CN105952834A - Shear valve type magnetorheological damper and parameter optimization method thereof - Google Patents

Shear valve type magnetorheological damper and parameter optimization method thereof Download PDF

Info

Publication number
CN105952834A
CN105952834A CN201610561984.XA CN201610561984A CN105952834A CN 105952834 A CN105952834 A CN 105952834A CN 201610561984 A CN201610561984 A CN 201610561984A CN 105952834 A CN105952834 A CN 105952834A
Authority
CN
China
Prior art keywords
piston
inner cylinder
antivibrator
cylinder tube
valve type
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201610561984.XA
Other languages
Chinese (zh)
Other versions
CN105952834B (en
Inventor
何银铜
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Beijing Machinery Equipment Research Institute
Original Assignee
Beijing Machinery Equipment Research Institute
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Beijing Machinery Equipment Research Institute filed Critical Beijing Machinery Equipment Research Institute
Priority to CN201610561984.XA priority Critical patent/CN105952834B/en
Publication of CN105952834A publication Critical patent/CN105952834A/en
Application granted granted Critical
Publication of CN105952834B publication Critical patent/CN105952834B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
    • 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • 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
    • F16F2224/00—Materials; Material properties
    • F16F2224/04—Fluids
    • F16F2224/045—Fluids magnetorheological

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

The invention relates to a shear valve type magnetorheological damper and a parameter optimization method thereof. The shear valve type magnetorheological damper comprises an outer cylinder barrel (4A), inner cylinder barrels (4B), a piston rod (7), a piston (6A), coils (5) and magnetorheological fluid (3). The number of the inner cylinder barrels (4B) is multiple. The inner cylinder barrels (4B) are the same in outer diameter and height and different in thickness. Piston rings (6B) are installed at the end of the piston (6A) and can be disassembled and replaced. The number of the piston rings (6B) is multiple. The piston rings (6B) are the same in inner diameter and outer diameter and different in thickness. According to the shear valve type magnetorheological damper, the force output range of the damper is adjusted by replacing the piston rings different in thickness and the inner cylinder barrels different in thickness, the effects of being simple and reliable are achieved, and the cost is reduced.

Description

A kind of shearing valve type magneto-rheological antivibrator and parameter optimization method thereof
Technical field
The present invention relates to MR damper technical field, particularly relate to a kind of shearing valve type magneto-rheological antivibrator and ginseng thereof Number optimization method.
Background technology
Vibration can cause the fracture failure of component of machine, the fracture of bridge is collapsed or the deterioration of workman's environment etc. some are non- The consequence of Chang Yanchong, therefore typically requires use amortisseur in the industries such as automobile, building, bridge and railway and carrys out vibration reduction efficiency, The amortisseur used at industry-by-industry is the most various.According to required control power and the input of energy, amortisseur is divided into Active amortisseur, semi-active type amortisseur and passive type amortisseur, wherein general due to its damping effect of passive energy dissipation device Property can not meet people's requirement higher to amortisseur, and active shock is owing to needing bigger control power, energy Input and extremely complex control algolithm also fail to be used widely, and semi-active type amortisseur consumed energy is less and again The shock-absorption quality of system can be improved by the parameter changing self and be paid close attention to widely.
MR damper is the semi-active type amortisseur of a kind of new structure that last decade occurs, wherein shearing valve type magnetic Rheological damper is widely used in every field with its simple structure, the convenient feature of magnetic Circuit Design.Shearing valve type magneto-rheological Antivibrator generally uses the version of piston and cylinder body, by the relative motion of piston Yu cylinder body, piston in extruding cylinder body The magneto-rheological fluid of side so that it is flowed to the opposite side of cylinder piston by gap, is perpendicular to fluid when adding in both sides, gap Behind the magnetic field of flow direction, due to " solidification " of magnetic flow liquid in gap, must make when making magneto-rheological fluid pass through in gap " Gu Change " magnetic flow liquid produce viscoplastic flow, thus produce corresponding damping force.
The scope of exerting oneself of shearing valve type magneto-rheological damping is relevant with the structural parameters of antivibrator, after its structure has designed The scope of exerting oneself can be fixed so that it is cannot change in a wide range, thus limits the use of antivibrator.
Summary of the invention
In view of above-mentioned analysis, it is desirable to provide a kind of shearing valve type magneto-rheological antivibrator and parameter optimization side thereof Method, this antivibrator is provided with piston ring and inner cylinder tube, carrys out damping adjusting device by the piston ring and inner cylinder tube changing different-thickness Scope of exerting oneself.
The purpose of the present invention is mainly achieved through the following technical solutions:
One aspect of the present invention provides a kind of shearing valve type magneto-rheological antivibrator, including: outer cylinder, at the one of described outer cylinder End is sequentially installed with attenuator end cap and top cover labyrinth from outside to inside, and the other end at described outer cylinder is installed the most successively There are base of damper and lower sealing cover；On the described outer cylinder inwall being arranged between described top cover labyrinth and described lower sealing cover Inner cylinder tube, described inner cylinder tube can be dismantled；Be installed in described inner cylinder tube through described attenuator end cap, top cover labyrinth, under Seal the piston rod of lid and base of damper, described piston rod is provided with piston, described piston is provided with coil, piston rod Be provided with wire guide on piston, described coil is drawn in described wire guide；Described top cover labyrinth, lower sealing cover, inner cylinder tube Inwall and piston are formed closes space, is filled with magnetic flow liquid in described closing space；Described inner cylinder tube has multiple, Mei Gesuo State that inner cylinder tube external diameter is identical, the most identical, thickness is different, change piston and inner cylinder tube by changing the inner cylinder tube of different-thickness Between gap, and then change antivibrator working clearance；
Described pistons end is provided with piston ring, described piston ring can dismounting and change, described piston ring has multiple, often Individual described piston ring internal diameter is identical, external diameter is identical, thickness is different, changes described piston by changing the piston ring of different-thickness Effective length, and then change damp channel length.
Further, it is respectively arranged with the groove matched each other mutually, institute inside described top cover labyrinth and described lower sealing cover State inner cylinder tube be stuck in described in the groove that is mutually matched.
Further, described piston two ends are provided with piston ring.
Further, the piston ring thickness at described piston two ends is identical.
Further, described top cover labyrinth, lower sealing cover are provided with O on the inwall of described plunger rod contacts； It is disposed with lattice in described O both sides to enclose and wear ring.
Another aspect of the present invention also provides for the parameter optimization method of a kind of shearing valve type magneto-rheological antivibrator, first, determines The computation model of damping force is:
F m r ( t ) = c 1 u · ( t ) + 12 ηLA p πDh 3 A p u · + 3 Lτ y A p h sgn ( u · )
Wherein, FmrFor damping force,Effective area for piston；τyThe surrender being magnetic flow liquid is strong Degree, is the function controlling electric current i；η is the coefficient of kinetic viscosity of magnetic flow liquid；It is the relative speed between damper piston with cylinder body Degree；L is damp channel length；D is piston diameter；D is piston shaft diameter；H is damp channel gap, and sgn is sign function,For antivibrator inertia force；
Then given parameters D, d,i、τy, η andForm damping force and damp channel gap, damp channel length Functional relationship；
Finally by adjust damp channel gap h, find out given parameters D, d,i、τy, η andIn the case of, Determine optimal damper path clearance h；Afterwards, then change damp channel length L, determine optimization length L；Final design goes out institute Need the scope of exerting oneself of antivibrator.
The present invention has the beneficial effect that:
MR damper of the present invention is provided with piston ring at described pistons end, by changing the work of different-thickness Plug ring changes the effective length of piston, thus changes damp channel length, changes damping force；Owing to damping force is logical with damping Road is directly proportional, it is possible to reach to do the scope of exerting oneself needed by the thickness of change piston ring thickness and inner cylinder tube more flexibly, Overcome the problem that range of exerting oneself when only changing damping clearance is bigger；Therefore piston ring matches with the inner cylinder tube of different-thickness Close, it is possible to mark off the most more flexible scope of exerting oneself, during MR damper uses, it is possible to meet more areas Demand, it is achieved that a kind of antivibrator has multiple scope of exerting oneself, and provides cost savings, simple and reliable, has the biggest practicality.
Other features and advantages of the present invention will illustrate in the following description, and, becoming from description of part Obtain it is clear that or understand by implementing the present invention.The purpose of the present invention and other advantages can be by the explanations write Structure specifically noted in book, claims and accompanying drawing realizes and obtains.
Accompanying drawing explanation
Accompanying drawing is only used for illustrating the purpose of specific embodiment, and is not considered as limitation of the present invention, at whole accompanying drawing In, identical reference marks represents identical parts.
Fig. 1 is MR damper structural representation described in the present embodiment；
Fig. 2 is the relation of damping force and damping clearance；
Fig. 3 is the relation of damping force and damping clearance 0.5mm～1.5mm；
Fig. 4 is the relation of damping force and damp channel length；
Wherein, 1-attenuator end cap, 2A-top cover labyrinth, 2B-lower sealing cover, 3-magnetic flow liquid, 4A-outer cylinder, 4B inner casing Cylinder, 5-coil, 6A-piston, 6B-piston ring, 7-piston rod, 8A-wear ring, 8B-lattice enclose, and 8C-O type circle, at the bottom of 9-antivibrator Seat.
Detailed description of the invention
Specifically describing the preferred embodiments of the present invention below in conjunction with the accompanying drawings, wherein, accompanying drawing constitutes the application part, and Together with embodiments of the present invention for explaining the principle of the present invention.
The embodiment of the present invention provides a kind of shearing valve type magneto-rheological antivibrator, as it is shown in figure 1, include outer cylinder 4A, in institute State the one end in outer cylinder 4A and be fixed with attenuator end cap 1 and top cover labyrinth 2A the most successively, in described outer cylinder 4A The other end be fixed with base of damper 9 and lower sealing cover 2B the most successively, described top cover labyrinth 2A and described lower seal Alternate a certain distance between lid 2B, forms the space of piston movement；
It is provided with cooperate recessed with outer cylinder contact surface inside described top cover labyrinth 2A, described lower sealing cover 2B Groove；Being provided with inner cylinder tube 4B in the described groove cooperated, described inner cylinder tube 4B outer wall is close to the interior of described outer cylinder 4A Wall, can change inner cylinder tube 4B by dismounting top cover labyrinth 2A or lower sealing cover 2B.
Being provided with in described outer cylinder 4A and described piston rod 7 coaxial for outer cylinder 4A, described piston rod 7 two ends pass Described attenuator end cap 1 and base of damper 9, and can be along axis relative to outer cylinder 4A and inner cylinder tube 4B relative motion； Described piston rod 7 is provided with piston 6A, all has certain between the piston 6A left and right sides and top cover labyrinth 2A, lower sealing cover 2B Distance, between piston 6A sidewall and described inner cylinder tube 4B, there is gap, at piston 6A, top cover labyrinth 2A, lower sealing cover 2B, interior It is filled with magnetic flow liquid 3 in the closing space that cylinder barrel 4B is formed, transports when piston rod 7 is relative with inner cylinder tube 4B relative to outer cylinder 4A Time dynamic, the magnetic flow liquid 3 of piston 6A meeting extrusion piston 6A side flows from gap to opposite side；Piston 6A sidewall arranges line Circle groove, described coil recess is tied with coil 5, coil 5 gap that just corresponding piston 6A and inner cylinder tube 4B is formed, and i.e. damps The damp channel gap of device, when magnetic flow liquid flows from gap, the coil 5 of energising can apply magnetic field, magnetic to magnetic flow liquid Rheology liquid 3 presents the Bingham bulk properties of high viscosity, lazy flow under the action of a magnetic field, thus the motion to piston 6A is produced Raw resistance, forms damping force.Being provided with through wire guide on piston rod 7 and piston 6A, described coil 5 is from described wire guide Draw, and extraneous power on, thus reach control coil 5 and be energized or the action of power-off.
Inner cylinder tube 4B has multiple, and each described inner cylinder tube 4B has identical external diameter, and (namely outer cylinder 4A's is interior Footpath), identical length and different thickness (namely there is different internal diameters), so use the inner cylinder tube 4B of different-thickness Time, the width forming gap between inner cylinder tube 4B from piston 6A sidewall also can be different, when other parameters are identical, between damp channel The difference of gap can affect the size of damping force, and when gap is the widest, damp channel gap is the biggest, and damping force is the least, when gap is got over Narrow, damp channel gap is the least, and damping force is the least, and along with the width in gap increases, the degree that damping force reduces also is got over Coming the least, be finally kept essentially constant, therefore when needing different scopes of exerting oneself, the present embodiment antivibrator can be changed not The inner cylinder tube 4B of stack pile is adjusted damp channel gap, the scope thus regulation is exerted oneself.
But when gap is less, the minor variations in damp channel gap but can cause damping force significantly to change, because of This is when needing the process range changed more by a small margin, only carrys out damping adjusting path clearance by the thickness of change inner cylinder tube 4B Not reaching, therefore the present invention is provided with piston ring 6B, described piston ring 6B at the end face of piston 6A and can tear open with piston 6A Unload；Piston ring 6B has multiple, each described piston ring 6B external diameter just as (identical with the external diameter of piston 6A), internal diameter identical (with The external diameter of piston rod 7 is identical), thickness different, antivibrator can use difference by the piston ring 6B of dismounting and change different-thickness The piston ring 6B of thickness, is equivalent to change the effective length of piston 6A, thus changes the damp channel length of antivibrator, makes to live 6A is different from the distance between top cover labyrinth 2A, lower sealing cover 2B for plug, thus when piston rod 7 moves, causes piston 6A to move The difference of stroke, when other parameters are identical, damp channel length and the proportional relation of damping force, damp channel length is more Greatly, damping force is the biggest, and damp channel length is the least, and damping force is the least, therefore for causing, when fine setting gap width, the scope of exerting oneself When amplitude of variation is bigger, the effective long of regulating piston 6A can be carried out by changing the piston ring 6B of different-thickness, change damping logical Road length, thus more refine and more flexible reach required scope of exerting oneself.
Piston ring 6B can be arranged on a side end face of piston 6A, it is also possible to is arranged on the both sides end face of piston 6A, when setting Putting when the both sides end face of piston 6A, the piston ring 6B thickness of both sides can be identical, it is also possible to differs.
Top cover labyrinth 2A, lower sealing cover 2B are provided with O 8C on the contact surface of piston rod 7, depend in back-up ring 8C both sides The secondary lattice that arrange are to enclose 8B and wear ring 8A, and lattice enclose the setting of 8B, wear ring 8A and back-up ring 8C can be further ensured that piston rod 7 Sealing with during top cover labyrinth 2A lower sealing cover 2B relative motion, makes antivibrator have more preferable movable sealing and static seal, increases The reliability of antivibrator.
The parameter optimization method of above-mentioned shearing valve type magneto-rheological antivibrator is specific as follows:
First, the computation model determining damping force is:
F m r ( t ) = c 1 u · ( t ) + 12 ηLA p πDh 3 A p u · + 3 Lτ y A p h sgn ( u · )
Wherein, FmrFor damping force,Effective area for piston；τyIt is the yield strength of magnetic flow liquid, It it is the function controlling electric current i；η is the coefficient of kinetic viscosity of magnetic flow liquid；It it is the relative velocity between damper piston and cylinder body； L is damp channel length；D is piston diameter；D is piston shaft diameter；H is damp channel gap, and sgn is sign function, For antivibrator inertia force；
Then given parameters D, d,i、τy, η andForm damping force and damp channel gap, damp channel length Functional relationship, just determine damper structure parameter as follows:
τyIt is the function of electric current i, the τ corresponding by i valueyIt is worth tabulated below:
i(A) 0 0.5 1 2
τy(N/mm2) 3206 10784 16244 23643
Fig. 2 represents that in piston speed be 0.3m/s, under conditions of a length of 20mm of damp channel, and damping clearance and damping force Relation.It can be seen that along with the increase of damping clearance, increase the circulation area of liquid, antivibrator upper and lower cavity it Between pressure differential reduce so that damping force reduce.
As shown in Figure 3: coil current is 0,0.5A, 1A, 2A time under conditions of, gap size 0.5～1.5mm and damping force Relation:
When damping clearance is 0.5mm, maximum damping force is 298kN, minimum damping force 265kN；
When damping clearance is 0.7mm, maximum damping force is 122kN, minimum damping force 98.3kN；
When damping clearance is 0.9mm, maximum damping force is 66.3kN, minimum damping force 47.4kN；
When damping clearance is 1.1mm, maximum damping force is 42.2kN, minimum damping force 26.8kN；
When damping clearance is 1.3mm, maximum damping force is 29.9kN, minimum damping force 16.8kN；
When damping clearance is 1.5mm, maximum damping force is 22.8kN, minimum damping force 11.4kN；
The damping force of antivibrator is affected very big by gap size 0.5～1.5mm, and maximum damping force is become from 298kN 22.8kN, magnitude differs 15 times, sees Fig. 3.On the premise of machining accuracy allows with cost, damping clearance scope is for being less than 0.7mm, damping force is in 10t level, for a kind of specification；Damping clearance scope is 0.7mm～0.9mm, and damping force is in 5t level, for one Specification；Damping clearance scope is more than 0.9mm, and damping force is less than 5t level, for a kind of specification.It is thus desirable to two kinds of specifications of processing Sleeve.
The piston of processing different size obtains more specifically damping force range.As shown in Figure 4, taking damping clearance is 0.75mm, piston speed is 0.3m/s, coil current is 0,0.5A, 1A, 2A time under conditions of, damp channel length 0～ With the linear relationship of damping force in the range of 20mm.
As a length of 5mm of damp channel, maximum damping force is 23kN, minimum damping force 18.7kN；
As a length of 10mm of damp channel, maximum damping force is 39.4kN, minimum damping force 32kN；
As a length of 15mm of damp channel, maximum damping force is 59N, minimum damping force 48kN；
As a length of 20mm of damp channel, maximum damping force is 79kN, minimum damping force 64.2kN；
It can be seen that along with the increase of damp channel length, the pressure differential between antivibrator upper and lower cavity increases, and damping force is also Increase.During design antivibrator, under conditions of structure allows, the length of damp channel should be increased as far as possible.Work as damping Passage length is that damping force is in 2t level, for a kind of specification less than 5mm；When damp channel length is more than 5mm and less than 10mm, resistance Buddhist nun's power is in 4t level, for a kind of specification；When damp channel length is more than 10mm and less than 15mm, and damping force, in 6t level, is advised for one Lattice；When damp channel length is more than 15mm and less than 20mm, and damping force is in 8t level, for a kind of specification.It is thus desirable to processing three kinds The piston ring of specification.The piston ring of the sleeve of two kinds of specifications and three kinds of specifications is mutually matched, thus reaches required damping force Requirement.Final design goes out required antivibrator.
In sum, embodiments provide a kind of shearing valve type magneto-rheological antivibrator, set at described pistons end It is equipped with piston ring, the damping force rank only changing damp channel gap can be refined further；Owing to damping force is effective with piston Length is directly proportional, it is possible to reach to do the model of exerting oneself needed by the thickness of change piston ring thickness and inner cylinder tube more flexibly Enclose, the problem that range of exerting oneself when overcoming to change damping clearance is bigger；Therefore match with the inner cylinder tube of different-thickness, energy Enough mark off the most more flexible scope of exerting oneself, during MR damper uses, it is possible to meet the need of more areas Ask, it is achieved that a kind of antivibrator has multiple scope of exerting oneself, and provides cost savings, simple and reliable, has the biggest practicality.
The above, the only present invention preferably detailed description of the invention, but protection scope of the present invention is not limited thereto, Any those familiar with the art in the technical scope that the invention discloses, the change that can readily occur in or replacement, All should contain within protection scope of the present invention.

Claims (6)

1. a shearing valve type magneto-rheological antivibrator, including: outer cylinder (4A), in one end of described outer cylinder (4A) from outside to inside Being sequentially installed with attenuator end cap (1) and top cover labyrinth (2A), the other end at described outer cylinder (4A) is pacified the most successively Equipped with base of damper (9) and lower sealing cover (2B)；It is arranged between described top cover labyrinth (2A) and described lower sealing cover (2B) Described outer cylinder (4A) inwall on inner cylinder tube (4B), described inner cylinder tube (4B) can be dismantled；It is installed on described inner cylinder tube (4B) through described attenuator end cap (1), top cover labyrinth (2A), lower sealing cover (2B) and the piston rod of base of damper (9) in (7), described piston rod (7) is provided with piston (6A), described piston (6A) is provided with coil (5), piston rod (7) and piston (6A) being provided with wire guide on, described coil (5) is drawn in described wire guide；Described top cover labyrinth (2A), lower sealing cover (2B), inner cylinder tube (4B) inwall and piston (6A) formed and close space, be filled with magnetic flow liquid (3) in described closing space；Institute Stating inner cylinder tube (4B) and have multiple, each described inner cylinder tube (4B) external diameter is identical, the most identical, thickness is different, by changing not The inner cylinder tube (4B) of stack pile changes the gap between piston (6A) and inner cylinder tube (4B), and then changes the workplace of antivibrator Gap；It is characterized in that,
Described piston (6A) end is provided with piston ring (6B), described piston ring (6B) can dismounting and change, described piston ring (6B) having multiple, each described piston ring (6B) internal diameter is identical, external diameter is identical, thickness is different, by changing different-thickness Piston ring (6B) changes the effective length of described piston (6A), and then changes damp channel length.
Shearing valve type magneto-rheological antivibrator the most according to claim 1, it is characterised in that described top cover labyrinth (2A) is with described Lower sealing cover (2B) inner side be respectively arranged with the groove matched each other mutually, described inner cylinder tube (4B) be stuck in described in be mutually matched recessed In groove.
Shearing valve type magneto-rheological antivibrator the most according to claim 1 or claim 2, it is characterised in that described piston (6A) two ends set It is equipped with piston ring (6B).
Shearing valve type magneto-rheological antivibrator the most according to claim 3, it is characterised in that the piston at described piston (6A) two ends Ring (6B) thickness is identical.
Shearing valve type magneto-rheological antivibrator the most according to claim 4, it is characterised in that described top cover labyrinth (2A), under close It is provided with O (8C) on the inwall that capping (2B) contacts with described piston rod (7)；In described O (8C) both sides successively It is provided with Ge Laiquan (8B) and wear ring (8A).
6. a parameter optimization method for shearing valve type magneto-rheological antivibrator as described in any one of claim 1-5, its feature exists In,
First, the computation model determining damping force is:
F m r ( t ) = c 1 u · ( t ) + 12 ηLA p πDh 3 A p u · + 3 Lτ y A p h sgn ( u · )
Wherein, FmrFor damping force,Effective area for piston；τyIt is the yield strength of magnetic flow liquid, is control The function of electric current i processed；η is the coefficient of kinetic viscosity of magnetic flow liquid；It it is the relative velocity between damper piston and cylinder body；L is resistance Buddhist nun's passage length；D is piston diameter；D is piston shaft diameter；H is damp channel gap, and sgn is sign function,For resistance Buddhist nun's device inertia force；
Then given parameters D, d,i、τy, η andForm damping force and damp channel gap, the letter of damp channel length Number relation；
Finally by adjust damp channel gap h, find out given parameters D, d,i、τy, η andIn the case of, determine Go out optimal damper path clearance h；Afterwards, then change damp channel length L, determine optimal damper passage length L；Final design Go out the scope of exerting oneself of required antivibrator.
CN201610561984.XA 2016-07-15 2016-07-15 A kind of shearing valve type magneto-rheological damper and its parameter optimization method Active CN105952834B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201610561984.XA CN105952834B (en) 2016-07-15 2016-07-15 A kind of shearing valve type magneto-rheological damper and its parameter optimization method

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201610561984.XA CN105952834B (en) 2016-07-15 2016-07-15 A kind of shearing valve type magneto-rheological damper and its parameter optimization method

Publications (2)

Publication Number Publication Date
CN105952834A true CN105952834A (en) 2016-09-21
CN105952834B CN105952834B (en) 2018-01-30

Family

ID=56901020

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201610561984.XA Active CN105952834B (en) 2016-07-15 2016-07-15 A kind of shearing valve type magneto-rheological damper and its parameter optimization method

Country Status (1)

Country Link
CN (1) CN105952834B (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106627287A (en) * 2016-11-02 2017-05-10 江苏大学镇江流体工程装备技术研究院 Magneto-rheological six-degree-of-freedom parallel vibration reduction platform for vehicle seat
CN114877006A (en) * 2022-04-07 2022-08-09 深圳市朝上科技有限责任公司 Magnetorheological damper formed by stepped piston cylinder

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020130003A1 (en) * 2001-03-16 2002-09-19 Delphi Technologies, Inc. Magnetorheological dampers with improved wear resistance
CN201778596U (en) * 2010-06-17 2011-03-30 孙炬安 Damper
CN202560922U (en) * 2012-05-10 2012-11-28 株洲时代新材料科技股份有限公司 Double-rod shear-valve type magnetorheological damper with adjustable damping forces
CN103089904A (en) * 2013-01-29 2013-05-08 谭晓婧 Combined cylinder double rod-out magnetorheological damper
CN104534012A (en) * 2015-01-04 2015-04-22 南京航空航天大学 Mageto-rheological damper with changeable working gap and parameter optimizing method thereof

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020130003A1 (en) * 2001-03-16 2002-09-19 Delphi Technologies, Inc. Magnetorheological dampers with improved wear resistance
CN201778596U (en) * 2010-06-17 2011-03-30 孙炬安 Damper
CN202560922U (en) * 2012-05-10 2012-11-28 株洲时代新材料科技股份有限公司 Double-rod shear-valve type magnetorheological damper with adjustable damping forces
CN103089904A (en) * 2013-01-29 2013-05-08 谭晓婧 Combined cylinder double rod-out magnetorheological damper
CN104534012A (en) * 2015-01-04 2015-04-22 南京航空航天大学 Mageto-rheological damper with changeable working gap and parameter optimizing method thereof

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106627287A (en) * 2016-11-02 2017-05-10 江苏大学镇江流体工程装备技术研究院 Magneto-rheological six-degree-of-freedom parallel vibration reduction platform for vehicle seat
CN114877006A (en) * 2022-04-07 2022-08-09 深圳市朝上科技有限责任公司 Magnetorheological damper formed by stepped piston cylinder
CN114877006B (en) * 2022-04-07 2023-03-24 深圳市朝上科技有限责任公司 Magnetorheological damper formed by stepped piston cylinder

Also Published As

Publication number Publication date
CN105952834B (en) 2018-01-30

Similar Documents

Publication Publication Date Title
CN203926577U (en) Magnetorheological fluid shock absorber
DE102013003841B4 (en) vibration
EP2618019A2 (en) Gas spring
DE102014009113A1 (en) FREQUENCY SENSITIVE SHOCK ABSORBER
DE10240568A1 (en) Shock absorption system for two-wheelers
DE102012014583A1 (en) Valve structure of a vibration damper
CN101382177A (en) Two-channel magnetorheological damper with passage gating capability
CN102767589B (en) Magneto-rheological damper adjustable in damping channel height
DE60225865T2 (en) Frequency-dependent damper
CN104481047B (en) The speed displacement external adjustable type viscous damper of two lock
CN104315072B (en) A kind of On A Retrofitted Damper for the adjustable rigidity damping on bullet train
DE102006006482A1 (en) Regulated active-passive vibration absorption device with energy recovery for two-wheelers
CN206617494U (en) A kind of damping adjustable automobile absorber
CN105952834A (en) Shear valve type magnetorheological damper and parameter optimization method thereof
CN108302152B (en) Magnetorheological damper with complex liquid flow channel structure
CN104534012B (en) The MR damper that working clearance is variable and parameter optimization method thereof
CN104806678A (en) Manually adjusted damp-adjustable shock absorber
CN105508494A (en) Anti-impact magnetorheological damper
CN107407364A (en) hydraulic cylinder device
CN205118106U (en) Magneto rheological damper with serial -type flow channel
CN204437164U (en) The MR damper that working clearance is variable
CN105221634B (en) Damper piston structure based on adaptive damping choke valve
CN202756532U (en) Rubber joint with liquid damping rigidity adjusting device
CN103939517A (en) Method for resisting over shock for shock resistant magnetorheological shock absorber
CN203685960U (en) Manually-adjusted damping-adjustable shock absorber

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant