CN104385874B - A kind of ultra-magnetic telescopic vehicle suspension vibration absorber of resonant frequency autotracking - Google Patents
A kind of ultra-magnetic telescopic vehicle suspension vibration absorber of resonant frequency autotracking Download PDFInfo
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- CN104385874B CN104385874B CN201410643718.2A CN201410643718A CN104385874B CN 104385874 B CN104385874 B CN 104385874B CN 201410643718 A CN201410643718 A CN 201410643718A CN 104385874 B CN104385874 B CN 104385874B
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Abstract
The invention discloses the ultra-magnetic telescopic vehicle suspension vibration absorber of a kind of resonant frequency autotracking, utilize giant magnetostrictive material energy density big, conversion efficiency is high, the advantage of fast response time, giant magnetostrictive material is embedded vehicle suspension vibration absorber, electromagnetic energy is converted mechanical energy into by magnetostrictive reaction and electromagnetic induction principle, the resonant frequency point of multiple LRC oscillation circuits is regulated by having the controller of frequency-tracking function, circuit is made to reach resonance power consumption state, it is achieved multi-modal passive vibration damping；Sending vibration reduction control signal by control circuit, drive GMM to offset vibration realizing active damping by magnetostriction positive-effect, the invention has the beneficial effects as follows the resonant frequency autotracking achieving vibration absorber, simple in construction, response is rapid, good damping result.
Description
Technical field
The present invention relates to a kind of vehicle suspension vibration damper, particularly to the ultra-magnetic telescopic vehicle suspension vibration damper of a kind of resonant frequency autotracking.
Background technology
Vehicle suspension can produce vibration owing to flexible member is subject to impact, affects safety and ride comfort that vehicle travels.In order to avoid Vibration of Vehicle Suspensions brings adverse influence, it is possible at vehicle suspension mounting dampers to reach the purpose of vibration damping.
Mostly the vibroshock of vehicle suspension is hydraulic shock absorber, its operation principle is vibrated when there is relative motion when between vehicle frame (or vehicle body) and vehicle bridge, piston in vibroshock moves up and down, and the fluid of vibroshock intracavity just flows into another intracavity from a chamber through different holes repeatedly.Vibration is formed damping force by now friction between hole wall and fluid and the intermolecular internal friction of fluid, makes automobile vibrational energy be converted into fluid heat energy, then is dispersed in air by shock absorber.
Rigidity and the vibration characteristics of above-mentioned traditional spring mass-damp type vehicle suspension vibration damper are superimposed on vehicle suspension, and the frequency response characteristic of vehicle suspension is additional on vibroshock, and show antiresonance feature at the fixing free-running frequency of vibroshock.The damping of vibroshock can affect frequency of vibration and exceed attenuation characteristic when system antiresonance responds, thus changing the vibration characteristics of system, it is achieved effective vibration damping.But the resonant frequency of above-mentioned traditional vehicle suspension vibration damper and damped coefficient are fixed, cause vibroshock cannot adapt to the Vehicular vibration operating mode of complexity.
Many research worker have carried out the research of self-adaptive damping coefficient vibroshock in recent years, and the damping adaptive of these vibroshocks substantially adopts two kinds of methods: first method changes resistance of shock absorber by regulating the hole size between vibroshock chamber；Second method realizes the change of resistance of shock absorber by changing the viscosity of fluid in vibroshock.Based on first method, Chinese invention patent 2010105522620 proposes a kind of circular hole by being drilled with specified quantity, position and size at the working cylinder tube wall of tradition double-cylinder hydraulic damper, changes the vibroshock aisle spare that fluid flows through under different operating modes and reaches to change the purpose of damping force.Upper piston body and the lower piston body of the vibroshock that Chinese invention patent 2005100212129 proposes are each provided with corresponding fluid opening in corresponding position, and upper piston body with lower piston body have at least one be connected with power set, can rotate under the driving of power set, fluid opening is made to misplace, change the sectional area of fluid circulation passage, change fluid from a cavity stream to the total amount flow velocity of another cavity, reach to adjust the requirement of damping.Based on second method, US Patent No. 7112474B2 proposes a kind of magnetorheological adaptive damping device, changes magnetic flow liquid viscosity by regulating magnetic field, it is achieved resistance of shock absorber size controls.Chinese invention patent 200710068598.8,201010241273.7,201010249025.7 propose a kind of magneto-rheological combined damping control method and device, comprehensive use magnetorheological fluid damp controls technology and giant magnetostrictive material branch damping, it is achieved resistance of shock absorber controls.
The self-adaptive damping coefficient vibroshock of above-mentioned Patent design achieves the adjustable control of damped coefficient, but no matter it is by changing the mechanical type of hole size damping control technology, or magnetorheological fluid damp controls technology or giant magnetostrictive material branch damping, and its resonant frequency is all fixing.Therefore above-mentioned self-adaptive damping coefficient vibroshock can only have higher energy conversion efficiency within the scope of narrower resonant frequency bandwidth, the mechanical energy of vibration is effectively dissipated.Under actual condition, the frequency of vibration of vehicle suspension, with the various factors such as road conditions, load, is often not at the resonant frequency bandwidth scope of vibroshock so that the effectiveness in vibration suppression of vibroshock is deteriorated.For improving effective damping frequency range of vibroshock, it is necessary to the ultra-magnetic telescopic vehicle suspension vibration damper of design autotracking resonant frequency.
Summary of the invention
For above-mentioned prior art Problems existing, the present invention provides the ultra-magnetic telescopic vehicle suspension vibration damper of a kind of resonant frequency autotracking, it is possible to frequency of vibration is carried out autotracking, makes vibroshock can effectively reduce Vibration of Vehicle Suspensions in wider frequency range, and simple in construction, response is rapidly.
To achieve these goals, the technical solution used in the present invention is: the ultra-magnetic telescopic vehicle suspension vibration damper of a kind of resonant frequency autotracking, including vehicle suspension, signal condition amplifying circuit, frequency-discriminating circuit, vibration damping controller；Described vehicle suspension vibration damper passes to signal condition amplifying circuit by sending GMM transducing signal, and according to this by frequency-discriminating circuit, vibration damping controller；Vibration damping controller realizes actively GMM branch damping and the damping of passive GMM branch by active damping signal generator and resonance energy consuming circuitry.
The present invention also provides for the ultra-magnetic telescopic vehicle suspension vibration absorber of a kind of resonant frequency autotracking, including urceolus, the soft magnetic bodies inner core being built-in with GMM and control circuit system.
The two ends of soft magnetic bodies inner core are connected with guide piston and piston rod respectively, and are fixed on urceolus by flexible member.
The two ends up and down of the GMM being arranged in soft magnetic bodies inner core are connected with lower permanent magnet and upper permanent magnet respectively, are surrounded with coil outside it.
Control circuit system includes vibration analysis control circuit and GMM control circuit.
Vibration analysis control circuit is made up of coil, signal condition amplifying circuit, frequency-discriminating circuit and vibration damping control circuit.
Described GMM control circuit is that single mode passive GMM branch damping control circuit, multi-modal branch damping control circuit or main passive hybridization GMM branch damping control circuit are a kind of.
The passive GMM branch damping control circuit of described single mode is by coil, resistance R, tunable capacitor CxConstitute.By tunable capacitor Cx, make coil, resistance R, tunable capacitor CxThe resonance circuit constituted is in resonance point.The electric energy that Suspension System Performance of Vehicle Model energy is changed into by counter magnetostriction effect resonance point can farthest to dissipate with the form of heat energy, thus realizing the target of vibration damping.
Described multi-modal branch damping control circuit, by multiple LRC tuning circuits, is specially resistance R1, Cx1LRC circuit in parallel, electric capacity C2 that described LRC circuit bag is sequentially connected in series, R2 and one's LC antiresonant circuit,On single mode passive GMM branch damping control circuit basis, multi-modal passive GMM branch adopts flow blocking circuit theory to realize multi-modal branch damping vibration control, it is possible to multiple vibration frequency components of vibration are effectively suppressed simultaneously.
Described master passively hybridizes GMM branch damping control circuit by coil, resistance R, current source i, tunable capacitor CxConstitute.Actively control to be then produce the vibration reduction control signal with vibration signal antiphase according to Vibration of Vehicle Suspensions, drive GMM to offset vibration by magnetostrictive effect.The controlled control that main passive hybridization GMM branch damping controls can make structure more stable, and actively controls can realize better controlling effect.
Described flexible member is spring.
The present invention, based on GMM transduction principle, integrated vibration signal frequency discrimination technology, defines the ultra-magnetic telescopic vehicle suspension vibration damping new technique of a kind of resonant frequency autotracking.The passive GMM branch damping of the present invention controls to utilize resonance circuit GMM when resonance point to have the feature of maximum conversion efficiency, and Vibration of Vehicle Suspensions energy is converted into thermal dissipation.The passive GMM branch damping of master of the present invention controls to adopt GMM to achieve active damping, makes the effectiveness in vibration suppression that main passive GMM branch damping controls more desirable with passive vibration damping combined effect.Frequency of vibration can be carried out autotracking by above-mentioned vehicle suspension damping technology, makes vibration absorber can effectively reduce Suspension System Performance of Vehicle Model in wider frequency range, overcomes the shortcoming that conventional truck suspension oscillation damping method operational frequency bandwidth is narrower.And the vehicle suspension damping device structure of present invention design is simple, response is rapidly, it is possible to adapt to the needs of vehicle suspension vibration damping under complex working condition.
Accompanying drawing explanation
Fig. 1 is the structured flowchart of the present invention.
Fig. 2 is vibration damping controller workflow diagram.
Fig. 3 is the ultra-magnetic telescopic vehicle suspension damping device structure figure of resonant frequency autotracking.
Fig. 4 is that the damping of passive GMM branch controls schematic diagram.
Fig. 5 is the passive GMM shunt impedance-frequency characteristic figure of single mode.
Fig. 6 is multi-modal passive GMM shunt impedance-frequency characteristic figure.
Fig. 7 is that main passive hybridization GMM branch damping controls schematic diagram.
In figure: 1, urceolus, 2, spring, 3, guide piston, 4, soft magnetic bodies inner core, 5, lower permanent magnet, 6, coil, 7, GMM, 8, upper permanent magnet, 9, piston rod.
Detailed description of the invention
Below in conjunction with accompanying drawing, the invention will be further described.
It is the structured flowchart of the present invention as shown in Figure 1, including vehicle suspension, signal condition amplifying circuit, frequency-discriminating circuit, vibration damping controller；Described vehicle suspension vibration absorber passes to signal condition amplifying circuit by sending GMM transducing signal, and according to this by frequency-discriminating circuit, vibration damping controller；Vibration damping controller realizes actively GMM branch damping and the damping of passive GMM branch by active damping signal generator and resonance energy consuming circuitry.It is through transforming circuit, the magnetic domain brought by vibration in GMM deflection is coupled to signal condition amplifying circuit at the voltage signal that coil induces carry out conditioning amplification that coil, GMM transforming circuit, signal condition amplifying circuit, frequency-discriminating circuit and vibration damping controller constitute its effect of vibration perception circuit, determined the frequency component of Vibration of Vehicle Suspensions by frequency-discriminating circuit, determine suitable vibration reduction strategy according to Vibration Condition on this basis.The vibration of vehicle suspension can produce changes of magnetic field by counter magnetostriction effect in GMM7, causes generation induced voltage in coil 6.Induced voltage signal is determined the frequency of vibration of vehicle suspension after being processed by signal condition amplifying circuit by frequency-discriminating circuit.Vibration damping controller regulates active damping signal generator and resonance energy consuming circuitry according to the frequency of vibration of vehicle suspension, it is achieved main passive GMM branch damping controls.
Being the vibration reduction strategy flow chart of vibration damping controller as shown in Figure 2, vibration damping controller determines the frequency distribution of vehicle suspension principal vibration energy by the frequency of vibration that frequency-discriminating circuit obtains.If vibrational energy distribution is at a Frequency point, then the passive GMM branch damping of single mode is adopted to control；If vibrational energy distribution is at multiple Frequency points, then the damping of multi-modal passive GMM branch is adopted to control.Determine that employing passive GMM branch damping controls or main passive GMM branch damping controls according to vehicle suspension size simultaneously.After determining vibration reduction strategy, by switching switch, circuit is switched to required shock absorption circuit.On this basis, tunable capacitor is regulated to adjust resonant frequency and the actively parameter such as the frequency of vibration of GMM branch and amplitude of passive GMM branch.
As shown in Figure 3, in the urceolus 1 of the ultra-magnetic telescopic vehicle suspension system vibration absorber of resonant frequency autotracking, soft magnetic bodies inner core 4 is installed, the two ends of soft magnetic bodies inner core 4 are connected with guide piston 3 and piston rod 9 respectively, it is fixed in urceolus 1 by spring 2, the two ends up and down of the GMM7 being arranged in soft magnetic bodies inner core 4 are connected with lower permanent magnet 5 and upper permanent magnet 8 respectively, are surrounded with coil 6 outside it.GMM7, lower permanent magnet 5, soft magnetic bodies inner core 4 and upper permanent magnet 8 constitute magnetic loop, and coil 6, signal condition amplifying circuit, frequency-discriminating circuit and vibration damping control circuit constitute vibration analysis control circuit.Coil 6, resistance R, tunable capacitor Cx constitute passive GMM branch damping control circuit.Coil 6, resistance R, current source i, tunable capacitor Cx constitutes main passive hybridization GMM branch damping control circuit.The magnetic loop that GMM, permanent magnet and soft magnetic bodies inner core are constituted.
The work process of the present invention is as follows:
Passive GMM branch damping control process as shown in Figure 4, during original state, GMM7 lower permanent magnet 5, on permanent magnet 8 effect under, its magnetic domain deflects vertically.Prefabricating load F is applied on vibroshock by piston rod 9, and provides support counter-force by spring 2.When vehicle suspension system produces vibration, oscillating load is added on prefabricating load F, makes the magnetic domain within GMM7 deflect, is changed by the magnetic flux of GMM7, and then produces induced voltage in coil.After induced voltage conditioning being amplified, obtained the frequency of vibration of vehicle suspension system by frequency-discriminating circuit.According to the dominant frequency component quantity of vibration, vibration damping controller determines that employing single mode passive GMM branch damping controls or the damping of multi-modal passive GMM branch controls.With Fig. 4 example, it is possible to achieve the abatement of single or two vibration frequency components.When frequency of vibration changes, by regulating tunable capacitor Cx1 and the Cx2 value in RC circuit, make LRC circuit be in resonant condition all the time, it is ensured that the faradic current in coil is converted into thermal energy consumption as far as possible, it is possible to the single of vibration or two vibration frequency components effectively to be suppressed simultaneously.
The impedance frequency characteristics curve of single mode passive GMM branch damping is as it is shown in figure 5, resonance circuit has maximum impedance at resonant frequency f0 place, and now RC circuit is in resonant condition, the faradic current in coil can be at utmost converted into thermal energy consumption.
The impedance frequency characteristics curve of multi-modal passive GMM branch damping is as shown in Figure 6, resonance circuit has maximum impedance at resonant frequency f1 and f2 place, now RC circuit is in resonant condition at frequency f1 and f2, faradic current in coil at utmost can be converted into thermal energy consumption, be suitable for eliminating the vibration that two frequency components are bigger.
Main passive hybridization GMM branch damping control process is as it is shown in fig. 7, its circuit seals in active current source in LRC circuit.It is similar that the passive control work process of this circuit damps control process with above-mentioned passive GMM branch, and its active control process is then according to the vibration signal generation vibration reduction control signal sensed, is applied to coil 6 rear drive GMM7 to realize the active control of vibration.The controlled control that main passive hybridization GMM branch damping controls can make structure more stable, and actively controls can realize better controlling effect.
GMM referred to herein is giant magnetostrictive material; such as Terfeol-D; above-mentioned detailed description of the invention is used for illustrating the present invention; rather than limit the invention; in the spirit and scope of the claims of the present invention; any amendment that the present invention is made and change, both fall within protection scope of the present invention.
Claims (3)
1. the ultra-magnetic telescopic vehicle suspension vibration absorber of a resonant frequency autotracking, it is characterised in that include urceolus, be built-in with soft magnetic bodies inner core and the control circuit system of GMM；The two ends of soft magnetic bodies inner core are connected with guide piston and piston rod respectively, and are fixed on urceolus by flexible member；The two ends up and down of the GMM being arranged in soft magnetic bodies inner core are connected with lower permanent magnet and upper permanent magnet respectively, are surrounded with coil outside it；Control circuit system includes vibration analysis control circuit and GMM control circuit；Vibration analysis control circuit is made up of coil, signal condition amplifying circuit, frequency-discriminating circuit and vibration damping control circuit；Described GMM control circuit is that single mode passive GMM branch damping control circuit, multi-modal branch damping control circuit or main passive hybridization GMM branch damping control circuit are a kind of；Described single mode passive GMM branch damping control circuit is made up of coil, resistance R, tunable capacitor Cx, and described multi-modal branch damping control circuit is made up of multiple LRC tuning circuits,
Described master passively hybridizes GMM branch damping control circuit by coil, resistance R, current source i, and tunable capacitor Cx is constituted.
2. the ultra-magnetic telescopic vehicle suspension vibration absorber of a kind of resonant frequency autotracking according to claim 1, it is characterised in that described flexible member is spring.
3. the ultra-magnetic telescopic vehicle suspension vibration absorber of a kind of resonant frequency autotracking according to claim 1, it is characterized in that, described multi-modal branch damping control circuit includes the LRC circuit in parallel with resistance R1, Cx1, electric capacity C2 that described LRC circuit bag is sequentially connected in series, R2 and one's LC antiresonant circuit.
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| CN105508495B (en) * | 2015-12-15 | 2016-08-24 | 西安科技大学 | A kind of energy magnetic rheology elastic body vehicle damper and control method thereof |
| CN107807532B (en) * | 2017-11-30 | 2020-02-18 | 北京航空航天大学 | Self-adaptive reverse vibration isolation control method for giant magnetostrictive vibration isolation platform |
| CN114448161B (en) * | 2022-01-27 | 2023-10-13 | 中国长江三峡集团有限公司 | High-temperature superconductive magnetic suspension flywheel with axial vibration isolation function |
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| US5163659A (en) * | 1990-12-11 | 1992-11-17 | Monroe Auto Equipment Company | Hydraulic actuator for leveling system |
| US7255290B2 (en) * | 2004-06-14 | 2007-08-14 | Charles B. Bright | Very high speed rate shaping fuel injector |
| CN100552257C (en) * | 2007-05-22 | 2009-10-21 | 浙江大学 | A kind of magneto-rheologic damping control method |
| CN201802802U (en) * | 2010-08-06 | 2011-04-20 | 浙江大学 | Magnetorheological composite damp control device |
| CN101915283B (en) * | 2010-08-06 | 2011-12-07 | 浙江大学 | Magneto-rheological combined damping control method and device |
| CN204222577U (en) * | 2014-11-14 | 2015-03-25 | 徐州华夏电子有限公司 | The ultra-magnetic telescopic vehicle suspension shock attenuation unit of resonant frequency autotracking |
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Denomination of invention: A damping device of giant magnetostrictive vehicle suspension with resonance frequency self tracking Effective date of registration: 20200805 Granted publication date: 20160629 Pledgee: Bank of China Limited by Share Ltd. Xuzhou Copper Mt branch Pledgor: XUZHOU HUAXIA ELECTRONICS Co.,Ltd. Registration number: Y2020320000180 |