CN104455140A - Damper for vehicle suspension - Google Patents
Damper for vehicle suspension Download PDFInfo
- Publication number
- CN104455140A CN104455140A CN201410644036.3A CN201410644036A CN104455140A CN 104455140 A CN104455140 A CN 104455140A CN 201410644036 A CN201410644036 A CN 201410644036A CN 104455140 A CN104455140 A CN 104455140A
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- Prior art keywords
- gmm
- vibration
- damping
- vehicle suspension
- control circuit
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Classifications
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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
- F16F6/00—Magnetic springs; Fluid magnetic springs, i.e. magnetic spring combined with a fluid
Abstract
The invention discloses a vehicle suspension system. A giant magnetostriction material (GMM) is embedded in the vehicle suspension system by means of the advantages of the giant magnetostriction material that the energy density is high, the conversion efficiency is high and the response speed is high, a damping control signal is emitted through a control circuit, and damping is achieved by driving the GMM through the magnetostrictive effect to neutralize vibration. The vehicle suspension system has the advantages that the structure is simple, rapid response is achieved, and a damping system is good.
Description
Technical field
The present invention relates to a kind of vehicle suspension vibration damper.
Background technique
Vehicle suspension can produce vibration because elastic element is subject to impact, affects Security and the smoothness of vehicle traveling.In order to avoid Vibration of Vehicle Suspensions brings adverse influence, can at vehicle suspension mounting dampers to reach the object of vibration damping.
Mostly the vibration damper of vehicle suspension is hydraulic shock absorber, its working principle when between vehicle frame (or vehicle body) and vehicle bridge, is subject to vibration when there is relative movement, piston in vibration damper moves up and down, and the fluid in vibration damper chamber just flows in another chamber from a chamber through different holes repeatedly.Friction now between hole wall and fluid and the intermolecular interior friction of fluid form damping force to vibration, make automobile vibrational energy be converted into fluid heat energy, then are dispersed in air by shock absorber.
Rigidity and the vibration characteristics of above-mentioned traditional spring mass-damped type vehicle suspension vibration damper are superimposed on vehicle suspension, and the frequency response characteristic of vehicle suspension is additional on vibration damper, and show anti-resonance feature at the fixing free-running frequency of vibration damper.The damping of vibration damper can affect attenuation characteristic when vibration frequency exceedes system antiresonance response, thus changes the vibration characteristics of system, realizes effective vibration damping.But resonant frequency and the damping constant of above-mentioned traditional vehicle suspension vibration damper are fixed, cause vibration damper cannot adapt to complicated Vehicular vibration operating mode.
Many researchers have carried out the research of self-adaptive damping coefficient vibration damper in recent years, and the damping adaptive of these vibration dampers adopts two kinds of methods substantially: first method changes resistance of shock absorber by regulating the hole size between vibration damper chamber; Second method realizes the change of resistance of shock absorber by the viscosity changing vibration damper inner fluid.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 clutch release slave cylinder tube wall of traditional double-cylinder hydraulic damper, changes the vibration damper aisle spare that fluid flows through under different operating mode and reaches the object changing damping force.The upper piston body of the vibration damper that Chinese invention patent 2005100212129 proposes and lower piston body are provided with corresponding fluid opening separately in corresponding position, and upper piston body with have one in lower piston body at least and be connected with power plant, can rotate under the driving of power plant, fluid opening is misplaced, change the sectional area of fluid circulation passage, change fluid flows to another cavity total amount flow velocity from a cavity, reach the requirement of adjustment damping.Based on second method, US Patent No. 7112474B2 proposes a kind of magnetorheological adaptive damping device, by regulating magnetic field to change magnetic flow liquid viscosity, realizing resistance of shock absorber size and controlling.Chinese invention patent 200710068598.8,201010241273.7,201010249025.7 propose a kind of magneto-rheological combined damping control method and device, and comprehensive use magnetorheological fluid damp control technique and super magnetostriction material damping along separate routes, realizes resistance of shock absorber and control.
The self-adaptive damping coefficient vibration damper of above-mentioned Patent design achieves the adjustable control of damping constant, but be no matter the mechanical type damping control technique by changing hole size, or magnetorheological fluid damp control technique or super magnetostriction material damping along separate routes, its resonant frequency is all fixing.Therefore above-mentioned self-adaptive damping coefficient vibration damper can only have higher energy conversion efficiency in narrower resonance frequency band wide range, the mechanical energy of vibration is effectively dissipated.Under actual conditions, the vibration frequency of vehicle suspension, with the various factors such as road conditions, load, is not often in the resonance frequency band wide range of vibration damper, and the effectiveness in vibration suppression of vibration damper is deteriorated.For improving effective damping frequency range of vibration damper, be necessary the ultra-magnetic telescopic vehicle suspension vibration damper designing self-tracking resonant frequency.
Summary of the invention
For above-mentioned prior art Problems existing, the invention provides a kind of vehicle suspension vibration damper, can carry out self-tracking to vibration frequency, make vibration damper effectively can reduce Vibration of Vehicle Suspensions in wider frequency range, and structure is simple, response rapidly.
To achieve these goals, the technical solution used in the present invention is: a kind of ultra-magnetic telescopic vehicle suspension vibration damping equipment of resonant frequency self-tracking, comprises urceolus and soft magnetic bodies inner core, described; The two ends of soft magnetic bodies inner core are connected with piston rod with guide piston respectively, and guide piston is fixed on urceolus by spring element, for being provided with a bronze medal parietal layer inside urceolus;
Soft magnetic bodies inner tube installation has GMM, and the two ends up and down of its GMM are connected with upper permanent magnet with lower permanent magnet respectively, and its periphery is wound with coil,
Control circuit system involving vibrations analysis controling circuit and GMM control circuit;
Vibration analysis control circuit is made up of coil, signal condition amplification circuit, frequency-discriminating circuit and vibration damping control circuit;
Described GMM control circuit is by coil, resistance
r, current source
i,tunable capacitor Cx is formed,
One end of resistance R connects the common port of single-pole double-throw switch (SPDT), and an output terminal of single-pole double-throw switch (SPDT) connects current source
ia end, another output terminal of double-pole switch and current source
i'sone end that b end connects electric capacity Cx connects.
Described spring element is Rectangular Spring.
Described GMM is Terfeol-D.
The present invention is based on GMM transduction principle, integrated oscillating signal frequency discrimination technology, define a kind of ultra-magnetic telescopic vehicle suspension vibration damping new technology of resonant frequency self-tracking.Passive GMM of the present invention along separate routes damping controls to utilize resonance circuitry GMM when resonance point to have the feature of maximum conversion efficiency, is thermal dissipation by Vibration of Vehicle Suspensions Conversion of Energy.The passive GMM of master of the present invention along separate routes damping controls to adopt GMM to achieve active damping, and the effectiveness in vibration suppression main passive GMM shunt damping being controlled with passive vibration damping acting in conjunction is more desirable.Above-mentioned vehicle suspension damping technology can carry out self-tracking to vibration frequency, makes vibration damping equipment effectively can 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 the present invention's design is simple, response rapidly, can adapt to the needs of vehicle suspension vibration damping under complex working condition.Meanwhile, the present invention can make system in passive GMM damping control and main passive hybridization GMM damping control switching mutually along separate routes along separate routes by single-pole double-throw switch (SPDT), can prevent leakage field inside urceolus for being provided with copper parietal layer.
Accompanying drawing explanation
Fig. 1 is 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 self-tracking.
Fig. 4 is passive GMM damping control schematic diagram along separate routes.
Fig. 5 is the passive GMM shunt impedance-frequency characteristic figure of single mode.
Fig. 6 is main passive hybridization GMM damping control schematic diagram along separate routes.
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, 10, single-pole double-throw switch (SPDT).
Embodiment
Below in conjunction with accompanying drawing, the invention will be further described.
Be structured flowchart of the present invention as shown in Figure 1, comprise vehicle suspension, signal condition amplification circuit, frequency-discriminating circuit, vibration damping controller; Described vehicle suspension vibration damping equipment passes to signal condition amplification circuit by sending GMM transducing signal, and according to this by frequency-discriminating circuit, vibration damping controller; Vibration damping controller realizes initiatively GMM damping and passive GMM damping along separate routes along separate routes by active damping signal generator and resonance energy consuming circuitry.It is the magnetic domain brought by vibration in GMM deflection is coupled to signal condition amplification circuit at the voltage signal that coil induces through transforming circuit carry out conditioning amplification that coil, GMM transforming circuit, signal condition amplification circuit, frequency-discriminating circuit and vibration damping controller constitute its effect of vibration perception circuit, by the frequency component of frequency-discriminating circuit determination Vibration of Vehicle Suspensions, 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 producing induced voltage in coil 6.Induced voltage signal, by after the process of signal condition amplification circuit, is determined the vibration frequency of vehicle suspension by frequency-discriminating circuit.Vibration damping controller regulates active damping signal generator and resonance energy consuming circuitry according to the vibration frequency of vehicle suspension, realizes main passive GMM damping control along separate routes.
The vibration reduction strategy flow chart of vibration damping controller as shown in Figure 2, the frequency distribution of the vibration frequency determination vehicle suspension principal vibration energy that vibration damping controller is obtained by frequency-discriminating circuit.If vibrational energy distribution is at a Frequency point, then adopt the passive GMM of single mode damping control along separate routes; If vibrational energy distribution is at multiple Frequency point, then adopt multi-modal passive GMM damping control along separate routes.Determine to adopt passive GMM shunt damping to control or main passive GMM damping control along separate routes according to vehicle suspension size simultaneously.After determining vibration reduction strategy, by diverter switch, circuit is switched to required shock absorption circuit.On this basis, regulate tunable capacitor with parameters such as the vibration frequency of the resonant frequency and initiatively GMM shunt that adjust passive GMM shunt and amplitudes.
As shown in Figure 3, in the urceolus 1 of the ultra-magnetic telescopic vehicle suspension system vibration damping equipment of resonant frequency self-tracking, soft magnetic bodies inner core 4 is installed, the two ends of soft magnetic bodies inner core 4 are connected with piston rod 9 with guide piston 3 respectively, be fixed in urceolus 1 by spring 2, for being provided with a bronze medal parietal layer inside urceolus 1, for magnetic-leakage preventing, the two ends being up and down arranged on the GMM7 in soft magnetic bodies inner core 4 are connected with upper permanent magnet 8 with lower permanent magnet 5 respectively, and its periphery is wound with coil 6.GMM7, lower permanent magnet 5, soft magnetic bodies inner core 4 and upper permanent magnet 8 constitute magnetic loop, and coil 6, signal condition amplification circuit, frequency-discriminating circuit and vibration damping control circuit constitute vibration analysis control circuit.One end of resistance R connects the common port of single-pole double-throw switch (SPDT) 10, and an output terminal of single-pole double-throw switch (SPDT) 10 connects current source
ia end, another output terminal of double-pole switch 10 and current source
i'sone end that b end connects electric capacity Cx connects.
Coil 6, resistance R, tunable capacitor Cx constitute passive GMM damping control circuit along separate routes.Coil 6, resistance R, current source i, tunable capacitor Cx constitutes main passive hybridization GMM damping control circuit along separate routes.The magnetic loop that GMM, permanent magnet and soft magnetic bodies inner core are formed.
Working procedure of the present invention is as follows:
Passive GMM along separate routes damping control procedure as shown in Figure 4, by double-pole switch 10 output terminal and current source
i'sone end that b end connects electric capacity Cx connects, and forms the passive GMM of single mode pattern along separate routes.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 vibration damper by piston rod 9, and to be provided support counter-force by spring 2.When vehicle suspension system produces vibration, oscillating load is added on prefabricating load F, the magnetic domain of GMM7 inside is deflected, is changed, and then produce induced voltage by the magnetic flux of GMM7 in coil.After induced voltage conditioning being amplified, obtained the vibration frequency of vehicle suspension system by frequency-discriminating circuit.
As shown in Figure 5, resonance circuitry has maximum impedance at resonant frequency f0 place to the impedance frequency characteristics curve of single mode passive GMM shunt damping, and now RC circuit is in resonant condition, the induction current in coil at utmost can be converted into thermal energy consumption.
As shown in Figure 6, its circuit seals in active current source to main passive hybridization GMM shunt damping control procedure in LRC circuit.Damping control procedure is similar along separate routes for the Passive Control working procedure of this circuit and above-mentioned passive GMM, and its ACTIVE CONTROL process is then the oscillating signal generation vibration reduction control signal according to sensing, is applied to coil 6 rear driving GMM7 to realize the ACTIVE CONTROL vibrated.The main passive hybridization GMM controlled control that damping controls along separate routes can make structure more stable, and ACTIVE CONTROL can realize better control effects.
The GMM mentioned herein is super magnetostriction material is Terfeol-D; above-mentioned embodiment is used for explaining and the present invention is described; instead of limit the invention; in the protection domain of spirit of the present invention and claim; the any amendment make the present invention and change, all fall into protection scope of the present invention.
Claims (3)
1. a vehicle suspension vibration damper, is characterized in that, comprises urceolus and soft magnetic bodies inner core, described; The two ends of soft magnetic bodies inner core are connected with piston rod with guide piston respectively, and guide piston is fixed on urceolus by spring element, for being provided with copper parietal layer inside urceolus;
Soft magnetic bodies inner tube installation has GMM, and the two ends up and down of its GMM are connected with upper permanent magnet with lower permanent magnet respectively, and its periphery is wound with coil,
Control circuit system involving vibrations analysis controling circuit and GMM control circuit;
Vibration analysis control circuit is made up of coil, signal condition amplification circuit, frequency-discriminating circuit and vibration damping control circuit;
Described GMM control circuit is by coil, resistance
r, current source
i,tunable capacitor
c x form,
One end of resistance R connects the common port of single-pole double-throw switch (SPDT), and an output terminal of single-pole double-throw switch (SPDT) connects current source
ia end, another output terminal of double-pole switch and current source
i'sone end that b end connects electric capacity connects.
2. a kind of vehicle suspension vibration damper according to claim 1, is characterized in that described spring element is Rectangular Spring.
3. a kind of vehicle suspension vibration damper according to claim 1, is characterized in that, described GMM is Terfeol-D.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410644036.3A CN104455140B (en) | 2014-11-14 | 2014-11-14 | Vehicle suspension vibration damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410644036.3A CN104455140B (en) | 2014-11-14 | 2014-11-14 | Vehicle suspension vibration damper |
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| CN104455140A true CN104455140A (en) | 2015-03-25 |
| CN104455140B CN104455140B (en) | 2017-12-08 |
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|---|---|---|---|
| CN201410644036.3A Active CN104455140B (en) | 2014-11-14 | 2014-11-14 | Vehicle suspension vibration damper |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105644291A (en) * | 2016-03-24 | 2016-06-08 | 厦门理工学院 | Novel fully-active suspension apparatus and vehicle |
| CN112392888A (en) * | 2020-11-11 | 2021-02-23 | 清华大学 | Magnetic liquid vibration damper |
Citations (5)
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|---|---|---|---|---|
| JP2005335455A (en) * | 2004-05-25 | 2005-12-08 | Ntn Corp | Bearing device for wheel |
| CN201155832Y (en) * | 2008-01-02 | 2008-11-26 | 东莞精诚电子有限公司 | Air humidifier |
| CN101686055A (en) * | 2008-09-25 | 2010-03-31 | 凌阳科技股份有限公司 | Frequency synthetic system with self-corrective loop stability and band width |
| CN101915283A (en) * | 2010-08-06 | 2010-12-15 | 浙江大学 | Magneto-rheological combined damping control method and device |
| CN102158228A (en) * | 2011-04-19 | 2011-08-17 | 复旦大学 | Very low voltage millimeter wave injection-locked dichotomous frequency divider |
-
2014
- 2014-11-14 CN CN201410644036.3A patent/CN104455140B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005335455A (en) * | 2004-05-25 | 2005-12-08 | Ntn Corp | Bearing device for wheel |
| CN201155832Y (en) * | 2008-01-02 | 2008-11-26 | 东莞精诚电子有限公司 | Air humidifier |
| CN101686055A (en) * | 2008-09-25 | 2010-03-31 | 凌阳科技股份有限公司 | Frequency synthetic system with self-corrective loop stability and band width |
| CN101915283A (en) * | 2010-08-06 | 2010-12-15 | 浙江大学 | Magneto-rheological combined damping control method and device |
| CN102158228A (en) * | 2011-04-19 | 2011-08-17 | 复旦大学 | Very low voltage millimeter wave injection-locked dichotomous frequency divider |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105644291A (en) * | 2016-03-24 | 2016-06-08 | 厦门理工学院 | Novel fully-active suspension apparatus and vehicle |
| CN105644291B (en) * | 2016-03-24 | 2019-12-03 | 厦门理工学院 | Full Active suspension device and automobile |
| CN112392888A (en) * | 2020-11-11 | 2021-02-23 | 清华大学 | Magnetic liquid vibration damper |
| CN112392888B (en) * | 2020-11-11 | 2021-06-08 | 清华大学 | Magnetic liquid vibration damper |
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|---|---|
| CN104455140B (en) | 2017-12-08 |
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| CB03 | Change of inventor or designer information |
Inventor after: Cheng Xuexiao Inventor after: He Jiahai Inventor after: Shang Qingdong Inventor after: He Jixiao Inventor before: Sun Xin |
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Effective date of registration: 20171107 Address after: 276500 No. 1 Rizhao East Road, Juxian Economic Development Zone, Shandong, Rizhao City Applicant after: The new energy vehicles Co. Ltd. Address before: 221100 Pizhou City, Xuzhou City, the town of canal Youth Road East Applicant before: Sun Xin |
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Address after: 276500 No. 1 Rizhao East Road, Juxian Economic Development Zone, Shandong, Rizhao City Patentee after: The New Energy Automobile Co. Ltd. Address before: 276500 No. 1 Rizhao East Road, Juxian Economic Development Zone, Shandong, Rizhao City Patentee before: The new energy vehicles Co. Ltd. |