CN104455140B - Vehicle suspension vibration damper - Google Patents
Vehicle suspension vibration damper Download PDFInfo
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- CN104455140B CN104455140B CN201410644036.3A CN201410644036A CN104455140B CN 104455140 B CN104455140 B CN 104455140B CN 201410644036 A CN201410644036 A CN 201410644036A CN 104455140 B CN104455140 B CN 104455140B
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- vibration
- gmm
- damping
- frequency
- circuit
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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 kind of vehicle suspension system, it is big using giant magnetostrictive material energy density, high conversion efficiency, the advantages of fast response time, giant magnetostrictive material is embedded in vehicle suspension system, vibration reduction control signal is sent by control circuit, drives GMM to offset vibration realizing vibration damping by magnetostrictive effect.The invention has the advantages that simple in construction, response is rapid, and vibration insulating system is good.
Description
Technical field
The present invention relates to a kind of vehicle suspension vibration damper.
Background technology
Vehicle suspension due to flexible member by impact can produce vibration, influence vehicle travel security and ride comfort.
In order to avoid Vibration of Vehicle Suspensions brings detrimental effect, the purpose of vibration damping can be reached in vehicle suspension mounting dampers.
The shock absorber of vehicle suspension is mostly hydraulic shock absorber, and its operation principle is to work as vehicle frame（Or vehicle body）Between vehicle bridge by
When relative motion occurs in vibration, the piston in shock absorber moves up and down, and the fluid of shock absorber intracavitary just repeatedly passes through from a chamber
Cross different holes and flow into another intracavitary.The now friction between hole wall and fluid and the intermolecular interior friction of fluid are to vibrating shape
Into damping force, automobile vibrational energy is set to be converted into fluid heat energy, then be dispersed into by shock absorber in air.
The rigidity and vibration characteristics of above-mentioned traditional spring mass-damp type vehicle suspension vibration damper are superimposed on vehicle
On suspension, and the frequency response characteristic of vehicle suspension is additional on shock absorber, and in the fixation free-running frequency of shock absorber
Show antiresonance feature.The attenuation characteristic when damping of shock absorber can influence vibration frequency more than system antiresonance response,
So as to change the vibration characteristics of system, effective vibration damping is realized.But the resonant frequency of above-mentioned traditional vehicle suspension vibration damper and
Damped coefficient is fixed, and causes shock absorber can not adapt to the Vehicular vibration operating mode of complexity.
Many researchers have carried out the research of self-adaptive damping coefficient shock absorber in recent years, and the damping of these shock absorbers is adaptive
Two methods should substantially be used：First method changes resistance of shock absorber by the hole size between adjusting shock absorber chamber；
Second method realizes the change of resistance of shock absorber by changing the viscosity of fluid in shock absorber.Based on first method, China
Patent of invention 2010105522620 proposes a kind of working cylinder tube wall by traditional double-cylinder hydraulic damper and is drilled with stated number
The circular hole of amount, position and size, change the shock absorber aisle spare that fluid flows through under different operating modes to reach change damping force
Purpose.The upper piston body and lower piston body for the shock absorber that Chinese invention patent 2005100212129 proposes are in corresponding position
The place of putting is each provided with corresponding fluid opening, and at least one in upper piston body and lower piston body and power set
It is connected, can be rotated under the driving of power set, fluid opening is misplaced, change the sectional area of fluid circulation passage, changes
Fluid flows to the total amount flow velocity of another cavity from a cavity, reaches the requirement of adjustment damping.Based on second method, the U.S.
Patent US7112474B2 proposes a kind of magnetorheological adaptive damping device, changes magnetic flow liquid viscosity by adjusting magnetic field, realizes
Resistance of shock absorber size controls.Chinese invention patent 200710068598.8,201010241273.7,201010249025.7 carries
A kind of magneto-rheological combined damping control method and device are gone out, synthesis uses magnetorheological fluid damp control technology and ultra-magnetic telescopic
Material branch damping, realizes resistance of shock absorber control.
The self-adaptive damping coefficient shock absorber of above-mentioned Patent design realizes the adjustable control of damped coefficient, but either logical
Cross the mechanical damping control technology for changing hole size, or magnetorheological fluid damp control technology or giant magnetostrictive material
Branch damping, its resonant frequency are all fixed.Therefore above-mentioned self-adaptive damping coefficient shock absorber can only be narrower humorous
There is higher energy conversion efficiency in vibration frequency bandwidth range, the mechanical energy of vibration is effectively dissipated.Under actual condition, car
The vibration frequency of suspension influences with many factors such as road conditions, loads, is often not at the resonant frequency bandwidth scope of shock absorber,
So that the effectiveness in vibration suppression of shock absorber is deteriorated.To improve effective damping frequency range of shock absorber, it is necessary to design autotracking resonance
The ultra-magnetic telescopic vehicle suspension vibration damper of frequency.
The content of the invention
In view of the above-mentioned problems of the prior art, the present invention provides a kind of vehicle suspension vibration damper, can be to vibration frequency
Rate carries out autotracking, shock absorber is effectively reduced Vibration of Vehicle Suspensions in wider frequency range, and simple in construction,
Response is rapid.
To achieve these goals, the technical solution adopted by the present invention is：A kind of super mangneto of resonant frequency autotracking is stretched
Contracting vehicle suspension vibration absorber, including outer barrel and soft magnetic bodies inner cylinder, it is described；The both ends of soft magnetic bodies inner cylinder respectively with guide piston
It is connected with piston rod, guide piston is fixed on outer barrel by spring element, is provided with a bronze medal parietal layer on the inside of outer barrel；
Soft magnetic bodies inner tube installation has GMM, and its GMM upper and lower ends are connected with lower permanent magnet and upper permanent magnet respectively, outside it
It is surrounded with coil,
Control circuit system includes vibration analysis control circuit and GMM control circuits；
Vibration analysis control circuit is made up of coil, signal condition amplifying circuit, frequency-discriminating circuit and vibration damping control circuit；
Described GMM control circuits are made up of coil, resistance R, current source i, tunable capacitor Cx,
The common port of resistance R one end connection single-pole double-throw switch (SPDT), the output end connection electric current of single-pole double-throw switch (SPDT)
Source i a ends, another output end of double-pole switch are connected electric capacity Cx one end connection with current source i b ends.
Described spring element is Rectangular Spring.
Described GMM is Terfeol-D.
The present invention is based on GMM transduction principles, integrates vibration signal frequency discrimination technology, forms a kind of resonant frequency autotracking
Ultra-magnetic telescopic vehicle suspension vibration damping new technology.The passive GMM branches damping control of the present invention is using resonance circuit in resonance point
When GMM there is the characteristics of maximum conversion efficiency, Vibration of Vehicle Suspensions energy is converted into thermal dissipation.The master of the present invention is passive
GMM branches damping control realizes active damping using GMM, makes to lead passive GMM branches damping control with passive vibration damping collective effect
The effectiveness in vibration suppression of system is more preferable.Above-mentioned vehicle suspension damping technology can carry out autotracking to vibration frequency, make vibration absorber
Suspension System Performance of Vehicle Model can effectively be reduced in wider frequency range, overcome conventional truck suspension oscillation damping method work
The shortcomings that working frequency narrower bandwidth.And the vehicle suspension damping device structure that the present invention designs is simple, response is rapid, Neng Goushi
Answer the needs of vehicle suspension vibration damping under complex working condition.Meanwhile the present invention can be by single-pole double-throw switch (SPDT) system in quilt
Dynamic GMM branches damping control mutually switches with main passive hybridization GMM branch damping controls, and being on the inside of outer barrel can provided with copper parietal layer
Prevent leakage field.
Brief description of the drawings
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 passive GMM branches damping control schematic diagram.
Fig. 5 is the passive GMM shunt impedances-frequency characteristic figure of single mode.
Fig. 6 is main passive hybridization GMM branch damping control schematic diagrames.
In figure：1st, outer barrel, 2, spring, 3, guide piston, 4, soft magnetic bodies inner cylinder, 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.
It is the structured flowchart of the present invention as shown in Figure 1, including vehicle suspension, signal condition amplifying circuit, frequency-discriminating circuit, subtracts
Shake controller；Described vehicle suspension vibration absorber passes to signal condition amplifying circuit by sending GMM transducing signals, and according to
This passes through frequency-discriminating circuit, vibration damping controller；Vibration damping controller is by active damping signal generator and resonance energy consuming circuitry come real
Now active GMM branches damping and the damping of passive GMM branches.Coil, GMM transforming circuits, signal condition amplifying circuit, frequency-discriminating circuit
It is to deflect the magnetic domain brought by vibration in GMM to induce in coil to constitute vibration perception circuit its effect with vibration damping controller
The voltage signal come is coupled to signal condition amplifying circuit through transforming circuit and carries out conditioning amplification, and vehicle is determined by frequency-discriminating circuit
The frequency component of suspension vibration, appropriate vibration reduction strategy is determined according to Vibration Condition on this basis.The vibration meeting of vehicle suspension
Changes of magnetic field is produced by counter magnetostriction effect in GMM7, causes to produce induced voltage in coil 6.Induced voltage signal leads to
After crossing the processing of signal condition amplifying circuit, the vibration frequency of vehicle suspension is determined by frequency-discriminating circuit.Vibration damping controller is according to car
The vibration frequency regulation active damping signal generator and resonance energy consuming circuitry of suspension, realize main passive GMM branches damping control
System.
It is the vibration reduction strategy flow chart of vibration damping controller as shown in Figure 2, vibration damping controller is shaken by what frequency-discriminating circuit obtained
Dynamic frequency determines the frequency distribution of vehicle suspension principal vibration energy.If vibrational energy distribution in a Frequency point, uses
The passive GMM branches damping control of single mode；If vibrational energy distribution is in multiple Frequency points, multi-modal passive GMM points of use
Road damping control.Determine that still leading passive GMM branches using passive GMM branches damping control hinders according to vehicle suspension size simultaneously
Buddhist nun controls.After determining vibration reduction strategy, circuit is switched to required shock absorption circuit by switching switch.On this basis, adjust
Tunable capacitor is saved to adjust the parameters such as the vibration frequency of the resonant frequency of passive GMM branches and active GMM branches and amplitude.
As shown in figure 3, installed in the outer barrel 1 of the ultra-magnetic telescopic vehicle suspension system vibration absorber of resonant frequency autotracking
There is soft magnetic bodies inner cylinder 4, the both ends of soft magnetic bodies inner cylinder 4 are connected with guide piston 3 and piston rod 9 respectively, are fixed on by spring 2 outer
In cylinder 1, the inner side of outer barrel 1 is provided with a bronze medal parietal layer, for magnetic-leakage preventing, the upper and lower ends of the GMM7 in soft magnetic bodies inner cylinder 4
It is connected respectively with lower permanent magnet 5 and upper permanent magnet 8, it is surrounded with coil 6 outside.GMM7, lower permanent magnet 5, soft magnetic bodies inner cylinder 4 and on
Permanent magnet 8 constitutes magnetic loop, and coil 6, signal condition amplifying circuit, frequency-discriminating circuit and vibration damping control circuit constitute vibration point
Analyse control circuit.The common port of resistance R one end connection single-pole double-throw switch (SPDT) 10, an output end of single-pole double-throw switch (SPDT) 10 connect
Current source i a ends are connect, another output end of double-pole switch 10 is connected electric capacity Cx one end connection with current source i b ends.
Coil 6, resistance R, tunable capacitor Cx constitute passive GMM branches damping control circuit.Coil 6, resistance R, electric current
Source i, tunable capacitor Cx constitute main passive hybridization GMM branch damping control circuits.GMM, permanent magnet and soft magnetic bodies inner cylinder are formed
Magnetic loop.
The course of work of the present invention is as follows：
Passive GMM branch damping control processes by the output end of double-pole switch 10 and current source i b ends as shown in figure 4, connected
Electric capacity Cx one end connection is connect, forms the passive GMM branches pattern of single mode.During original state, GMM7 lower permanent magnet 5, on forever
In the presence of magnet 8, its magnetic domain deflects vertically.Prefabricating load F is applied on shock absorber by piston rod 9, and is passed through
Spring 2, which provides, supports counter-force.When vehicle suspension system produces vibration, oscillating load is added on prefabricating load F, makes inside GMM7
Magnetic domain deflect, changed by GMM7 magnetic flux, and then induced voltage is produced in coil.Induced voltage is adjusted
After reason amplification, the vibration frequency of vehicle suspension system is obtained by frequency-discriminating circuit.
The impedance frequency characteristics curve of single mode passive GMM branches damping as shown in figure 5, resonance circuit in resonant frequency
There is maximum impedance, now RC circuits are in resonant condition, can at utmost be converted into the induced-current in coil at f0
Thermal energy consumption.
Main passive hybridization GMM branch damping control processes are as shown in fig. 6, its circuit seals in active current in LRC circuits
Source.The passive control course of work of the circuit is similar with above-mentioned passive GMM branches damping control process, its active control process
It is then that vibration reduction control signal is occurred according to the vibration signal sensed, drives GMM7 to realize the master of vibration after being applied to coil 6
Dynamic control.The controlled control of main passive hybridization GMM branch damping controls can make structure more stable, and active control can be realized more preferably
Control effect.
GMM referred to herein is that giant magnetostrictive material is Terfeol-D, and above-mentioned embodiment is used for explaining
The bright present invention, rather than limit the invention, in the protection domain of spirit and claims of the present invention, to the present invention
Any modifications and changes made, both fall within protection scope of the present invention.
Claims (3)
- A kind of 1. vehicle suspension vibration damper, it is characterised in that including outer barrel and soft magnetic bodies inner cylinder, the two of described soft magnetic bodies inner cylinder End is connected with guide piston and piston rod respectively, and guide piston is fixed on outer barrel by spring element, is provided with copper on the inside of outer barrel Parietal layer；Soft magnetic bodies inner tube installation has GMM, and its GMM upper and lower ends are connected with lower permanent magnet and upper permanent magnet respectively, its periphery Coil is wound with, control circuit system includes vibration analysis control circuit and GMM control circuits；Vibration analysis control circuit is by line Circle, signal condition amplifying circuit, frequency-discriminating circuit and vibration damping control circuit are formed；Described GMM control circuits are by coil, resistance R, current source i, tunable capacitor Cx are formed, the common port of resistance R one end connection single-pole double-throw switch (SPDT), single-pole double-throw switch (SPDT) One output end connection current source i a ends, another output end of double-pole switch are connected one end of electric capacity with current source i b ends Connection, vibration damping control circuit by active damping signal generator and resonance energy consuming circuitry come realize active GMM branches damping and Passive GMM branches damping, coil, GMM transforming circuits, signal condition amplifying circuit, frequency-discriminating circuit and vibration damping controller constitute Its effect of vibration perception circuit is the voltage signal for inducing the magnetic domain brought in GMM by vibration deflection in coil through transformation Circuit is coupled to signal condition amplifying circuit and carries out conditioning amplification, and the frequency point of Vibration of Vehicle Suspensions is determined by frequency-discriminating circuit Amount, vibration damping controller adjust active damping signal generator and resonance energy consuming circuitry according to the vibration frequency of vehicle suspension, realize Main passive GMM branches damping control.
- 2. a kind of vehicle suspension vibration damper according to claim 1, it is characterised in that described spring element is Rectangular Spring.
- 3. a kind of vehicle suspension vibration damper according to claim 1, it is characterised 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 CN104455140A (en) | 2015-03-25 |
| CN104455140B true 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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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105644291B (en) * | 2016-03-24 | 2019-12-03 | 厦门理工学院 | Full Active suspension device and automobile |
| CN112392888B (en) * | 2020-11-11 | 2021-06-08 | 清华大学 | Magnetic liquid vibration damper |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005335455A (en) * | 2004-05-25 | 2005-12-08 | Ntn Corp | Bearing device for wheel |
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2014
- 2014-11-14 CN CN201410644036.3A patent/CN104455140B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
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| CN104455140A (en) | 2015-03-25 |
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| SE01 | Entry into force of request for substantive examination | ||
| 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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| CB03 | Change of inventor or designer information | ||
| TA01 | Transfer of patent application right |
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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| CP01 | Change in the name or title of a patent holder |
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. |
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| CP01 | Change in the name or title of a patent holder |