CN103758913A - Mixed mode magneto-rheological shock absorber - Google Patents
Mixed mode magneto-rheological shock absorber Download PDFInfo
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- CN103758913A CN103758913A CN201410051435.9A CN201410051435A CN103758913A CN 103758913 A CN103758913 A CN 103758913A CN 201410051435 A CN201410051435 A CN 201410051435A CN 103758913 A CN103758913 A CN 103758913A
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- piston rod
- vibration damper
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Abstract
A mixed mode magneto-rheological shock absorber comprises a magnetic structure, a piston rod, a guide seat and a work cylinder. An annular damping channel is formed between an electromagnetic piston and a cylinder barrel, a magnet exciting coil is fixedly embedded in the middle of the piston, the magnetic structure of the single-stage excitation mixed type magneto-rheological shock absorber is formed, the magnet exciting coil passes through the piston rod, the piston, the damping channel and a cylinder wall to form a closed magnet loop, and a magnetic field is generated in the damping channel. Through the design of a clearance, viscous damping force for maintaining a magnetorheological fluid damper even in a failure can be generated, the damper has the failed-safe characteristic, meanwhile, the sealing part is improved, the structure of the shock absorber is simplified, the sealing effect is enhanced, and the work stability of the shock absorber is improved.
Description
Technical field
The invention belongs to the vibration damping control field of automotive engineering, be specifically related to a kind of mixed mode magneto-rheological vibration damper.
Background technique
Magnetic flow liquid is the intellectual material that a kind of yield stress and viscosity can change with externally-applied magnetic field, there is the features such as quick, reversible, controlled, itself and vibration damper being combined, can make the continuously output of adjusting machinery controllably of vibration damper, is a kind of novel semi-active damper of having very much a prospect.Because the resistance of shock absorber of being combined with magnetic flow liquid is variable, and simple in structure, robustness is good, and power is low, and response is fast, makes it be widely used in field, the especially auto industry fields such as aerospace industry, bridge construction thing.
Existing Magnetic-Rheology Absorber of Automotive Suspension System is generally comprised of cylinder body, piston rod, electromagnetic piston, movable piston and Sealing, but there is following some problem: 1. for the asymmetry problem of tension and compression damping force on vehicle, all to adopt valve to mate mostly, and the opening of valve cannot accurately be controlled, thereby the controllable damping force that can not control accurately in real time single kind of traditional pattern of magneto-rheological vibration damper 2. and can provide as flow pattern, squeeze mode is all subject to the restriction of structural design, the good damping of performance magnetic flow liquid not.3. the gap of magneto-rheological vibration damper between active chamber and piston is as damp channel, in vibration damper to-and-fro motion process, easily cause the out of line phenomenon of piston rod and cylinder barrel, piston rod tilts with respect to cylinder body, rod seal circle is subject to monolateral pressure distortion large, easily weares and teares and causes leakage.
Summary of the invention
In order to solve above-mentioned problems of the prior art, the present invention is achieved through the following technical solutions: a kind of mixed mode magneto-rheological vibration damper, mainly by magnetic structure, piston rod 2, guide holder 6 and clutch release slave cylinder 8 form.Between described electromagnetic piston 9 and cylinder barrel 8, form annular damp channel, field coil 11 is embedded in piston intermediate portion admittedly, forms the magnetic structure that single-stage encourages hybrid magneto-rheological vibration damper.
Described piston rod and clutch release slave cylinder are selected 20 steel, because 20 steel are not wear-resisting, need carburizing and quenching to improve hardness and wear resistance to improve it, piston 9 is selected ferrocobalt, ferrocobalt has high saturated magnetic induction intensity, and field coil forms closed magnetic loop by piston rod 2, piston 9, damp channel, casing wall 8, in generation magnetic field, damp channel place, and magnetic direction, perpendicular to the mobile direction of magnetic flow liquid, can be given full play to the magnetic rheology effect of magnetic flow liquid.
Described cylinder barrel upper end cap 5 internal diameters have 2 road O type grooves, and external diameter has O type groove, the leak of liquid phenomenon having caused while effectively having improved piston movement one.
Described floating piston 16 end faces have concave groove, have effectively avoided end face discontinuity phenomenon.
Described piston rod 2 adopts single rod structure, fills with epoxy resin glue sealing in piston rod wire outlet hole.
The beneficial effect that the present invention brings: magneto-rheological vibration damper mode of operation of the present invention is single-stage excitation mixed mode, adopts the gap of piston and cylinder barrel as damp channel, adopts rational guiding device simultaneously, has guaranteed magnetorheological useful effect gap homogeneous.Meanwhile, ingenious permeance and the Magnetic field distribution rule of utilizing material, selects 20 steel at piston rod and clutch release slave cylinder place, and piston is selected ferrocobalt, has improved the validity of Magnetic field distribution.Guide holder particular design, installs piston rod O RunddichtringO more convenient in addition, can avoid the wearing and tearing of O type circle.Wire outlet hole adopts epoxy resin glue sealing, and sealing effect is better.
Accompanying drawing explanation
Fig. 1 is mixed mode magneto-rheological vibration damper structural representation of the present invention.
In figure, 1, suspension ring, 2, piston rod, 3, nut (1), 4, nut (2), 5, left end cap, 6, guide holder, 7, buffer stopper, 8, cylinder barrel, 9, electromagnetic piston, 10, damp channel, 11, spring, 12, pad, 13, bolt, 14, oil tank, 15, rubber band, 16, have an end cap, 17, gas charging valve, 18, bottom, 19 lower lift rings.
Embodiment
Below in conjunction with drawings and the specific embodiments, the present invention will be further described.A mixed mode magneto-rheological vibration damper, comprises upper rings 1, piston rod 2, nut (1) 3, nut (2) 4, left end cap 5, guide holder 6, buffer stopper 7, cylinder barrel 8, electromagnetic piston 9, damp channel 10, spring 11, pad 12, bolt 13, oil tank 14, rubber band 15, right end cap 16, gas charging valve 17, bottom 18, lower lift ring 19.The present embodiment comprises magnetic structure, piston rod 2, guide holder 6 and clutch release slave cylinder 8 form, and by cylinder barrel end cap 5, guide holder 6 and buffer stopper 7 are pressed on the ladder seat of cylinder barrel 8, and the bottom of cylinder barrel 8 is provided with bottom 18, bottom 18 is affixed with lower lift ring 19, and gas charging valve 17 is arranged on cylinder barrel 8.Piston rod 2 is fixed on piston on piston rod by screw thread.The piston rod end opposite upper rings 1 that has been threaded, by upper rings 1 and lower lift ring 19 by vibration damper mounting vehicle suspension, when automobilism produces vibration, piston rod 2 promotes combined electromagnetic piston compression or recovery, magnetic flow liquid produces damping force by magnetic flow liquid passage, make vibration attenuation, by impressed current, change the magnetic intensity of electromagnetic piston 9 and cylinder barrel 8 gap locations, with this, change the viscosity characteristics of magnetic flow liquid.Make vibration damper output damping force size variation, to improve smoothness and the operability of vehicle under different operating modes.
With reference to Fig. 1, in reciprocating motion of the pistons process, while fluid being flowed by rational guide holder 6 at passage place, can not cause the axial of middle magnet case and move radially, while being conducive to vibration damper work, the gap operating mode that magnetic rheology effect occurs does not change, and the stability of magneto-rheological vibration damper work is high.
Claims (5)
1. a mixed mode magneto-rheological vibration damper, mainly by magnetic structure, piston rod (2), guide holder (6) and clutch release slave cylinder (8), formed, it is characterized in that: between described electromagnetic piston (9) and cylinder barrel (8), form annular damp channel, field coil (11) is embedded in piston intermediate portion admittedly, forms the magnetic structure that single-stage encourages hybrid magneto-rheological vibration damper.
2. mixed mode magneto-rheological vibration damper according to claim 1, it is characterized in that: piston rod (2) and clutch release slave cylinder (8) are selected 20 steel, because 20 steel are not wear-resisting, need carburizing and quenching to improve hardness and wear resistance to improve it, piston (9) is selected ferrocobalt, ferrocobalt has high saturated magnetic induction intensity, field coil (11) is by piston rod (2), piston (9), damp channel (10), casing wall (8) forms closed magnetic loop, in damp channel (11), locate to produce magnetic field, and magnetic direction is perpendicular to the mobile direction of magnetic flow liquid, can give full play to the magnetic rheology effect of magnetic flow liquid.
3. mixed mode magneto-rheological vibration damper according to claim 1, is characterized in that: the material of described buffer stopper (7) adopts elastic rubber material to make.
4. mixed mode magneto-rheological vibration damper according to claim 1, is characterized in that: described piston rod (2) adopts single rod structure, fills with epoxy resin glue sealing in described piston rod (2) wire outlet hole.
5. mixed mode magneto-rheological vibration damper according to claim 1, is characterized in that: described floating piston (17) has groove.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410051435.9A CN103758913A (en) | 2014-02-16 | 2014-02-16 | Mixed mode magneto-rheological shock absorber |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410051435.9A CN103758913A (en) | 2014-02-16 | 2014-02-16 | Mixed mode magneto-rheological shock absorber |
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| CN103758913A true CN103758913A (en) | 2014-04-30 |
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| CN201410051435.9A Pending CN103758913A (en) | 2014-02-16 | 2014-02-16 | Mixed mode magneto-rheological shock absorber |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107143606A (en) * | 2017-05-16 | 2017-09-08 | 西北工业大学 | The magnetic field bidirectional modulation method of magnetic structure can be remembered for magneto-rheological vibration damper |
| CN107830102A (en) * | 2017-11-14 | 2018-03-23 | 福建工程学院 | The MR vibration damper of non-magnetic piston rod |
| US10024379B2 (en) | 2015-04-10 | 2018-07-17 | Safran Landing Systems Uk Ltd | Hydraulic shock absorber |
| CN112161017A (en) * | 2020-09-22 | 2021-01-01 | 汕头大学 | Quick response magneto-rheological damper |
| CN114321256A (en) * | 2020-09-29 | 2022-04-12 | 汪丽 | Asymmetric damping force magneto-rheological shock absorber piston |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008224001A (en) * | 2007-03-15 | 2008-09-25 | Honda Motor Co Ltd | Variable damping force damper |
| JP4754456B2 (en) * | 2006-10-17 | 2011-08-24 | 本田技研工業株式会社 | Hydraulic damper |
| CN102287477A (en) * | 2011-08-15 | 2011-12-21 | 重庆大学 | Magnet-rheological shock absorber for automobile suspension system |
| CN102367858A (en) * | 2011-09-19 | 2012-03-07 | 重庆大学 | Magneto-rheological friction type hybrid damper |
| CN202597575U (en) * | 2012-04-20 | 2012-12-12 | 南京农业大学 | Flow mode magnetorheological damper |
-
2014
- 2014-02-16 CN CN201410051435.9A patent/CN103758913A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4754456B2 (en) * | 2006-10-17 | 2011-08-24 | 本田技研工業株式会社 | Hydraulic damper |
| JP2008224001A (en) * | 2007-03-15 | 2008-09-25 | Honda Motor Co Ltd | Variable damping force damper |
| CN102287477A (en) * | 2011-08-15 | 2011-12-21 | 重庆大学 | Magnet-rheological shock absorber for automobile suspension system |
| CN102367858A (en) * | 2011-09-19 | 2012-03-07 | 重庆大学 | Magneto-rheological friction type hybrid damper |
| CN202597575U (en) * | 2012-04-20 | 2012-12-12 | 南京农业大学 | Flow mode magnetorheological damper |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10024379B2 (en) | 2015-04-10 | 2018-07-17 | Safran Landing Systems Uk Ltd | Hydraulic shock absorber |
| CN107143606A (en) * | 2017-05-16 | 2017-09-08 | 西北工业大学 | The magnetic field bidirectional modulation method of magnetic structure can be remembered for magneto-rheological vibration damper |
| CN107143606B (en) * | 2017-05-16 | 2019-03-29 | 西北工业大学 | The magnetic field bidirectional modulation method of magnetic structure can be remembered for magneto-rheological vibration damper |
| CN107830102A (en) * | 2017-11-14 | 2018-03-23 | 福建工程学院 | The MR vibration damper of non-magnetic piston rod |
| CN112161017A (en) * | 2020-09-22 | 2021-01-01 | 汕头大学 | Quick response magneto-rheological damper |
| CN112161017B (en) * | 2020-09-22 | 2022-08-16 | 汕头大学 | Quick response magneto-rheological damper |
| CN114321256A (en) * | 2020-09-29 | 2022-04-12 | 汪丽 | Asymmetric damping force magneto-rheological shock absorber piston |
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Application publication date: 20140430 |