 | 2015-09-30 | 哈尔滨工程大学 | The spring steel chip dynamic vibration absorber that a kind of rigidity is adjustable |
| CN105156532A (en) * | 2015-09-02 | 2015-12-16 | 西北工业大学 | Permanent magnet type eddy current energy-consumption dynamic vibration absorber |
| CN105156532B (en) * | 2015-09-02 | 2017-03-22 | 西北工业大学 | Permanent magnet type eddy current energy-consumption dynamic vibration absorber |
| CN105317912A (en) * | 2015-11-13 | 2016-02-10 | 哈尔滨工程大学 | Wideband semi-active vibration absorber with adjustable rigidity and damping |
| CN105443635A (en) * | 2016-01-07 | 2016-03-30 | 南昌航空大学 | Frequency adjustable stair beam type dynamic vibration absorber based on piezoelectric feedback control |
| CN105443635B (en) * | 2016-01-07 | 2017-09-19 | 南昌航空大学 | A kind of frequency-adjustable ladder beam-type dynamic vibration absorber based on piezoelectricity feedback control |
| CN108602167A (en) * | 2016-02-16 | 2018-09-28 | 西门子股份公司 | The inhibition of machine vibration |
| CN108602167B (en) * | 2016-02-16 | 2020-09-18 | 西门子股份公司 | Suppression of machine vibrations |
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| CN105587812A (en) * | 2016-03-15 | 2016-05-18 | 哈尔滨工程大学 | Electromagnetic spring with linear negative stiffness characteristic |
| CN105757153A (en) * | 2016-03-15 | 2016-07-13 | 哈尔滨工程大学 | Electromagnetic spring with linear stiffness characteristic |
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| CN105909713B (en) * | 2016-05-12 | 2018-08-17 | 哈尔滨工程大学 | A kind of high linearity electromagnetic type semi active vibration absorber |
| CN106015420B (en) * | 2016-08-08 | 2018-05-11 | 河海大学 | A kind of semi-active type vibration control eddy current damper |
| CN106015420A (en) * | 2016-08-08 | 2016-10-12 | 河海大学 | Semi-active vibration control eddy current damper |
| CN107339352A (en) * | 2017-08-21 | 2017-11-10 | 哈尔滨工程大学 | A kind of electromagnetism Electromechanical Coupling Circuit tunes bump leveller |
| CN109630582A (en) * | 2018-12-27 | 2019-04-16 | 上海大学 | A kind of electromagnetic spring of adjustable rigidity |
| CN109630582B (en) * | 2018-12-27 | 2019-11-26 | 上海大学 | A kind of electromagnetic spring of adjustable rigidity |
| US10844927B2 (en) | 2018-12-27 | 2020-11-24 | Shanghai University | Stiffness-adjustable electromagnetic spring |
| CN109915519A (en) * | 2019-03-12 | 2019-06-21 | 上海交通大学 | Electromagnetism inhales vibrating isolation system |
| CN110686034A (en) * | 2019-10-11 | 2020-01-14 | 北京邮电大学 | Rotary electromagnetic damper with bidirectional torsion spring |
| CN114688204A (en) * | 2022-04-20 | 2022-07-01 | 西南交通大学 | Full-active vibration absorption system driven by electromagnetic force and gravity in combined mode and using method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1016983B (en) | 1992-06-10 |
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