CN102102731A - Magnetorheological body-based decoupled damping and stiffness controllable hydro-pneumatic spring damping device - Google Patents
Magnetorheological body-based decoupled damping and stiffness controllable hydro-pneumatic spring damping device Download PDFInfo
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- CN102102731A CN102102731A CN 201110047739 CN201110047739A CN102102731A CN 102102731 A CN102102731 A CN 102102731A CN 201110047739 CN201110047739 CN 201110047739 CN 201110047739 A CN201110047739 A CN 201110047739A CN 102102731 A CN102102731 A CN 102102731A
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Abstract
The invention provides a magnetorheological body-based decoupled damping and stiffness controllable hydro-pneumatic spring damping device with a double-cylinder, double-rod and double-piston structure. In the invention, through a special structure design, volumes of the two cylinders are compensated and cancelled out and the magnetorheological fluid is maintained in a state of constant pressure to realize the decoupling of damping and stiffness; on the basis, the controllable damping of a hydro-pneumatic spring can be realized through the controllable characteristic of the magnetorheological body and the stiffness control and further vehicle posture control and the like can be realized through an external pressure control device.
Description
Technical field
The present invention relates to a kind of hydro-pneumatic spring vibration damping equipment new structure that is used for automotive suspension.
Background technique
Automotive suspension has material impact to the dynamic performance of vehicle, makes the decisive link of vehicle handling stability and riding comfort, is therefore always paid attention to by engineering circle.To Active suspension, the development to semi-active suspension shows again from passive suspension, and it is the target that engineering circle continues pursuit that damping, the rigidity of suspension are controlled in real time.
The passive suspension system of traditional mechanical type mostly is made up of vibration damper and helical spring, leaf spring.Rigidity of helical spring is a definite value normally.In order to guarantee the smoothness of vehicle driving on different road surfaces, need the rigidity of suspension softer, thereby need bigger suspension space.For this reason, in passive suspension system, people have designed different variable rate springs and have solved this problem.Such as the helical spring of footpath, the distance of switching political loyalty in becoming, major-minor leaf spring suspension or the like.
From the controllable damping angle, people have studied half active controllable damping suspension system by real time altering damp channels such as electric control valve how much, but owing to complex structure, with high costs, reliability is low, frequency response is not enough etc., and reason is difficult to get the nod; Vehicle suspension half ACTIVE CONTROL system based on magnetorheological (electrorheological) body controllable damping feature development has obtained development energetically in recent years, and has been applied on the senior vehicle of only a few.But ubiquity collocation structure complexity, big, the non-linear problem that is unfavorable for aspects such as controlling by force of sealing difficulty.
Automotive suspension half ACTIVE CONTROL also has the example of using rigidity controllable, generally uses pneumatic spring (or hydro-pneumatic spring), realizes the controllable stiffness characteristic by its gas pressure being carried out real-time regulated.Simultaneously, in isolation mountings such as engine mounting, the rigidity controllable device based on realizations such as magnetic rheology elastic bodies is also arranged, but its controllable stiffness scope is generally less.
Compare with electrorheological fluid controllable damping technology, magnetic flow liquid has higher shear yield stress, adopts current excitation, puncture, Security and the complicated problems such as increasing apparatus of avoiding the excitation of electrorheological fluid high voltage to cause, good to the impurity tolerance, advantage such as temperature range is wide.The Recent study staff development various forms of magnetorheological damping devices, they are based on flowing, shear and pushing three kinds of basic working modes or their integrated mode, by apply the purpose that externally-applied magnetic field reaches real time altering magnetic flow liquid apparent viscosity in damp channel.In order to adapt to the magnetic flow liquid volume-variation that the piston rod turnover causes, generally adopt structures such as accumulator, floating piston to hold/discharge magnetic flow liquid.Therefore the damping characteristic of MR damper is not only relevant with the pressure reduction that damp channel produces, also change relevant with the conducting pressure that accumulator, floating piston produce, therefore MR damper itself has certain hydro-pneumatic spring characteristic, thereby make damping and stiffness characteristics produce coupling, increased the complexity of control algorithm exploitation.When being used for the semi-active suspension vibration control, MR damper need with uses in parallel such as helical spring, to bear car load.
Hydro-pneumatic spring has various ways.Press single cylinder accumulator form, be divided into single air chamber, two air chamber, two-stage pressure type etc.; Whether link to each other by each suspension cylinder of vehicle bridge and can be divided into stand alone type and communication type; By in the vehicle driving process, whether suspension control needs the external energy input to be divided into passive, half hydro pneumatic suspension initiatively and initiatively; Single Air-chamber type hydro-pneumatic spring also has not separated type of oil-gas dividing and oil gas.The damping characteristic of hydro-pneumatic spring is uncontrollable, under the working state of vibration suppression, the piston rod turnover will cause the working solution volume-variation, thereby compression air chamber changes rigidity, the variation in pressure that this stiffness change causes will be transmitted to oil pocket, change damping state, as seen, rigidity, the damping characteristic of hydro-pneumatic spring also intercouple.Hydro-pneumatic spring can be realized rigidity control and car height controlling etc. by external pressure regulator.
As fully visible, the vibration damping equipment in existing suspension vibration suppression field has the hydro-pneumatic spring that is applicable to the large-scale heavy duty vehicle, and the suspension system of vibration damper and helical spring (or leaf spring) combination.No matter which kind of scheme, because the existence of accumulator, their rigidity and damping characteristic intercouple, and damping and stiffness characteristics do not possess controllable characteristics.In order to adapt to growing technical need, magneto-rheological vibration damping system that damping is controlled and the hydro-pneumatic spring of controllable stiffness (pneumatic spring) have obtained paying close attention to widely, but realize that the controlled comprehensively vibration damping equipment of rigidity and damping has prior value undoubtedly.And the decoupling zero of rigidity and damping will significantly simplify the design and the exploitation of vibration damping equipment, and improves the damping and the stiffness characteristics of suspension system respectively, thereby better suppresses the suspension vibration.
Summary of the invention
The invention provides a kind of decoupling type damping and controllable stiffness hydro-pneumatic spring vibration damping equipment based on magnetic rheological body, it adopts the structural type of the two bar double-pistons of twin-tub, on the basis of realizing hydro-pneumatic spring damping and rigidity decoupling zero, realize that by magnetorheological controllable damping technology damping is controlled, realize controllable stiffness by adding other pressure regulators, in conjunction with suitable control algorithm, make the damping property of automotive suspension obtain the essence improvement.Simultaneously, new structure makes the hydro-pneumatic spring oil pocket keep normal pressure, can reduce seal request, compact structure, and cost is lower, helps hydro-pneumatic spring and promotes to medium and small vehicle.
Technological scheme of the present invention is as follows:
A kind of decoupling type damping and controllable stiffness hydro-pneumatic spring vibration damping equipment based on magnetic rheological body, it adopts the structural type of the two bar double-pistons of twin-tub, is rigidly connected between the double piston-rod, simultaneously motion.Described hydro-pneumatic spring has oil cylinder and the cylinder that is arranged side by side.
Be divided into two chambeies up and down by oil cylinder piston in the described oil cylinder, epicoele is an expansion chamber, cavity of resorption is a compression chamber, be wound with electromagnetic coil in the oil cylinder piston periphery, leave the damp channel that is communicated with two chambeies between oil cylinder piston periphery and the inboard wall of cylinder block, in described oil cylinder, be full of magnetic flow liquid, when piston up-down forces fluid to pass through damp channel, form damping force and be used for the dissipates vibration energy.Oil cylinder piston bar one end connects oil cylinder piston, one end is passed by expansion chamber, the lead-in wire of electromagnetic coil is outwards drawn by piston rod, is activated at the damp channel position by impressed current and forms magnetic field, the damping force that produces when being used to control magnetic flow liquid by damp channel.
Also be divided into two chambeies up and down by cylinder piston in the described cylinder, epicoele is a compensated cavity, and cavity of resorption is an atmospheric pressure cavity, in described atmospheric pressure cavity, be full of inert gas, bear vehicle weight, link to each other with external gas pressure regulator simultaneously by suitable air pressure, be full of magnetic flow liquid simultaneously, to realize the control of car appearance.The compensated cavity of described cylinder links to each other by pipeline with the expansion chamber of oil cylinder, and the compensated cavity of cylinder is used for holding oil cylinder because the fluid volume-variation that piston rod moves up and down and causes.Its cylinder piston rod one end connects cylinder piston rod, and the other end is passed by compensated cavity.The lower end of described oil cylinder and cylinder is jointly by cylinder body base stationary housing suspension ring, and cylinder piston rod and oil cylinder piston bar are positioned at the outer end of cylinder body jointly by piston rod connecting plate fixed piston bridle ring.
In order to make oil cylinder working-pressure keep normal pressure, must make the cylinder piston sectional area equal cylinder and oil cylinder piston rod area sum.
Further, on the top of described oil cylinder piston and on the oil cylinder piston bar, pilot valve can be set, be Spielpassung between the periphery of pilot valve and the cylinder wall, on pilot valve, have and hold the hole that magnetic flow liquid passes through, be used for magnetic flow liquid and between compression chamber A and expansion chamber B, flow.
Adopt structure of the present invention, when piston rod movement, the volume that the oil cylinder piston bar arranged/discharged working solution will enter/flow out the compensated cavity of cylinder by connecting tube, and just in time equaling cylinder piston forces gas compression/expansion volume and cylinder piston rod to arrange/discharge the poor of working solution volume, guaranteed no matter how piston moves up and down, the common working solution space that constitutes of the compensated cavity of the compression chamber of oil cylinder, expansion chamber and cylinder can not be compressed or expand, thereby the maintenance oil cylinder working-pressure is a normal pressure.At this moment, because that cylinder piston remains near the pressure of compensated cavity side is constant, the variation in pressure in the atmospheric pressure cavity of cylinder depends on the decrement of cylinder piston fully, also is the amount of exercise of piston rod.Like this, though the rigidity behavior of the damping behavior of oil cylinder or cylinder can accomplish to be independent of each other, full decoupled, thus realize the design respectively of hydro-pneumatic spring damping characteristic and stiffness characteristics, the dynamics of better realizing ideal.
Traditional dydraulic shock absorber, because piston rod turnover oil cylinder causes the incompressible characteristic of volume-variation and liquid, therefore need an accumulator to come the volume of balance working medium (liquid), there is complicated dynamic behavior between accumulator and working solution, absorber damping force is not only relevant with vibrational state with the damp channel design, and is also closely related with the state of accumulator; And for hydro-pneumatic spring, in one form or another, also need accumulator to hold volume-variation, so air chamber pressure also is coupled with the pressure of accumulator.As seen, no matter be traditional dydraulic shock absorber or existing various forms of hydro-pneumatic springs, its stiffness characteristics and damping characteristic be highly coupling all, makes its dynamic behavior very complicated, is unfavorable for realizing the good design of rigidity, damping.The novel damping device that the present invention proposes makes the cylinder piston sectional area equal cylinder and oil cylinder piston rod area sum, no matter where piston is in, the compensated cavity volume that cylinder piston takies/discharges, just the volume that discharges with double piston-rod/take is consistent, it is constant to make that oil cylinder working-pressure remains normality, thereby makes damping and rigidity effect full decoupled.At this moment, can realize the good damping controllable characteristics of hydro-pneumatic spring by damp channel and excitation design merely, then fully by air chamber design and air chamber pressure decision, car appearance control algorithm is simplified in the coupling of elimination and energy storage pressure to stiffness characteristics greatly.
Decoupling type damping and controllable stiffness hydro-pneumatic spring vibration damping equipment based on magnetic rheological body, when realizing damping characteristic and stiffness characteristics decoupling zero, owing to realized the compensation of oil cylinder volume-variation by special construction, can make oil pocket remain normal pressure power, greatly reduce the seal request of oil pocket and two piston rods, thereby the saving cost is easy to realize.
Description of drawings
Fig. 1 is based on the decoupling type damping of magnetic rheological body and controllable stiffness hydro-pneumatic spring vibration damping equipment general structure schematic representation
Fig. 2-I is the oil cylinder piston structure figure based on the decoupling type damping of magnetic rheological body and controllable stiffness hydro-pneumatic spring vibration damping equipment;
Fig. 2-II is the cylinder piston structure figure based on the decoupling type damping of magnetic rheological body and controllable stiffness hydro-pneumatic spring vibration damping equipment.
Embodiment
As shown in Figure 1, this vibration damping equipment comprises cylinder body suspension ring 1, cylinder block base 2, oil cylinder 3, magnetic flow liquid 4, oil cylinder piston 5, electromagnetic coil 6, pilot valve 7, oil cylinder piston bar 8, piston rod connecting plate 9, piston rod suspension ring 10, cylinder piston rod 11, connecting tube 12, cylinder piston sealing 13, cylinder piston 14, cylinder 15, nitrogen 16, air valve 17 etc.Oil cylinder 3 and cylinder 15 are arranged side by side.Wherein oil cylinder 3 is divided into compression chamber A and expansion chamber B together by oil cylinder piston 5 and pilot valve 7, the periphery of oil cylinder piston 5 is wound with electromagnetic coil 6, and the gap that oil cylinder is 3 forms damp channel, and under the impressed current effect, electromagnetic coil 6 forms controllable magnetic field in damp channel; The lead-in wire of electromagnetic coil 6 is guided into outside the device by the through hole (not outpouring among the figure) in the middle of the oil cylinder piston bar 8, is used for the connection of controllable current device; Pilot valve 7 is installed in the top of institute's oil cylinder piston 5 and on oil cylinder piston bar 8, is used for the motion guide of oil cylinder piston 5, and the bigger hole that has magnetic flow liquid to pass through on it is used for magnetic flow liquid and flows between compression chamber A and expansion chamber B.Cylinder 15 is divided into atmospheric pressure cavity C and compensated cavity D by cylinder piston 14, and cylinder piston 14 is sealed by cylinder piston sealing 13, thus nitrogen among the isolation atmospheric pressure cavity C and the magnetic flow liquid among the expansion chamber D.By linking to each other connecting tube 12, the place can be provided with valve in connecting tube 12 between oil cylinder expansion chamber B and the compensation cylinder chamber D, can close the rigidity locking that realizes vibration damping equipment in case of necessity.Can charge and discharge gas to cylinder atmospheric pressure cavity C by air valve 17, to adapt to different vehicle weights; Simultaneously, can link to each other with the external pressure controlling device, the pressure among the atmospheric pressure cavity C is controlled in real time, thereby realize the rigidity control of vibration damping equipment and the real-time control of car appearance by air valve 17.The cross-section area of cylinder piston 14 equals the cross-section area sum of oil cylinder piston bar 8 and cylinder piston rod 11.Oil cylinder piston 6, cylinder piston 9 respectively and need necessary seal arrangement (unreceipted among the figure) between oil cylinder, cylinder, but because oil cylinder keeps normal pressure power, so the seal request of piston rod is not high.The lower end of oil cylinder 3 and cylinder 15 is jointly by cylinder block base 2 stationary housing suspension ring 1, and cylinder piston rod 11 and oil cylinder piston bar 8 are positioned at the outer end of cylinder body jointly by piston rod connecting plate 9 fixed piston bridle rings 11.This vibration damping equipment links to each other with sprung weight, the unsprung weight of vehicle respectively with piston rod suspension ring 11 by cylinder body suspension ring 1.
Fig. 2 is that wherein Fig. 2-I is the oil cylinder piston part based on the decoupling type damping of magnetic rheological body and controllable stiffness hydro-pneumatic spring vibration damping equipment piston structure detailed drawing, and Fig. 2-II is the cylinder piston part.The oil cylinder piston part mainly is made up of oil cylinder 3, oil cylinder piston locking nut 18, elastic washer 19, oil cylinder piston 5, electromagnetic coil 6, pilot valve 7, guide link 20, damper valve plate 21, oil cylinder piston bar 8.Wherein damp channel is the annular space that forms between oil cylinder piston 5 and the oil cylinder 3; Electromagnetic coil 6 lead-in wires are used for the control of damp channel magnetic field by through hole (not outpouring among the figure) directed outward in the middle of the oil cylinder piston bar 8; In order to generate controllable magnetic field, the permeability magnetic material that remanent magnetism such as oil cylinder piston 5 usefulness soft irons are little is made; Controllable magnetic field in the damp channel is used for the apparent viscosity of real time altering damp channel magnetic flow liquid, reaches the purpose of control damping force; Pilot valve 7 and guide link 20 be together for oil cylinder piston bar 8 provides motion guide, in order to avoid piston and oil cylinder 3 bump in the motion; Guide link 20 is made by wear-resisting polytetrafluoroethylmaterial material, the guiding when being used for oil cylinder piston and oil cylinder relative movement; Be processed with a large amount of through holes in the pilot valve, be used for the path of magnetic flow liquid from compression chamber A to expansion chamber B; Damper valve plate 21 is the super thin metal annulus, the damping force when being used to regulate compression and recovery, and less, the bigger damping characteristic requirement of damping force when restoring of damping force can be provided with the multi-disc damper valve plate as required when realizing compression.The cylinder piston part then is made up of cylinder piston rod 11, cylinder piston locking nut 22, elastic washer 23, piston seal 24, cylinder piston 14 and cylinder 15 etc.Piston seal 24 can be any suitable Sealing, is mainly used in nitrogen among the seal isolation atmospheric pressure cavity C and the magnetic flow liquid among the expansion chamber D, because atmospheric pressure cavity C pressure is higher than the pressure among the compensated cavity D, so the one-way seals that comparatively is fit to can be set; For weight reduction, piston 14 can adopt lightweight materials such as aluminum alloy.
The tradition MR damper is when applying big exciting current, magnetic flow liquid is near solidifying in the damp channel, cause magnetic flow liquid can not by and absorbed by accumulator, cause the expansion chamber negative pressure, the damping force retardation phenomenon that occurs in piston commutation moment is called " idle running " phenomenon (the part document is called " unloading " effect).Because decoupling type damping and controllable stiffness hydro-pneumatic spring vibration damping equipment based on magnetic rheological body have been realized cubage compensation by the special construction design, thereby cancelled accumulator, incompressible characteristic based on magnetic flow liquid, when when electromagnetic coil 5 applies big electric current, magnetic flow liquid is except not there being flow passage by damp channel, thereby can avoid common MR damper comparatively ubiquitous " idle running " phenomenon.
Magnetorheological controllable damping realizes adopting the passage but the magnetic structure that is not limited to express among Fig. 2-I and magnetic flow liquid flow, and the corresponding construction of other MR damper all goes for this.Oil cylinder piston among Fig. 2-I and Fig. 2-II, cylinder piston have all adopted nut fastening, can adopt in concrete enforcement but are not limited to this fastening means.Though the piston rod among Fig. 1, Fig. 2-I and Fig. 2-II has adopted same diameter, oil cylinder piston and cylinder piston to be positioned at same height, oil cylinder and cylinder have adopted same diameter, and they can be different in concrete enforcement.Only need satisfy its cross-section area sum for the piston rod area and equal the cylinder piston cross-section area; And the cylinder piston height need be determined according to the stiffness characteristics of vehicle needs, but oil cylinder piston and cylinder piston position need satisfy enough upper and lower displacement spaces are arranged near the equilibrium position.Cylinder bore then is decided by the vehicle weight of needs carrying, and diameter is little then to need higher inflation pressure, so cylinder bore is decided by to seal the maximum gas pressure that can bear generally; Cylinder diameter is decided by the damping characteristic of vehicle needs, because the mobile pressure reduction that causes is certain, the big more then damping force of piston area is big more when piston damp channel two ends.In order to prevent that oil cylinder and cylinder from being injured by external effect, can outside twin-tub, install protecting cover additional.
To sum up, pass through special structural design, remain normal pressure power state based on the decoupling type damping of magnetic rheological body and the magnetic flow liquid in controllable stiffness hydro-pneumatic spring vibration damping equipment oil cylinder compression chamber A, expansion chamber B and the cylinder compensated cavity D, damping characteristic and stiffness characteristics are independent of each other, realize decoupling zero.On this basis, the controllable damping characteristic by magnetic rheological body realizes the controllable damping of novel damping device, realizes the controllable stiffness characteristic by external pressure regulator.
Under external pressure regulator situation, when vehicle remained static, atmospheric pressure cavity pressure was used to bear the load of vehicle, when atmospheric pressure cavity C is inflated, overall height was increased, and spring rate descends; On the contrary, discharge the gas among the atmospheric pressure cavity C, overall height decline, spring rate will be increased.When the air pressure among the atmospheric pressure cavity C of this kind novel damping device that vehicle is installed is implemented unified control, the lifting control of overall height will be realized, and when the atmospheric pressure cavity C of each device in 4 (or more) vibration damping equipments of vehicle suspension independently implemented to charge and discharge gas control system, will realize that the car appearance adjusts function.
Claims (4)
1. decoupling type damping and controllable stiffness hydro-pneumatic spring vibration damping equipment based on a magnetic rheological body, its adopts the structural type of the two bar double-pistons of twin-tub; It is characterized in that: described vibration damping equipment has oil cylinder and the cylinder that is arranged side by side;
Be divided into two chambeies up and down by oil cylinder piston in the described oil cylinder, epicoele is an expansion chamber, cavity of resorption is a compression chamber, be wound with electromagnetic coil in the oil cylinder piston periphery, leave the damp channel that is communicated with two chambeies between oil cylinder piston periphery and the inboard wall of cylinder block, in described oil cylinder, be full of magnetic flow liquid, oil cylinder piston bar one end connects oil cylinder piston, one end is passed by expansion chamber, the lead-in wire of electromagnetic coil is outwards drawn by piston rod, be activated at the damp channel position by impressed current and form magnetic field, the damping force that produces when being used to control magnetic flow liquid by damp channel;
Also be divided into two chambeies up and down in the described cylinder by cylinder piston, epicoele is a compensated cavity, cavity of resorption is an atmospheric pressure cavity, in described atmospheric pressure cavity, be full of inert gas, the compensated cavity of described cylinder links to each other by pipeline with the expansion chamber of oil cylinder, be full of magnetic flow liquid simultaneously, cylinder piston rod one end connects cylinder piston rod, and the other end is passed by compensated cavity;
The cross-section area of described cylinder piston equals the cross-section area sum of oil cylinder piston bar and cylinder piston rod;
The lower end of described oil cylinder and cylinder is jointly by cylinder body base stationary housing suspension ring, and cylinder piston rod and oil cylinder piston bar are positioned at the outer end of cylinder body jointly by piston rod connecting plate fixed piston bridle ring.
2. decoupling type damping and controllable stiffness hydro-pneumatic spring vibration damping equipment based on magnetic rheological body according to claim 1, it is characterized in that: the top of described oil cylinder piston and oil cylinder piston bar are provided with pilot valve, it between the periphery of pilot valve and the cylinder wall Spielpassung, on pilot valve, have and hold the hole that magnetic flow liquid passes through, be used for magnetic flow liquid and between compression chamber A and expansion chamber B, flow.
3. decoupling type damping and controllable stiffness hydro-pneumatic spring vibration damping equipment based on magnetic rheological body according to claim 1 and 2, it is characterized in that: the compensated cavity of described cylinder and the connecting tube between oil cylinder are provided with control valve.
4. decoupling type damping and controllable stiffness hydro-pneumatic spring vibration damping equipment based on magnetic rheological body according to claim 1 and 2 is characterized in that: on the described atmospheric pressure cavity air valve is set, links to each other with external gas pressure regulator by air valve.
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| CN2011100477394A CN102102731B (en) | 2011-02-28 | 2011-02-28 | Magnetorheological body-based decoupled damping and stiffness controllable hydro-pneumatic spring damping device |
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| CN2011100477394A CN102102731B (en) | 2011-02-28 | 2011-02-28 | Magnetorheological body-based decoupled damping and stiffness controllable hydro-pneumatic spring damping device |
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| CN102102731B CN102102731B (en) | 2012-08-01 |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108547908A (en) * | 2018-04-17 | 2018-09-18 | 安徽卓特信息技术有限公司 | A kind of interior wound MR damper of multi-cylinder cylinder linkage |
| CN110107640A (en) * | 2019-05-27 | 2019-08-09 | 江西科技学院 | Dampening arrangement and its control method |
| CN111819092A (en) * | 2018-03-29 | 2020-10-23 | 日立汽车系统株式会社 | Suspension control device |
| CN112878527A (en) * | 2021-02-26 | 2021-06-01 | 同济大学 | Tuned mass damper of nonlinear gas spring |
| CN113074210A (en) * | 2021-03-16 | 2021-07-06 | 广西科技大学 | Passive magnetorheological vibration damper |
| CN114233792A (en) * | 2021-12-18 | 2022-03-25 | 新乡市新华液压机械有限公司 | Piston rod structure for hydro-pneumatic spring |
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| US7445094B1 (en) * | 2005-10-11 | 2008-11-04 | The United States Of America As Represented By The Secretary Of The Air Force | Passive magneto-rheological vibration isolation apparatus |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111819092A (en) * | 2018-03-29 | 2020-10-23 | 日立汽车系统株式会社 | Suspension control device |
| CN111819092B (en) * | 2018-03-29 | 2023-05-23 | 日立安斯泰莫株式会社 | Suspension control device |
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| CN110107640B (en) * | 2019-05-27 | 2024-02-09 | 江西科技学院 | Shock absorber device and control method thereof |
| CN112878527A (en) * | 2021-02-26 | 2021-06-01 | 同济大学 | Tuned mass damper of nonlinear gas spring |
| CN112878527B (en) * | 2021-02-26 | 2022-09-20 | 同济大学 | Tuned mass damper of nonlinear gas spring |
| CN113074210A (en) * | 2021-03-16 | 2021-07-06 | 广西科技大学 | Passive magnetorheological vibration damper |
| CN114233792A (en) * | 2021-12-18 | 2022-03-25 | 新乡市新华液压机械有限公司 | Piston rod structure for hydro-pneumatic spring |
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