CN103527702A - Magneto-rheological damper suitable for high-speed impact/low-speed vibration control system - Google Patents
Magneto-rheological damper suitable for high-speed impact/low-speed vibration control system Download PDFInfo
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- CN103527702A CN103527702A CN201310508757.7A CN201310508757A CN103527702A CN 103527702 A CN103527702 A CN 103527702A CN 201310508757 A CN201310508757 A CN 201310508757A CN 103527702 A CN103527702 A CN 103527702A
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Abstract
The invention discloses a magneto-rheological damper suitable for a high-speed impact/low-speed vibration control system. The magneto-rheological damper comprises a cylinder body I, a cylinder body II and a piston, wherein the cylinder body I comprises an inner cavity, and the piston can slide along the inner wall of the cylinder body I. The cylinder body I is arranged in the cylinder body II, and an outer cavity is formed between the cylinder body I and the cylinder body II. Magneto-rheological fluid is filled into the inner cavity and the outer cavity, and the inner cavity and the outer cavity are communicated with each other through flowing holes formed in the two ends of the cylinder body I. At least one groove where an electromagnetic coil is wound is formed in the outer wall of the cylinder body I and/or the inner wall of the cylinder body II. On the premise that the external dimension, field current and energy consumption of an existing magneto-rheological damper are not increased, the speed ratio of the movement of the piston to a magneto-rheological fluid flowing channel (the outer cavity) can be effectively lowered, and the requirements for a controllable damping ratio and a controllable speed range of the magneto-rheological damper of the high-speed impact and low-speed vibration control system can be met.
Description
Technical field
The present invention relates to utilize magnetic flow liquid to carry out the technical field of vibration damping, relate in particular to a kind of MR damper that is applicable to high speed impact/low speed vibration control system.
Background technique
MR damper is to make full use of magnetic flow liquid can realize by Newtonian fluid and be changed to semisolid or be changed to the characteristic of Newtonian fluid and the half active actuators part made by semisolid at Millisecond under magnetic fields, it is large that it has yield stress, response is fast, energy consumption is little, the features such as stable performance, can be applicable to the landing system of aircraft/astrovehicle, weaponry is as cannon, the back seat buffer system of machine gun etc., vehicle suspension and pilot set suspension and the train of amphibious (cross-country) vehicle, automobile, motorcycle, bicycle, steamer, building, in sports facility and other impact/vibration control system.Its runner by magnetic flow liquid is arranged on the closed-loop path of controllable magnetic field, when the piston of MR damper and cylinder body generation relative movement, magnetic flow liquid flows in runner, excitation field by control action on flux circuit just can change the shearing stress of magnetic flow liquid, realizes the damping force step-less adjustment of MR damper.
Traditional MR damper, the magnetic flow liquid runner that a ring is normally set on piston head carries out damping force control, this is for the occasion of low speed, such as the suspension system of car or train, at aspects such as controllable damping force, controllable damping ratio and controllable speed scopes, can meet the demands.But according to velocity squared effect, along with the increase of speed (movement velocity of piston) of excitation, the viscous damping force of traditional MR damper is quadratic power ratio and rises, as formula:
A in formula
pfor effective piston area; F
areaction force for compensation air bag; L is single effective shearing ring height; N is the quantity of effective shearing ring; D is the width of ring magnetic flow liquid runner; ρ is the density of magnetic flow liquid; V
dfor the circulation of magnetic flow liquid in ring liquid chunnel hastens; V
fpfor the flow velocity of magnetic flow liquid in outlet and ingress; K
eNand K
eXbe respectively inflow, flow out the factor; K
sCand K
sEbe respectively elbow coefficient in magnetic flow liquid runner; f
dfor the darcy factor based on reynolds' number, it can be described as:
Herein
In formula, ε is the relative roughness of magnetic flow liquid circulation road; η is the viscous damping coefficient of magnetic flow liquid.
The controllable damping of MR damper can be expressed as than D
F in formula
oncan be expressed as
τ in formula
yit is the shear yield stress of magnetic flow liquid.
According to formula (a)-(d), the increase of velocity of piston will significantly reduce controllable damping ratio and the controlled speed scope of MR damper, for the application of (velocity of piston > 1m/s) at a high speed, such as armored vehicle pilot set suspension, go-anywhere vehicle impact energy absorb system and other vehicular traffics, and the fender system of helicopter and aircraft landing system etc., viscous damping force will be very large, this can cause the controllable damping ratio of MR damper to approximate 1, because now viscous damping force approximates total ouput force of MR damper, so in order to meet the application requirements of high-speed applications, generally by sacrificing the controllable damping force of MR damper and the working efficiency of flux circuit, realize, this is because the viscous damping force of traditional MR damper can be realized reduction by reducing the efficiency of the total ouput force of MR damper and field circuit.
Based on Ci， U.S. patent of invention " a kind of double-valve type MR damper " (application number: disclose a kind of two ends in MR damper 7900755B2) " speed up " application requirements that magnetic rheological valve meets controllable damping ratio and controlled speed scope is set respectively.In this double-valve type MR damper, magnetic flow liquid runner is arranged at the joint of the interior outer cylinder body of MR damper, and electromagnetic coil is arranged at the port of the two.Controllable damping ratio and the controlled speed scope of this MR damper can obtain suitable optimization and raising.But, than the application requirements of (speed) scope, also seem awkward for higher speed-controllable damping.
Therefore, meet the control performance requirement of high speed impact and low speed vibration in order to realize MR damper, the performance that the structure that proposes a kind of more superior design principle and MR damper improves MR damper is the current problem that should solve simultaneously.
Summary of the invention
In view of this, the invention provides a kind of MR damper that is applicable to high speed impact/low speed vibration control system, can be under the prerequisite of energy consumption that does not increase MR damper outside dimensions, field current and MR damper, effectively reduce the velocity ratio of piston movement speed and magnetic flow liquid runner, the controllable damping ratio while simultaneously meeting high speed impact and low speed vibration and the requirement of controlled speed scope.
The invention provides a kind of MR damper that is applicable to high speed impact/low speed vibration control system, comprise: containing the cylinder body I of inner chamber body, cylinder body I I and the piston that can slide along the inwall of described cylinder body I, described cylinder body I is arranged between the inherent described cylinder body I of described cylinder body I I, II and forms outer chamber, described inner chamber body and outer chamber are all filled magnetic flow liquid and are communicated with by being arranged on the liquid flow hole at described cylinder body I two ends, at the outer wall of described cylinder body I and/or the inwall of described cylinder body I I, are provided with the groove that at least one is wound with electromagnetic coil.
Further, the outer wall in described cylinder body I is provided with the groove that several are wound with electromagnetic coil.
Further, the inwall at described cylinder body I I is provided with the groove that several are wound with electromagnetic coil.
Further, described cylinder body I, II all adopt high magnetic conductive metal material to make.
Further, described cylinder body I, II arrange with one heart.
Further, the two ends of described cylinder body I are respectively arranged with liquid flow hole described in several.
Further, also comprise: end cap I, II, the two ends of described cylinder body I, II are respectively by described end cap I, II fixing seal.
Further, described end cap I, II are that non-magnetic material is made.
Further, described piston is for singly going out rod piston, and the piston rod of described piston is stretched out by described end cap I, and described MR damper also comprises: be arranged on the compensation air bag on described end cap II.
Further, described piston goes out rod piston for two, and the main piston rod of described piston and auxiliary piston rod stretch out from described end cap I, II respectively.
Beneficial effect of the present invention:
The embodiment of the present invention, owing to forming magnetic flow liquid runner between cylinder body I, II, and in the outer wall of cylinder body I and/or the inwall setting of cylinder body I I, be wound with the groove of electromagnetic coil, therefore the specification of electromagnetic coil can not be subject to the restriction of the size of piston, in other words, this MR damper can be utilized the stroke of piston to greatest extent, and the height that need not need to limit as traditional MR damper of coiling electromagnetic coil on piston electromagnetic coil is to guarantee the stroke of motion of MR damper.The stroke of this MR damper is decoupling zero with shearing effective depth pistion, therefore says that the controllable damping ratio of this MR damper and the scope of controlled speed can increase significantly.Secondly, the null field damping force of MR damper can drop to very little, and this compares scope by the controllable damping that is more conducive to effectively to improve damper.Therefore, with respect to traditional MR damper, can not increase under the prerequisite of the outside dimensions of MR damper, field current and MR damper energy consumption, effectively increase the shearing area of magnetic flow liquid resistance channel, reduce the viscous damping force of MR damper under high-speed energisation condition, at less field current, there is larger controllable damping force as the used time, make controllable damping ratio of the present invention and controlled range wider, the present invention simultaneously has high efficiency, simple in structure, the advantage such as volume is little.
Accompanying drawing explanation
Below in conjunction with drawings and Examples, the invention will be further described:
Fig. 1 is the first embodiment's of the MR damper that is applicable to high speed impact/low speed vibration control system provided by the invention structure sectional view.
Fig. 2 is the A-A sectional drawing in Fig. 1.
Fig. 3 is the second embodiment's of the MR damper that is applicable to high speed impact/low speed vibration control system provided by the invention structure sectional view.
Fig. 4 is the 3rd embodiment's of the MR damper that is applicable to high speed impact/low speed vibration control system provided by the invention structure sectional view.
Embodiment
Please refer to Fig. 1, is the first embodiment's of the MR damper that is applicable to high speed impact/low speed vibration control system provided by the invention structure sectional view, and Fig. 2 is its A-A sectional drawing.
The MR damper 100 of Fig. 1 mainly comprises: two cylinder bodies of installing with one heart, i.e. illustrated cylinder body I 101 and cylinder body I I102, piston 103 and magnetic flow liquid 104.
Wherein, cylinder body I 101 is arranged in cylinder body I I102, and then between forms outer chamber 105.The inside of cylinder body I 101 be illustrated inner chamber body 106.Magnetic flow liquid 104 is filled in inner chamber body 106 and outer chamber 105.At least respectively there is the liquid flow hole 107A, the 107B that for magnetic flow liquid, pass through in two ends 121A, the 121B of cylinder body I 101. Liquid flow hole 107A, 107B on the magnetic flow liquid circulation road 123 forming between cylinder body I 101 and cylinder body I I102, cylinder body I 101 two ends 121A, 121B is used to the fluid communication channels between inner chamber body 106 and outer chamber 105 that circulates in of magnetic flow liquid 104.
The piston 103 that wherein, can be free to slide along cylinder body I 101 comprises piston rod 108 and is connected in the piston head 122 on piston rod 108.The concentric piston ring 109 arranging on piston head 122 is used to packed-piston 103 with cylinder body I 101 and cylinder body I 101 is divided into two parts, i.e. piston rod cavity 106A and piston cavity 106B.When piston 103 moves along piston rod 108 directions in cylinder body I 101, magnetic flow liquid 104 is extruded from the piston rod cavity 106A of inner chamber body 106 and flows out and pass through liquid flow hole 107A to outer chamber 105, along outer chamber 105, through liquid flow hole 107B, arrives piston cavity 106B.When piston 103 moves round about, the flow direction of magnetic flow liquid 104 is contrary.
Wherein, the thickness of the magnetic flow liquid circulation road 123 between cylinder body I 101 and cylinder body I I102 depends on specific applied environment. Liquid flow hole 107A, 107B are meeting under the prerequisite that cylinder body I 101 and cylinder body I I102 are fixing and can expand as much as possible, to reduce to greatest extent the viscous damping force of MR damper 100, maximize its controllable damping ratio and controlled speed scope.The quantity of liquid flow hole 107A, 107B can be but not necessarily be confined to three or four or five, and in Fig. 2, having provided quantity is the cross sectional view of the liquid flow hole 107B of four.
Wherein, MR damper 100 is used upper end cap 110 that cylinder body I 101 and cylinder body I I102 are realized to connection and guarantee the coaxality between the two.The mode of this connection cylinder body I 101 and upper end cap 110 and cylinder body I I102 and upper end cap 110 can be but be not limited to screw thread, fastening piece or other modes.U-RunddichtringO 111 is used to the leakage that packed-piston bar 108 stops magnetic flow liquid 104.O-RunddichtringO 118A, 118B are arranged at respectively between the inwall of upper end cap 110 and cylinder body I I102 and lower end cap 113 and cylinder body I I102 inwall to realize seal action.Drawing wire 112 can be connected with outside controllable electric power through the through hole on upper end cap 110.The sealing means of through hole 110 can be epoxy resin or as the U. S. Patent (patent No.: electrical connection device 7900755B2).Lower end cap 113 makes to keep coaxial between the two as location cylinder body I101 and cylinder body I I102 on the one hand, above compensation air bag 114 can being arranged on the other hand.The volume differences producing when the effect of compensation air bag 114 is compensating piston bar 108 turnover inner cylinder body 101 or during temperature variation.As the U. S. Patent (patent No.: 4811919) the compensation air bag of disclosed floating piston form can be used as volume compensation device equally, and the present embodiment does not limit to.
Wherein, the material of cylinder body I 101 and cylinder body I I102 is preferential selects but is not limited to high permeability material.And the preferential non-magnet materials such as stainless steel or aluminium of selecting of piston rod 108, upper end cap 110 and lower end cap 113.
Wherein, five economize on electricity magnetic coils 115 are wound in five grooves on the outer wall of inner cylinder body 101.Generally speaking, electromagnetic coil quantity, comprise joint number, the number of turn and width, all can determine according to the shearing effective length of MR damper self, the stroke size that makes full use of flux circuit, MR damper and the length of interior outer cylinder body, for example, can be two, three, four, five or more.
Wherein, magnetic line of force 116A, the 116B being produced by the five economize on electricity magnetic coil 115A, 115B, 115C, 115D, the 115E that are connected with field current, 116C, 116D, 116E are as shown in Figure 1. Effective shearing ring 117A, 117B, 117C, 117D, 117E, the 117F of five closed flux circuits and magnetic flow liquid 104 form between cylinder body I 101 and cylinder body I I102.The direction of winding of two adjacent electromagnetic coils should could form five closed flux circuits on the contrary.In outer chamber 105, the direction in magnetic field can be perpendicular to the magnetic flow liquid 104 along effective shearing ring 117A, 117B, 117C, 117D, 117E, 117F circulation.The attribute of the magnetic flow liquid 104 of circulation will be controlled by 115 field currents on electromagnetic coil.The controllable damping force performance of MR damper 100 will determine for two factors: velocity of piston and the magnetic flow liquid 104 that controlled by electromagnetic field.
Please refer to Fig. 3, is the second embodiment's of the MR damper that is applicable to high speed impact/low speed vibration control system provided by the invention structure sectional view.The MR damper 200 of Fig. 3 has similar structure with the MR damper 100 of Fig. 1, difference is: in MR damper 200, five economize on electricity magnetic coil 215A, 215B, 215C, 25D, 215E are wound in the groove on the inwall of cylinder body I I202, and magnetic line of force 216A, the 216B of its generation, 216C, 216D, 216E are as shown in Figure 3. Effective shearing ring 217A, 217B, 217C, 217D, 217E, the 217F of five closed flux circuits and magnetic flow liquid 204 form between cylinder body I 201 and cylinder body I I202.Generally speaking, electromagnetic coil quantity, comprise joint number, the number of turn and width, all can determine according to the shearing effective length of MR damper self, the stroke size that makes full use of flux circuit, MR damper and the length of interior outer cylinder body, for example, can be two, three, four or five or more.
The structure of the structure of the MR damper 200 that Fig. 3 embodiment is given and Fig. 1 embodiment's MR damper 100 has the difference of principle.On the one hand, by electromagnetic coil 215A, 215B, 215C, 215D, 215E are set on the cylinder body I I202 in MR damper 200, not only can reduce the number of turn of electromagnetic coil, so that effectively reduce diameter and the volume of MR damper 200.On the other hand, on cylinder body I I202, coiling electromagnetic coil 215A, 215B, 215C, 215D, 215E can effectively reduce because input the heat that field current produces on electromagnetic coil 215A, 215B, 215C, 215D, 215E when MR damper 200 work, and this structure will be conducive to the heat radiation of MR damper more.Finally, electromagnetic coil 215A, the 215B of MR damper 200,215C, 215D, 215E can be directly pass or carry out by other means effective sealing from cylinder body I I202, and Fig. 1 embodiment is not the same for another example, must pass by the through hole from the upper end cap 110 of MR damper 100, be unfavorable for design and the layout of the internal structure of MR damper.
Please refer to Fig. 4, is the 3rd embodiment's of MR damper provided by the invention structure sectional view.This MR damper 300 from different shown in Fig. 1 and 3 is, it is two rod form structures, two piston 303 both ends of the surface that go out rod-type arrange respectively main piston rod 308 and auxiliary piston rod 314, so just can omit compensation air bag and floating piston in inner cylinder body 301.This structure can reduce effectively by increasing auxiliary piston rod 314 complexity of MR damper 300.Auxiliary piston rod 314 can be easy to realize, and this structure also can be placed in the structure as shown in accompanying drawing 1 and 3.
Fig. 1,3 and 4 embodiment, by changing the structural principle of traditional MR damper, reduce the velocity ratio of piston movement speed and magnetic flow liquid circulation passage (being outer chamber) with the reynolds' number of reduction circulating liquid, and then the controllable damping that improves MR damper than and controlled speed scope, when realizing the half active actuators performance requirement that high speed impact uses, meet low speed vibration control requirement.It is with respect to traditional MR damper, do not increasing under the prerequisite of the outside dimensions of MR damper, field current and MR damper energy consumption, effectively increase the shearing area of liquid flowing resistance passage, reduced the viscous damping force of MR damper under high-speed energisation condition, less field current there is larger controllable damping force as the used time, the controllable damping that makes above-described embodiment than and controlled range wider, there is high efficiency simultaneously, simple in structure, the advantage such as volume is little.
The magnetic flow liquid circulation road (being outer chamber) that above-described embodiment forms is caused by inside and outside two concentric cylinder body gaps, and electromagnetic coil is wound in the groove between the effective cutting length on the inwall of outer cylinder body (being cylinder body I I).Inner core can be used as a part for flux circuit and the guiding of piston of MR damper simultaneously and uses.Be connected with magnetic field that the electromagnetic coil of field current produces from effective shearing ring, the magnetic flow liquid circulation road that passes ring along the radial direction of effective shearing ring arrives on inner cylinder body (being cylinder body I), on inner cylinder body, along the direction contrary with effective shearing ring, arrive another effective shearing ring place, magnetic flow liquid circulation road through ring arrives effective shearing ring, last closed in outer cylinder body.Concentric interior outer cylinder body, magnetic flow liquid circulation road and upper and lower communication port will keep the connection of magnetic flow liquid, and piston head is divided into two inner cylinder body.When piston moves downward, magnetic flow liquid will flow to outer chamber in piston inner cylinder body cavity.When piston moves in the opposite direction, magnetic flow liquid flows round about.Like this, also just realized the controllable damping force performance of MR damper.
The structure of the MR damper that above-described embodiment forms has three special advantages.First, the specification of electromagnetic coil can not be subject to the restriction of the size of piston.In other words, this MR damper can be utilized the stroke of piston to greatest extent, and the height that need not need to limit as traditional MR damper of coiling electromagnetic coil on piston electromagnetic coil is to guarantee the stroke of motion of MR damper.The stroke of this MR damper is decoupling zero with shearing effective depth pistion, therefore says that the controllable damping ratio of this MR damper and the scope of controlled speed can increase significantly.Secondly, the null field damping force of MR damper can drop to very little, and this compares scope by the controllable damping that is more conducive to effectively to improve damper.Finally, the structure of the MR damper that the present invention forms is simpler with respect to traditional MR damper structure, utilize the end cap at MR damper two ends directly the interior outer cylinder body of MR damper to be sealed with fastening, these members and Placement, guaranteed the separate closely connection mutually again of each part of MR damper, such reliable in structure, is applicable to batch production, and cost is low.
Selection for material in the parts of the MR damper of above-described embodiment has certain requirement, as the connection end cap at piston rod, piston head and two ends should limited selection non-magnet material, and interior outer cylinder body is preferably high permeability material, to guarantee the magnetic line of force in field circuit, concentrate as far as possible in the main flux loop distributing through annular magnetic rheology liquid chunnel, give full play to the effect of vertical magnetic field to magnetic flow liquid, effectively control the damping force of MR damper, improve the working efficiency of MR damper, reduce the energy consumption of MR damper.
Finally explanation is, above embodiment is only unrestricted in order to technological scheme of the present invention to be described, although the present invention is had been described in detail with reference to preferred embodiment, those of ordinary skill in the art is to be understood that, can modify or be equal to replacement technological scheme of the present invention, and not departing from aim and the scope of technical solution of the present invention, it all should be encompassed in the middle of claim scope of the present invention.
Claims (10)
1. a MR damper that is applicable to high speed impact/low speed vibration control system, comprise: containing the cylinder body I of inner chamber body, cylinder body I I and the piston that can slide along the inwall of described cylinder body I, described cylinder body I is arranged between the inherent described cylinder body I of described cylinder body I I, II and forms outer chamber, described inner chamber body and outer chamber are all filled magnetic flow liquid and are communicated with by being arranged on the liquid flow hole at described cylinder body I two ends, it is characterized in that: at the outer wall of described cylinder body I and/or the inwall of described cylinder body I I, be provided with the groove that at least one is wound with electromagnetic coil.
2. MR damper as claimed in claim 1, is characterized in that: the outer wall in described cylinder body I is provided with the groove that several are wound with electromagnetic coil.
3. MR damper as claimed in claim 1, is characterized in that: the inwall at described cylinder body I I is provided with the groove that several are wound with electromagnetic coil.
4. MR damper as claimed in claim 1, is characterized in that: described cylinder body I, II all adopt high magnetic conductive metal material to make.
5. MR damper as claimed in claim 1, is characterized in that: described cylinder body I, II arrange with one heart.
6. MR damper as claimed in claim 1, is characterized in that: the two ends of described cylinder body I are respectively arranged with liquid flow hole described in several.
7. the MR damper as described in any one in claim 1-6, is characterized in that: also comprise: end cap I, II, the two ends of described cylinder body I, II are respectively by described end cap I, II fixing seal.
8. MR damper as claimed in claim 7, is characterized in that: described end cap I, II are that non-magnetic material is made.
9. MR damper as claimed in claim 7, is characterized in that: described piston is for singly going out rod piston, and the piston rod of described piston is stretched out by described end cap I, and described MR damper also comprises: be arranged on the compensation air bag on described end cap II.
10. MR damper as claimed in claim 7, is characterized in that: described piston goes out rod piston for two, and the main piston rod of described piston and auxiliary piston rod stretch out from described end cap I, II respectively.
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005054847A (en) * | 2003-08-01 | 2005-03-03 | Univ Kanagawa | Viscous variable fluid shock absorber |
| JP2006017228A (en) * | 2004-07-01 | 2006-01-19 | Kawasaki Heavy Ind Ltd | Magnetic viscous fluid flow damper |
| JP2008208885A (en) * | 2007-02-26 | 2008-09-11 | Univ Kanagawa | Viscous variable fluid damper |
| CN101878379A (en) * | 2007-09-28 | 2010-11-03 | 通用汽车环球科技运作公司 | Bi-fold valve-type magnetorheological fluid energy absorbing device |
| WO2013059951A1 (en) * | 2011-10-27 | 2013-05-02 | Pontificia Universidad Catolica De Chile | Magnetorheological damper |
| CN203532614U (en) * | 2013-10-24 | 2014-04-09 | 合肥工业大学 | Magneto-rheological damper suitable for high-speed impact/low-speed vibration control system |
-
2013
- 2013-10-24 CN CN201310508757.7A patent/CN103527702B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005054847A (en) * | 2003-08-01 | 2005-03-03 | Univ Kanagawa | Viscous variable fluid shock absorber |
| JP2006017228A (en) * | 2004-07-01 | 2006-01-19 | Kawasaki Heavy Ind Ltd | Magnetic viscous fluid flow damper |
| JP2008208885A (en) * | 2007-02-26 | 2008-09-11 | Univ Kanagawa | Viscous variable fluid damper |
| CN101878379A (en) * | 2007-09-28 | 2010-11-03 | 通用汽车环球科技运作公司 | Bi-fold valve-type magnetorheological fluid energy absorbing device |
| WO2013059951A1 (en) * | 2011-10-27 | 2013-05-02 | Pontificia Universidad Catolica De Chile | Magnetorheological damper |
| CN203532614U (en) * | 2013-10-24 | 2014-04-09 | 合肥工业大学 | Magneto-rheological damper suitable for high-speed impact/low-speed vibration control system |
Cited By (28)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
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