CN105045986B - The Optimization Design for the composite damping gap magnetorheological damping unit that performance is oriented to - Google Patents
The Optimization Design for the composite damping gap magnetorheological damping unit that performance is oriented to Download PDFInfo
- Publication number
- CN105045986B CN105045986B CN201510396796.1A CN201510396796A CN105045986B CN 105045986 B CN105045986 B CN 105045986B CN 201510396796 A CN201510396796 A CN 201510396796A CN 105045986 B CN105045986 B CN 105045986B
- Authority
- CN
- China
- Prior art keywords
- mrow
- msub
- phi
- magnetic
- magnetic conduction
- 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.)
- Active
Links
Landscapes
- Soft Magnetic Materials (AREA)
- Fluid-Damping Devices (AREA)
Abstract
A kind of Optimization Design for the composite damping gap magnetorheological damping unit being oriented to the present invention relates to performance, comprises the following steps：Obtain demand and required data of the user to performance, determine exterior design parameter and indoor design parameter to be optimized, carry out dimensionless processing and determine occurrence or scope, establish the computation models such as the magnetic field intensity of damping unit, establish the performance model of damping unit, simultaneously running optimizatin function is established to specific damping unit draw ratio, obtain the performance after corresponding Optimal Parameters and optimization, finally in the range of given draw ratio, repeat previous step, draw out corresponding Optimal Parameters and optimization performance sensitivity curve, exterior design parameter is flexibly determined on performance sensitivity curve according to application environment etc.；Performance evaluation of this method to magnetorheological damping unit provides accurate, reliable, clearly nondimensionalization parameter influence curve, and the optimization design to magnetorheological damping unit can be achieved.
Description
Technical field
The present invention relates to magnetic flow liquid and hydraulic damping cell parameters optimization design field, relate more specifically to a kind of performance
The Optimization Design of the magnetorheological damping unit of guiding.
Background technology
Magnetorheological damping unit is a kind of hydraulic control unit designed using magnetic flow liquid effect, is MR valve and magnetic
Core component in rheological damper, can be by changing magnetic of the electric current in magnet exciting coil come controlled loading in magnetic flow liquid
, to change the damping characteristic of fluid, reach flow and pressure drop control.There is the magnetic of annular and disc fluid course simultaneously
Rheology damping unit, due to the design of its composite damping gap and magnetic conduction annulus so that shear surface of the magnetic field to magnetic flow liquid
Product increase, clipped position is appropriate, and magnetic field utilization rate greatly improves, and the response time is greatly reduced, compared to the magnetic current of other structures
Variable damping unit, has a wide range of application, function admirable, has very high practicality.However, the design ginseng of magnetorheological fluid damp unit
It is several that service behaviour is had a very big impact, it is limited and in the case of meeting user's application demand in volume, how optimization design
Parameter causes the performance of magnetorheological damping unit to be optimal, and is industry urgent problem to be solved.
The optimization design of MR valve to the greatest extent may be used mainly with two aspects for criterion first, being obtained in less structure space
The excellent service behaviour of energy；Second, suitable physical dimension is being selected according to actual application environment and performance requirement.However, magnetic current
Variable damping unit has the influence of coupling because it covers three machinery, electromagnetism, fluid fields between its complicated parameter,
Therefore propose that a kind of development of clear, accurate, mathematical optimization models that practicality is high to magnetorheological damping unit is significant.
The optimization design research of initial magnetorheological damping cellular construction is concentrated mainly on approximate to mechanical parameter progress excellent
To change to reach a certain performance, this optimization method have ignored magnetic saturation phenomenon, simplify the complex relationship between all kinds of parameters,
So that optimization accuracy is greatly reduced.Univ Maryland-Coll Park USA once proposed a kind of body to the MR valve of unicoil annular channel
Design of Structural parameters criterion under product qualifications, this method are analyzed from magnetic circuit modeling and obtained not with FInite Element
Magnetic induction intensity under same parameter, but magnetorheological damping performance depends not only on magnetic circuit, is more damped flow passage structure
Influence.Nguyen et al. establishes the performance indications such as the dynamic regulation scope for MR valve of knowing clearly, inlet and outlet pressure drop, to unicoil
Analysis is optimized in runner and twin coil runner respectively, and is changed into the constrained optimization problem of single goal by penalty
Nondimensional unconfinement optimization problem.But this method, the magnetic saturation effect in magnetorheological damping runner is not accounted for, with
And interference problem that may be present between electromagnetism.
The content of the invention
Patent of the present invention provides a kind of optimization design side for the composite damping gap magnetorheological damping unit that performance is oriented to
Method.This method considers machinery, electromagnetism, fluid three aspect factor, establishes the analysis model of magnetorheological damping unit performance, and
It is layered by parameter, cumbersome parameter is classified as indoor design parameter and exterior design parameter.Further pass through nondimensionalization
Processing, it is established that using active damping pressure drop as the Optimized model under the multi-constraint condition of object function, can both solve inside and set
The optimal solution of parameter is counted, while analyzes sensitiveness of the exterior design parameter to performance impact.
The technical solution adopted for the present invention to solve the technical problems is as follows：
The Optimization Design for the composite damping gap magnetorheological damping unit that a kind of performance is oriented to, between the composite damping
Gap magnetorheological damping unit includes coiling sleeve, valve element, coil, connecting pin, non-magnetic pad, upper magnetic conduction annulus, lower magnetic conduction circle
Ring, upper magnetic conduction disk, lower magnetic conduction disk, cylinder body etc.；Valve element, coiling sleeve, coil, cylinder body are sequentially coaxially installed from inside to outside；
Coiling sleeve is coaxially mounted to outside valve element.Upper magnetic conduction disk, lower magnetic conduction disk are arranged on the two of valve element by connecting pin respectively
End, between upper magnetic conduction disk and valve element, non-magnetic pad is lined between lower magnetic conduction disk and valve element, forms disc liquid stream and lead to
Road；Upper magnetic conduction annulus is coaxially mounted to magnetic conduction disk outer portion, lower magnetic conduction annulus is coaxially mounted to lower magnetic conduction disk outer portion, above leads
Annular fluid course is formed respectively between magnetic annulus and upper magnetic conduction disk, between lower magnetic conduction annulus and lower magnetic conduction disk.Coil
It is wound on coiling sleeve；Upper magnetic conduction disk end and lower magnetic conduction disk end are provided with screw thread；The center spool is provided with
Cylindrical shape fluid course, annular fluid course, disc fluid course, cylindrical shape fluid course are sequentially communicated, and are formed complete
Annulus-disk-cylindrical shape composite damping gap.The side of cylinder body is provided with fairlead, and the wire of coil draws from the fairlead
Go out；Cylinder interior sets shoulder hole, and shoulder hole forms step with upper magnetic conduction annulus and coordinated；The coiling sleeve, connecting pin, non-lead
Magnetic insert uses non-magnet material, and upper magnetic conduction annulus, lower magnetic conduction annulus, upper magnetic conduction disk, lower magnetic conduction disk, cylinder body are used and led
Magnetic material；This method comprises the following steps：
Step 1：Obtain the H of magnetic flow liquidMR-τy(magnetic field intensity-shear yield stress) characteristic, BMR-HMR(magnetic induction is strong
Degree-magnetic field intensity) characteristic, the viscosity coefficient η of magnetic flow liquidMRF, magnetic flow liquid saturation magnetic field intensity HMRF,sat, selected lead
The relative permeability μ of magnetic materialsteel；The saturation induction density B of selected permeability magnetic materialsteel,sat, space permeability μ0, magnetic
The maximum functional flow Q and maximum excitation electric current I of rheology damping unit；Copper wire sectional area Aω, copper conductor electricalresistivityρω；Cylinder body
The radius R of outer surface, the performance requirement required by user, including active pressure drop demand Δ PAR,τref, passive pressure drop demand Δ
PAR,ηref, dynamic regulation coefficient demand λref, response time demand Tinref；
Step 2：The external dimensions design parameter of nondimensionalization is determined, includes the draw ratio of damping unitExamine
Consider the practical of damping unit, set in the range of 0.5~3, wherein L is upper magnetic conduction annulus upper surface and lower magnetic conduction annulus following table
The distance between face；
It is determined that and calculate the external electromagnetic design parameter φ of nondimensionalizationIWith external fluid design parameter φQ, wherein,τy,satFor the saturation shear yield stress of magnetic flow liquid, the shearing of magnetic flow liquid is bent
Taking stress can be by formulaObtain, c0、c1、c2、c3、c4For magnetic flow liquid
Fitting parameter, therefore,
Step 3：Determine indoor design parameter to be optimized, including the thickness L of upper magnetic conduction disk and lower magnetic conduction diska, valve element
Radius Rc, annular fluid course width ta, the width t of disc fluid courser(ta=tr), cylinder body thickness th；Cylindrical shape liquid
The radius R of circulation road0, the wall thickness t of coiling sleeveb1, the gap width t of coil and cylinder bodyb2, and by above-mentioned inside to be optimized
Design parameter is converted into Dimensionless Form, and sets occurrence or scope.
Wherein, the width t of annular fluid courseaWith the ratio between outer surface of cylinder block radius R φtaScope be about 0.02~
0.15；The width t of disc fluid courserWith the ratio between outer surface of cylinder block radius R φtrScope be about 0.02~0.15；Valve element
Thickness RCWith the ratio between outer surface of cylinder block radius R scope φRcAbout 0.25~0.7；Magnetic conduction disc thickness LaWith upper magnetic conduction annulus
The ratio between the distance between upper surface and lower magnetic conduction annulus lower surface L φLaScope be about 0.1~0.4；Cylinder body thickness thWith cylinder body
The ratio between appearance radius surface R φthScope be about 0.1~0.4；The radius R of cylindrical shape fluid coursesWith outer surface of cylinder block radius R
The ratio between φRsScope be about 0~0.4, the wall thickness t of coiling sleeveb1With the ratio between outer surface of cylinder block radius R φtb1Scope
About 0~0.15, the gap width t of coil and cylinder bodyb2With the ratio between outer surface of cylinder block radius R φtb2Scope be about 0~0.15；
Step 4：The magnetic field intensity H established in annulus damping clearanceMR,a, shear yield stress τy,a, disk damping gap
In magnetic field intensity HMR,r, shear yield stress τy,rComputation model, it is specific as follows：
Main flux loop is segmented by magnetic conductive media and magnetic flux area shape, calculates each section of magnetic flux area, the magnetic line of force
Length, main flux loop magnetic flux phi is obtained according to the H-B relations of each section of material in magnetic field law and loop0, so as to obtain
Each section of magnetic induction intensityAnd by magnetic induction intensity compared with the saturation induction density of this section of magnetic conductive media, if jth
The magnetic induction intensity of section is more than the saturation induction density B of this section of materialj,sat(when medium is permeability magnetic material, then Bj,sat=
Bsteel,sat, when medium is magnetic flow liquid, then Bj,sat=BMRF,sat), then calculate the saturation flux amount Φ of this sectionj=Bj,sat·
Sj；Wherein SjFor the magnetic flux area of jth section.With ΦjOn the basis of Φ0, with reference to each section of magnetic flux area, recalculate each section of magnetic
InductionMagnetic induction density B until making each sectionjMeet Bj≤Bj,sat, can be obtained by each section of magnetic induction intensity
To each section of magnetic field intensity,Wherein b0、b1、b2、b3、b4For magnetic flow liquid
Fitting parameter；
It can thus be concluded that the magnetic induction intensity to annular runnerThe magnetic field intensity of annular runnerThe Shear Yield Stress of Magnetorheological Fluids of annular runnerThe magnetic induction intensity of disc-shaped runnerDisk
The magnetic field intensity of shape runnerThe magnetic flow liquid of disc-shaped runner is cut
Cut yield stressSMR,aFor the magnetic flux face at annular fluid flow gap
Product, SMR,rFor the magnetic flux area at radial fluid flow gap；
Step 5, performance computation model is established, according to dimensionless group φQ、φI、φLR, in annular fluid flow gap
Magnetic field intensity HMR,a, shear yield stress τy,a, the magnetic field intensity H in radial fluid flow gapMR,r, shear yield stress τy,rEnter
One step obtains the active damping pressure drop Δ P of damping unitAR,τ, passive damping pressure drop Δ PAR,η, dynamic regulation coefficient lambda, the sensitive time
Constant Tin, resistance coil heat power consumption E, wherein,
E=n π ρωφωcφwhφdcφI 2RHMR,sat 2 (4a)
In formula, φωc=1- φRc-φth-φtb1-φtb2, φωh=φLR/n-2φLaφLR-2φtb-2φta, φRd=
φRc+0.5φta, φdc=1+ φRc-φth+φtb1-φtb2；ca、crFor correction factor, value is 2；
Step 6：Majorized function is established, state computation model and performance computation model are input in majorized function, with master
Dynamic damping pressure drop Δ PAR,τInverse be object function, i.e. Jopt=1/ Δ PAR,τ, with the parameter area in step 1 and two and
Inequality (6a) is structure constraint, with Δ PAR,η≤ΔPAR,ηref、Tin≤TinrefWith λ >=λrefFor performance constraints；It is right
Indoor design variable to be optimized assigns initial value；
In formula, hmax、hminIt is true according to the application limitation such as installation by user for the maximum and minimum value of coil length-width ratio
It is fixed；
Using global optimization approach, the optimal value of indoor design parameter under specific exterior design parameter and corresponding is obtained
Meet the optimal performance of above-mentioned constraints.
Step 7：To outside design parameter φLR, N number of point (including end points), φ are chosen from its scopeLR 1~φLR N, make
Its scope N-1 deciles, to φLR 1~φLR NIn each value use step 6, obtain and meet Δ PAR,η≤ΔPAR,ηref、Tin≤
TinrefAnd λ >=λrefThe optimal design parameter φ of performance constraints and structure constraintRc, φth, φta, φLaValue
With the optimal performance calculated according to formula (1a)-(5a), final output φLR~φth, φLR~φRc, φLR~φta, φLR~
φLa4 Optimal Parameters curves, and φLR~Δ PAR,τ、φLR~Δ PAR,η、φLR~λ, φLR~E, φLR~Tin5 excellent
Change performance curve.
If because being unsatisfactory for performance constraints and without Optimal Curve, return to step one, change R value, repeat step
One to six, obtain Optimal Curve.
Step 8：According to given damping unit radius R, the Optimal Parameters curve obtained with reference to step 7, after optimization
Dimensionless group be converted into dimensional parameters, obtain τh、τa、τr、τb1、τb2、RS、RC、L、LaEtc. parameter, damping unit is completed
Optimization design.
The present invention has the advantage that compared with technical background：
The physical dimension of magnetorheological damping unit decides active pressure drop, passive pressure drop, response time of damping unit etc.
Work in every performance, and structural parameters have coupling effect with the influence of fluid parameter and electromagnetic parameter to performance, particularly
Magnetorheological damping unit with composite damping gap, all kinds of parameters are higher to the susceptibility of performance.However, both at home and abroad to magnetic current
The Optimization Design of variable damping unit is only rested on qualitatively in structural analysis aspect, and only single parameter is optimized point
Analysis, mostly selects a certain numerical value in general scope by rule of thumb.Therefore, the present invention has following technique effect：
1. the present invention to start with terms of fluid, structure, electromagnetism three magnetorheological damping unit is established it is complete, accurate,
Reliable analysis model, and establish accurate service behaviour model；
2. the present invention uses nondimensionalization method, analysis model and performance model are simplified, is more intuitively reflected each
Influence of the class parameter to service behaviour；
3. the parameter of model is classified as two classes, i.e. indoor design parameter phi by the present inventionta、φth、φRs、φRc、φta、φtb、
φLa, and exterior design parameter phiLR(structure is related), φI(electromagnetism is related), φF(fluid is related), makes model further bright
It is clear；
4. the present invention both can be applicable to composite damping gap magnetorheological damping unit, versatility is high.
5. the present invention in practical application, can enter row constraint to outside design parameter according to the limitation of external environment condition, applies
Scope is wide.
Brief description of the drawings
Fig. 1 is magnetorheological damping unit optimization design method flow chart；
Fig. 2 is composite damping gap magnetorheological damping cellular construction schematic diagram；
Fig. 3 is composite damping gap magnetorheological damping cellular construction dimension model schematic diagram；
Fig. 4 is that magnetorheological damping location mode variable calculates modeling procedure figure；
Fig. 5 is the optimized dimensions result schematic diagram of the application example 1 of the present invention；
Fig. 6 is the optimization results of property schematic diagram of the application example 1 of the present invention；
In figure, coiling sleeve 1, valve element 2, coil 3, connecting pin 4, non-magnetic pad 5, upper magnetic conduction annulus 6a, lower magnetic conduction circle
Ring 6b, upper magnetic conduction disk 7a, lower magnetic conduction disk 7b, annular fluid course 8, disc fluid course 9, cylindrical shape fluid course
10th, cylinder body 11, piston rod 12.
Embodiment
The present invention is described in further detail below by embodiment.
Example 1, the present embodiment are public from Lord from magnetorheological damping unit as shown in Figures 2 and 3, magnetic flow liquid model
The MRF122EG of department, permeability magnetic material from electrical pure iron DT4, outside maximum excitation electric current I=1A, maximum stream flow Q=8.4 ×
10-4m3/s；Due to outside limited working space, it is desirable to damping unit draw ratioWithin the scope of 1.0~2.8, according to
Information above optimizes magnetorheological damping unit so that performance reaches following requirement：Active pressure drop demand Δ PAR,τref=1MPa, quilt
Dynamic pressure drop demand Δ PAR,ηref=0.35MPa, dynamic regulation coefficient demand λref=10, response time demand Tinref=50ms, tool
Body comprises the following steps：
Step 1, the H- τ (magnetic field intensity-shear yield stress) for obtaining the MRF122EG magnetic flow liquids of Lord companies are special
Property, B-H (magnetic induction intensity-magnetic field intensity) characteristic, the viscosity coefficient η of magnetic flow liquidMR=0.042Pa.s, magnetic flow liquid it is full
Intensity H is answered with magnetic fieldMR,sat=300KA/m, permeability magnetic material saturation induction density Bsat=1.25T, magnetic conductive media it is relative
Magnetic permeability μDT4=2500；Space permeability μ0=4 π × 10-7TmA-1, the maximum functional flow Q=of compound magnetorheological damping unit
8.4×10-4m3/ s and maximum excitation electric current I=1A；Copper wire sectional area Aω=2.463 × 10-7m2, copper conductor resistivityThe radius R=0.025m of the outer surface of cylinder body 11.
Wherein, the relation multinomial of magnetic field intensity and shear strength is obtained by the H- τ property fittings of magnetic flow liquid：
Magnetic induction intensity and the relation multinomial of magnetic field intensity are obtained by the B-H property fittings of magnetic flow liquid：
Step 2, it is determined that with the larger parameter of performance coherence such as active damping pressure drop, it is classified as exterior design ginseng
Number and indoor design parameter to be optimized, and determine occurrence or scope：
Determine the draw ratio of the external dimensions design parameter, i.e. damping unit of nondimensionalizationConsider damping unit
It is practical, set in the range of 1.0~2.8, wherein L be upper magnetic conduction annulus 6a upper surfaces and lower magnetic conduction annulus 6b lower surfaces it
Between distance；
Determine the external electromagnetic design parameter φ of nondimensionalizationIWith fluid design parameter phiQ, and obtained according to step 1
Parameter, it is calculated
Step 3：Determine indoor design parameter (meaning of parameters is shown in Fig. 3) to be optimized, including upper magnetic conduction disk 7a and lower magnetic conduction
Disk 7b thickness La, valve core outer surface radius Rc, annular fluid course width ta, the width t of disc fluid courser(ta
=tr), cylinder body thickness th；The radius R of cylindrical shape fluid course 10S, the wall thickness t of coiling sleeve 1b1, coil 3 and cylinder body 11
Gap width tb2, and above-mentioned internal band optimal design parameter is converted into Dimensionless Form, and set occurrence or scope.
Wherein, the width t of annular fluid courseaWith the ratio between the appearance radius surface R of cylinder body 11 φtaScope be about 0.02~
0.15；The width t of disc fluid courserWith the ratio between the appearance radius surface R of cylinder body 11 φtrScope be about 0.02~0.15；Valve
Core outer surface radius RCWith the ratio between the appearance radius surface R of cylinder body 11 scope φRcAbout 0.25~0.7；Magnetic conduction disc thickness LaWith
The ratio between the distance between upper magnetic conduction annulus 6a upper surfaces and lower magnetic conduction annulus 6b lower surfaces L φLaScope be about 0.1~0.4；Cylinder
Body thickness thWith the ratio between the appearance radius surface R of cylinder body 11 φthScope be about 0.1~0.4；Set the half of cylindrical shape fluid course 10
Footpath RsWith the ratio between the appearance radius surface R of cylinder body 11 φRs=0.16, the wall thickness t of coiling sleeve 1b1With the appearance radius surface R of cylinder body 11
The ratio between φtb1=0.08, the gap width t of coil 3 and cylinder body 11b2With the ratio between the appearance radius surface R of cylinder body 11 φtb2=0.08；
Step 4：The magnetic field intensity H established in annulus damping clearanceMR,r, shear yield stress τy,r, disk damping gap
In magnetic field intensity HMR,a, shear yield stress τy,aState computation model：
Main flux loop is calculated into each section of magnetic flux area by magnetic conductive media and the segmentation of magnetic flux area shape (see Fig. 3),
Magnetic force line length, main flux loop magnetic flux phi is obtained according to the H-B relations of each section of material in magnetic field law and loop0, from
And obtain each section of magnetic induction intensityAnd by the saturation induction density ratio of magnetic induction intensity and this section of magnetic conductive media
Compared with if the magnetic induction intensity of jth section is more than the saturation induction density B of permeability magnetic materialj,sat, then the saturation flux amount of this section is calculated
Φj=Bj,sat·Sj；Wherein SjFor the magnetic flux area of jth section.With ΦjOn the basis of Φ0, with reference to each section of magnetic flux area, count again
Calculate each section of magnetic induction intensityMagnetic induction density B until making each sectionjMeet Bj≤Bsteel,sat, it is specific available
Cyclic program is realized (as shown in Figure 4) by following steps：
(1) to the design parameter φ of inputth, φta, φRc, φRs, φtb1, φtb2, φLa, initial value is assigned, and make φta=
φtr, φtb1=φtb2=φtb, calculating has dimensional parameters ta, th, Rc, La, RS, tb1, tb2, Nc。
(2) by the main flux loop segmentation in magnetorheological damping unit (as shown in Figure 3), every section of magnetic flux face is obtained
Product Si, and each section of magnetic force line length li, according toObtain return flux amount
Φ0；
(3) cyclic program is set, makes j=1；
(4) basisCalculate the magnetic induction intensity of jth section
(5) judge whether the magnetic induction intensity of jth section is less than the saturation induction density of this section of magnetic conductive media (when medium is
During permeability magnetic material, then Bj,sat=Bsteel,sat, when medium is magnetic flow liquid, then Bj,sat=BMRF,sat)：Bj≤Bj,sat, if so,
Then enter step (6), if it is not, then selecting calculating benchmark of the saturation flux amount of jth section as whole magnetic circuit, make Φ0=Bj, satSj, repeat step (3)~(5)；
(6) judge whether j is less than n, i.e.,：J≤n, if so, j=j+1 is then made, repeat step (4)~(6)；If otherwise enter
Step (7)；
(7) magnetic induction intensity of annular runner is calculatedThe magnetic field intensity of annular runnerThe Shear Yield Stress of Magnetorheological Fluids of annular runnerThe induction of disc-shaped runnerDisc
The magnetic field intensity of runnerThe magnetic flow liquid of disc-shaped runner is cut
Cut yield stress
Step 5, performance computation model is established, according to dimensionless group φQ、φI、φLR, in annular fluid flow gap
Magnetic field intensity HMR,a, shear yield stress τy,a, magnetic field intensity H in radial fluid flow gapMR,r, shear yield stress τy,r, enter
One step obtains the active damping pressure drop Δ P of damping unitAR,τ, passive damping pressure drop Δ PAR,η, dynamic regulation coefficient lambda, the sensitive time
Constant Tin, resistance coil heat power consumption E, wherein,
E=n π ρωφωcφwhφdcφI 2RHMR,sat 2 (4a)
In formula, φωc=1- φRc-φth-φtb1-φtb2, φωh=φLR/n-2φLaφLR-2φtb-2φta, φRd=
φRc+0.5φta, φdc=1+ φRc-φth+φtb1-φtb2；ca、crFor correction factor, value is 2；
Step 6：Majorized function is established, state computation model and performance computation model are input in majorized function, with master
Dynamic damping pressure drop Δ PAR,τInverse be object function, i.e. Jopt=1/ Δ PAR,τ, with the parameter area in step 1 and two and
Inequality (6a) is structure constraint, with Δ PAR,η≤ΔPAR,ηref、Tin≤TinrefWith λ >=λrefFor performance constraints；It is right
Indoor design variable to be optimized assigns initial value；
Using global optimization approach, the optimal value of indoor design parameter under specific exterior design parameter and corresponding is obtained
Meet the optimal performance of above-mentioned constraints.
Step 7：From φLRScope in (including end points) choose 10 point φLR 1~φLR 10, by its 9 decile, to φLR 1
~φLR 10In each value use step 6, obtain and meet Δ PAR,η≤ΔPAR,ηref=1MPa, Tin≤Tinref=50ms and λ
≥λrefThe optimal design parameter φ of=10 performance constraints and structure constraintRc, φth, φta, φLaValue and root
The optimal performance calculated according to formula (1)-(5), final output φLR~φth, φLR~φRc, φLR~φta, φLR~φLa4
Optimal Parameters curve, as shown in figure 5, and φLR~Δ PAR,τ、φLR~Δ PAR,η、φLR~λ, φLR~E, φLR~Tin5
Optimize performance curve, as shown in Figure 6.
Step 8：It is illustrated in fig. 5 shown below, user can be more according to actual external demand, and consider performance indications, in curve
On select most suitable point, for example, choose φLRWhen=2.0, specific dimensionless group φ is obtainedRc=0.303, φth=
0.14、φta=0.035, φLa=0.122, according to R=0.025m, with reference to dimensionless formula, by dimensionless design Parameter Switch
Into the design parameter for having dimension, τ is obtainedh=0.35cm, τa=0.09cm, τb1=0.20cm, τb2=0.20cm, RS=
0.40cm、RC=0.76cm, L=5.00cm, La=0.31；By the performance Δ P of the obtained damping unit of this optimization methodAR,τ
=1.85MPa, Δ PAR,η=0.30MPa, Tin=32.3ms, meets user's request, completes the optimization design of the damping unit.
Claims (1)
1. a kind of Optimization Design for the composite damping gap magnetorheological damping unit that performance is oriented to, the composite damping gap
Magnetorheological damping unit includes coiling sleeve (1), valve element (2), coil (3), connecting pin (4), non-magnetic pad (5), upper magnetic conduction
Annulus (6a), lower magnetic conduction annulus (6b), upper magnetic conduction disk (7a), lower magnetic conduction disk (7b), cylinder body (11)；Valve element (2), coiling set
Cylinder (1), coil (3), cylinder body (11) are sequentially coaxially installed from inside to outside；It is outside that coiling sleeve (1) is coaxially mounted to valve element (2)；
Upper magnetic conduction disk (7a), lower magnetic conduction disk (7b) are arranged on the both ends of valve element (2), upper magnetic conduction disk by connecting pin (4) respectively
Between (7a) and valve element (2), non-magnetic pad (5) is lined between lower magnetic conduction disk (7b) and valve element (2), forms disc liquid
Circulation road (9)；Upper magnetic conduction annulus (6a) is coaxially mounted to that magnetic conduction disk (7a) is outside, lower magnetic conduction annulus (6b) is coaxially mounted to
Lower magnetic conduction disk (7b) is outside, between upper magnetic conduction annulus (6a) and upper magnetic conduction disk (7a), lower magnetic conduction annulus (6b) and lower magnetic conduction
Annular fluid course (8) is formed between disk (7b) respectively；Coil (3) is wound on coiling sleeve (1)；Upper magnetic conduction disk (7a)
End and lower magnetic conduction disk (7b) end are provided with screw thread；The valve element (2) is provided centrally with cylindrical shape fluid course (10),
Annular fluid course (8), disc fluid course (9), cylindrical shape fluid course (10) are sequentially communicated, and form complete circle
Ring-disk-cylindrical shape composite damping gap；The side of cylinder body (11) is provided with fairlead, and the wire of coil (3) is from the fairlead
Draw；Shoulder hole is set inside cylinder body (11), and shoulder hole forms step with upper magnetic conduction annulus (6a) and coordinated；The coiling sleeve
(1), connecting pin (4), non-magnetic pad (5) use non-magnet material, upper magnetic conduction annulus (6a), lower magnetic conduction annulus (6b), on lead
Magnetic disk (7a), lower magnetic conduction disk (7b), cylinder body (11) use permeability magnetic material；Characterized in that, this method includes following step
Suddenly：
Step 1：Obtain the H of magnetic flow liquidMR-τyCharacteristic, BMR-HMRThe viscosity coefficient η of characteristic, magnetic flow liquidMRF, magnetic flow liquid
Saturation magnetic field intensity HMRF, sat, selected permeability magnetic material relative permeability μsteel；The saturation induction of selected permeability magnetic material
Intensity BSteel, sat, space permeability μ0, the maximum functional flow Q and maximum excitation electric current I of magnetorheological damping unit；Copper wire is cut
Area Aω, copper conductor electricalresistivityρω；The radius R of cylinder body (11) outer surface, the performance requirement required by user, including actively press
Drop demand Δ PAR, τ ref, passive pressure drop demand Δ PAR, η ref, dynamic regulation coefficient demand λref, response time demand Tinref；HMRFor
Magnetic field intensity, τyFor shear yield stress, BMRMagnetic induction intensity；
Step 2：The external dimensions design parameter of nondimensionalization is determined, includes the draw ratio of damping unitConsider damping
Unit it is practical, set in the range of 0.5~3, wherein L be upper magnetic conduction annulus (6a) upper surface with lower magnetic conduction annulus (6b)
The distance between surface；
It is determined that and calculate the external electromagnetic design parameter φ of nondimensionalizationIWith external fluid design parameter φQ, wherein,τY, satFor the saturation shear yield stress of magnetic flow liquid, the shear yielding of magnetic flow liquid
Stress can be by formulaObtain, c0、c1、c2、c3、c4For the fitting of magnetic flow liquid
Parameter, therefore,
Step 3：Determine indoor design parameter to be optimized, including upper magnetic conduction disk (7a) and the thickness L of lower magnetic conduction disk (7b)a,
Valve element radius Rc, annular fluid course width ta, the width t of disc fluid courser, ta=tr, cylinder body thickness th；Cylindrical shape
The radius R of fluid course (10)0, the wall thickness t of coiling sleeve (1)b1, the gap width t of coil (3) and cylinder body (11)b2, and
By above-mentioned indoor design Parameter Switch to be optimized into Dimensionless Form, and set occurrence or scope；
Wherein, the width t of annular fluid courseaWith the ratio between cylinder body (11) appearance radius surface R φtaScope for 0.02~
0.15；The width t of disc fluid courserWith the ratio between cylinder body (11) appearance radius surface R φtrScope be 0.02~0.15；Valve
Core thickness RCWith the ratio between cylinder body (11) appearance radius surface R scope φRcFor 0.25~0.7；Magnetic conduction disc thickness LaWith upper magnetic conduction
The ratio between the distance between annulus (6a) upper surface and lower magnetic conduction annulus (6b) lower surface L φLaScope be 0.1~0.4；Cylinder body is thick
Spend thWith the ratio between cylinder body (11) appearance radius surface R φthScope be 0.1~0.4；The radius R of cylindrical shape fluid course (10)sWith
The ratio between cylinder body (11) appearance radius surface R φRsScope be 0~0.4, the wall thickness t of coiling sleeve (1)b1With cylinder body (11) outside
The ratio between surface radius R φtb1Scope be 0~0.15, the gap width t of coil (3) and cylinder body (11)b2With cylinder body (11) appearance
The ratio between radius surface R φtb2Scope be 0~0.15；
Step 4：The magnetic field intensity H established in annulus damping clearanceMR, a, shear yield stress τY, a, the magnetic in disk damping gap
Field intensity HMR, r, shear yield stress τY, rComputation model, it is specific as follows：Main flux loop is pressed into magnetic conductive media and magnetic flux
Area shape is segmented, and calculates each section of magnetic flux area, magnetic force line length, according to the H-B of each section of material in magnetic field law and loop
Relation obtains main flux loop magnetic flux phi0, so as to obtain each section of magnetic induction intensityAnd by magnetic induction intensity with
The saturation induction density of this section of magnetic conductive media compares, if the magnetic induction intensity of jth section is more than the saturation induction of this section of material
Intensity BJ, sat, then the saturation flux amount Φ of this section is calculatedj=BJ, sat·Sj；Wherein SjFor the magnetic flux area of jth section；With ΦjFor base
Quasi- Φ0, with reference to each section of magnetic flux area, recalculate each section of magnetic induction intensityUntil making each section of magnetic induction strong
Spend BjMeet Bj≤BJ, sat, each section of magnetic field intensity is can obtain by each section of magnetic induction intensity,Wherein b0、b1、b2、b3、b4For the fitting parameter of magnetic flow liquid；
It can thus be concluded that the magnetic induction intensity to annular runnerThe magnetic field intensity of annular runnerThe Shear Yield Stress of Magnetorheological Fluids of annular runnerThe magnetic induction intensity of disc-shaped runnerDisc
The magnetic field intensity of runnerThe magnetic flow liquid shearing of disc-shaped runner
Yield stressSMR, aFor the magnetic flux area at annular fluid flow gap,
SMR, rFor the magnetic flux area at radial fluid flow gap；
Step 5, performance computation model is established, according to dimensionless group φQ、φI、φLR, the magnetic field in annular fluid flow gap is strong
Spend HMR, a, shear yield stress τY, a, the magnetic field intensity H in radial fluid flow gapMR, r, shear yield stress τY, rFurther
To the active damping pressure drop Δ P of damping unitAR, τ,Passive damping pressure drop Δ PAR, η, dynamic regulation coefficient lambda, sensitive time constant
Tin, resistance coil heat power consumption E, wherein,
<mrow>
<msub>
<mi>&Delta;P</mi>
<mrow>
<mi>A</mi>
<mi>R</mi>
<mo>,</mo>
<mi>&tau;</mi>
</mrow>
</msub>
<mo>=</mo>
<mfrac>
<mrow>
<mn>2</mn>
<msub>
<mi>c</mi>
<mi>a</mi>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>a</mi>
</mrow>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>R</mi>
</mrow>
</msub>
</mrow>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>t</mi>
<mi>a</mi>
</mrow>
</msub>
</mfrac>
<msub>
<mi>t</mi>
<mrow>
<mi>y</mi>
<mo>,</mo>
<mi>a</mi>
</mrow>
</msub>
<mrow>
<mo>(</mo>
<msub>
<mi>H</mi>
<mrow>
<mi>M</mi>
<mi>R</mi>
<mo>,</mo>
<mi>a</mi>
</mrow>
</msub>
<mo>)</mo>
</mrow>
<mo>+</mo>
<mfrac>
<mrow>
<mn>2</mn>
<msub>
<mi>c</mi>
<mi>r</mi>
</msub>
<mrow>
<mo>(</mo>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>R</mi>
<mi>c</mi>
</mrow>
</msub>
<mo>-</mo>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>R</mi>
<mi>s</mi>
</mrow>
</msub>
<mo>)</mo>
</mrow>
</mrow>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>t</mi>
<mi>r</mi>
</mrow>
</msub>
</mfrac>
<msub>
<mi>t</mi>
<mrow>
<mi>y</mi>
<mo>,</mo>
<mi>r</mi>
</mrow>
</msub>
<mrow>
<mo>(</mo>
<msub>
<mi>H</mi>
<mrow>
<mi>M</mi>
<mi>R</mi>
<mo>,</mo>
<mi>r</mi>
</mrow>
</msub>
<mo>)</mo>
</mrow>
<mo>-</mo>
<mo>-</mo>
<mo>-</mo>
<mrow>
<mo>(</mo>
<mn>1</mn>
<mi>a</mi>
<mo>)</mo>
</mrow>
</mrow>
<mrow>
<msub>
<mi>&Delta;P</mi>
<mrow>
<mi>A</mi>
<mi>R</mi>
<mo>,</mo>
<mi>&eta;</mi>
</mrow>
</msub>
<mo>=</mo>
<mfrac>
<mrow>
<mn>12</mn>
<msub>
<mi>&phi;</mi>
<mi>Q</mi>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>a</mi>
</mrow>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>R</mi>
</mrow>
</msub>
<msub>
<mi>&tau;</mi>
<mrow>
<mi>y</mi>
<mo>,</mo>
<mi>s</mi>
<mi>a</mi>
<mi>t</mi>
</mrow>
</msub>
</mrow>
<mrow>
<msup>
<msub>
<mi>&pi;&phi;</mi>
<mrow>
<mi>t</mi>
<mi>a</mi>
</mrow>
</msub>
<mn>3</mn>
</msup>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>R</mi>
<mi>d</mi>
</mrow>
</msub>
</mrow>
</mfrac>
<mo>&lsqb;</mo>
<mn>1</mn>
<mo>+</mo>
<mfrac>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>R</mi>
<mi>d</mi>
</mrow>
</msub>
<mrow>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>a</mi>
</mrow>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>R</mi>
</mrow>
</msub>
</mrow>
</mfrac>
<mi>ln</mi>
<mfrac>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>R</mi>
<mi>c</mi>
</mrow>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>R</mi>
<mi>s</mi>
</mrow>
</msub>
</mfrac>
<mo>+</mo>
<mfrac>
<mrow>
<mi>2</mi>
<msup>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>t</mi>
<mi>a</mi>
</mrow>
</msub>
<mn>3</mn>
</msup>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>R</mi>
<mi>d</mi>
</mrow>
</msub>
</mrow>
<mrow>
<mn>3</mn>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>a</mi>
</mrow>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>R</mi>
</mrow>
</msub>
</mrow>
</mfrac>
<mfrac>
<mrow>
<mo>(</mo>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>R</mi>
</mrow>
</msub>
<mo>-</mo>
<mn>2</mn>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>a</mi>
</mrow>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>R</mi>
</mrow>
</msub>
<mo>-</mo>
<mn>2</mn>
<msub>
<mi>n&phi;</mi>
<mrow>
<mi>t</mi>
<mi>a</mi>
</mrow>
</msub>
<mo>)</mo>
</mrow>
<mrow>
<msup>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>R</mi>
<mi>s</mi>
</mrow>
</msub>
<mn>4</mn>
</msup>
</mrow>
</mfrac>
<mo>&rsqb;</mo>
<mo>-</mo>
<mo>-</mo>
<mo>-</mo>
<mrow>
<mo>(</mo>
<mn>2</mn>
<mi>a</mi>
<mo>)</mo>
</mrow>
</mrow>
<mrow>
<msub>
<mi>T</mi>
<mrow>
<mi>i</mi>
<mi>n</mi>
</mrow>
</msub>
<mo>=</mo>
<mfrac>
<mrow>
<mn>2</mn>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>R</mi>
<mi>d</mi>
</mrow>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>a</mi>
</mrow>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>R</mi>
</mrow>
</msub>
</mrow>
<mrow>
<msub>
<mi>n&phi;</mi>
<mrow>
<mi>d</mi>
<mi>c</mi>
</mrow>
</msub>
</mrow>
</mfrac>
<mfrac>
<mrow>
<msub>
<mi>B</mi>
<mrow>
<mi>M</mi>
<mi>R</mi>
<mo>,</mo>
<mi>a</mi>
</mrow>
</msub>
<msup>
<mi>R</mi>
<mn>2</mn>
</msup>
</mrow>
<mrow>
<msub>
<mi>&rho;</mi>
<mi>&omega;</mi>
</msub>
<msub>
<mi>H</mi>
<mrow>
<mi>M</mi>
<mi>R</mi>
<mo>,</mo>
<mi>s</mi>
<mi>a</mi>
<mi>t</mi>
</mrow>
</msub>
</mrow>
</mfrac>
<mfrac>
<mn>1</mn>
<msub>
<mi>&phi;</mi>
<mi>I</mi>
</msub>
</mfrac>
<mo>-</mo>
<mo>-</mo>
<mo>-</mo>
<mrow>
<mo>(</mo>
<mn>3</mn>
<mi>a</mi>
<mo>)</mo>
</mrow>
</mrow>
E=n π ρωφωcφwhφdcφI 2RHMR, sat2 (4a)
<mrow>
<mi>&lambda;</mi>
<mo>=</mo>
<mfrac>
<mrow>
<msub>
<mi>&Delta;P</mi>
<mrow>
<mi>A</mi>
<mi>R</mi>
<mo>,</mo>
<mi>&tau;</mi>
</mrow>
</msub>
</mrow>
<mrow>
<msub>
<mi>&Delta;P</mi>
<mrow>
<mi>A</mi>
<mi>R</mi>
<mo>,</mo>
<mi>&eta;</mi>
</mrow>
</msub>
</mrow>
</mfrac>
<mo>-</mo>
<mo>-</mo>
<mo>-</mo>
<mrow>
<mo>(</mo>
<mn>5</mn>
<mi>a</mi>
<mo>)</mo>
</mrow>
</mrow>
In formula, φωc=1- φRc-φth-φtb1-φtb2, φωh=φLR/n-2φLaφLR-2φtb-2φta, φRd=φRc+
0.5φta, φdc=1+ φRc-φth+φtb1-φtb2；ca、crFor correction factor, value is 2；
Step 6：Majorized function is established, state computation model and performance computation model are input in majorized function, actively to hinder
Buddhist nun's pressure drop Δ PAR, τInverse be object function, i.e. Jopt=1/ Δ PAR, τ, with the parameter area in step 1 and two and
Formula (6a) is structure constraint, with Δ PAR, η≤ΔPAR, η ref、Tin≤TinrefWith λ >=λrefFor performance constraints；Treat excellent
Change indoor design variable and assign initial value；
<mrow>
<mfenced open = "{" close = "">
<mtable>
<mtr>
<mtd>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>w</mi>
<mi>c</mi>
</mrow>
</msub>
<mo>=</mo>
<mn>1</mn>
<mo>-</mo>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>R</mi>
<mi>c</mi>
</mrow>
</msub>
<mo>-</mo>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>t</mi>
<mi>h</mi>
</mrow>
</msub>
<mo>-</mo>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>t</mi>
<mi>b</mi>
<mn>1</mn>
</mrow>
</msub>
<mo>-</mo>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>t</mi>
<mi>b</mi>
<mn>2</mn>
</mrow>
</msub>
<mo>></mo>
<mn>0</mn>
</mtd>
</mtr>
<mtr>
<mtd>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>w</mi>
<mi>h</mi>
</mrow>
</msub>
<mo>=</mo>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>R</mi>
</mrow>
</msub>
<mo>/</mo>
<mi>n</mi>
<mo>-</mo>
<mn>2</mn>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>a</mi>
</mrow>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>L</mi>
<mi>R</mi>
</mrow>
</msub>
<mo>/</mo>
<mi>n</mi>
<mo>-</mo>
<mn>2</mn>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>t</mi>
<mi>b</mi>
<mn>1</mn>
</mrow>
</msub>
<mo>-</mo>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>t</mi>
<mi>a</mi>
</mrow>
</msub>
<mo>></mo>
<mn>0</mn>
</mtd>
</mtr>
<mtr>
<mtd>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>R</mi>
<mi>c</mi>
</mrow>
</msub>
<mo>-</mo>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>R</mi>
<mi>s</mi>
</mrow>
</msub>
<mo>></mo>
<mn>0</mn>
</mtd>
</mtr>
<mtr>
<mtd>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>w</mi>
<mi>h</mi>
</mrow>
</msub>
<mo>-</mo>
<msub>
<mi>h</mi>
<mrow>
<mi>m</mi>
<mi>a</mi>
<mi>x</mi>
</mrow>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>w</mi>
<mi>c</mi>
</mrow>
</msub>
<mo><</mo>
<mn>0</mn>
</mtd>
</mtr>
<mtr>
<mtd>
<msub>
<mi>h</mi>
<mrow>
<mi>m</mi>
<mi>i</mi>
<mi>n</mi>
</mrow>
</msub>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>w</mi>
<mi>c</mi>
</mrow>
</msub>
<mo>-</mo>
<msub>
<mi>&phi;</mi>
<mrow>
<mi>w</mi>
<mi>h</mi>
</mrow>
</msub>
<mo><</mo>
<mn>0</mn>
</mtd>
</mtr>
</mtable>
</mfenced>
<mo>-</mo>
<mo>-</mo>
<mo>-</mo>
<mrow>
<mo>(</mo>
<mn>6</mn>
<mi>a</mi>
<mo>)</mo>
</mrow>
</mrow>
In formula, hmax、hminFor the maximum and minimum value of coil length-width ratio；
Using global optimization approach, obtain the optimal value of the indoor design parameter under specific exterior design parameter and meet accordingly
The optimal performance of above-mentioned constraints；
Step 7：To outside design parameter φLR, N number of point including end points, φ are chosen from its scopeLR 1~φLR N, make
Its scope N-1 deciles, to φLR 1~φLR NIn each value use step 6, obtain and meet Δ PAR, η≤ΔPAR, η ref、Tin≤
TinrefAnd λ >=λrefThe optimal design parameter φ of performance constraints and structure constraintRc, φth, φta, φLaValue
With the optimal performance calculated according to formula (1a)-(5a), final output φLR~φth, φLR~φRc, φLR~φta, φLR~
φLa4 Optimal Parameters curves, and φLR~Δ PAR, τ、φLR~Δ PAR, η、φLR~λ, φLR~E, φLR~Tin5 optimizations
Performance curve；
If because being unsatisfactory for performance constraints and without Optimal Curve, return to step one changes R value, repeat step one to
Six, obtain Optimal Curve；
Step 8：According to given damping unit radius R, the Optimal Parameters curve obtained with reference to step 7, by the nothing after optimization
Dimensional parameters have been converted into dimensional parameters, obtain τh、τa、τr、τb1、τb2、RS、RC、L、LaParameter, complete damping unit optimization and set
Meter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510396796.1A CN105045986B (en) | 2015-07-02 | 2015-07-02 | The Optimization Design for the composite damping gap magnetorheological damping unit that performance is oriented to |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510396796.1A CN105045986B (en) | 2015-07-02 | 2015-07-02 | The Optimization Design for the composite damping gap magnetorheological damping unit that performance is oriented to |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105045986A CN105045986A (en) | 2015-11-11 |
| CN105045986B true CN105045986B (en) | 2018-04-10 |
Family
ID=54452529
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510396796.1A Active CN105045986B (en) | 2015-07-02 | 2015-07-02 | The Optimization Design for the composite damping gap magnetorheological damping unit that performance is oriented to |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105045986B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105840718B (en) * | 2016-05-16 | 2017-12-22 | 中国人民解放军装甲兵工程学院 | MR damper fast optimal design method |
| CN110765559B (en) * | 2019-10-08 | 2021-06-25 | 浙江大学 | Method for predicting flow characteristic of sleeve valve |
| CN111677806B (en) * | 2020-04-27 | 2021-03-02 | 清华大学 | Method and system for determining damping force of magnetorheological shock absorber |
| CN113938082A (en) * | 2021-10-29 | 2022-01-14 | 歌尔股份有限公司 | Control method, control device, apparatus and medium for linear motor |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8400036B1 (en) * | 2009-12-16 | 2013-03-19 | Mainstream Engineering Corporation | High specific force capacity thrust magnetic bearing and method of making |
| CN104100671A (en) * | 2014-07-04 | 2014-10-15 | 中国人民解放军装甲兵工程学院 | Magnetorheological damper having parallel normally-open holes and methods for calculating zero-field damping coefficient, on-field damping coefficient and damping force of magnetorheological damper |
-
2015
- 2015-07-02 CN CN201510396796.1A patent/CN105045986B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8400036B1 (en) * | 2009-12-16 | 2013-03-19 | Mainstream Engineering Corporation | High specific force capacity thrust magnetic bearing and method of making |
| CN104100671A (en) * | 2014-07-04 | 2014-10-15 | 中国人民解放军装甲兵工程学院 | Magnetorheological damper having parallel normally-open holes and methods for calculating zero-field damping coefficient, on-field damping coefficient and damping force of magnetorheological damper |
Non-Patent Citations (2)
| Title |
|---|
| Optimal desing of control values in magnetorheological fluid dampers using a nondimensional analytical method;朱笑丛等;《Journal of Interlligent Material System and Structures》;20121230;第24卷(第1期);第108-129页 * |
| 磁流变阻尼器的有限元参数优化设计;李以农等;《重庆大学学报》;20100515;第33卷(第5期);第35-40页 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105045986A (en) | 2015-11-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105045986B (en) | The Optimization Design for the composite damping gap magnetorheological damping unit that performance is oriented to | |
| CN105840718B (en) | MR damper fast optimal design method | |
| Yoo et al. | Design of a high-efficiency magnetorheological valve | |
| Gavin et al. | Optimal design of MR dampers | |
| Hu et al. | Design, analysis and optimization of a hybrid fluid flow magnetorheological damper based on multiphysics coupling model | |
| Xu et al. | Design, performance test and analysis on magnetorheological damper for earthquake mitigation | |
| Sun et al. | Effects of structure parameters on the static electromagnetic characteristics of solenoid valve for an electronic unit pump | |
| Cristofori et al. | The modeling of electrohydraulic proportional valves | |
| Parlak et al. | Optimal magnetorheological damper configuration using the Taguchi experimental design method | |
| CN109283120B (en) | Three-coil oil detection device and manufacturing method thereof | |
| CN105160053B (en) | A kind of optimum design method for the magnetorheological damping unit that performance is oriented to | |
| Sorli et al. | Mechatronic model and experimental validation of a pneumatic servo-solenoid valve | |
| Gołdasz et al. | Magnetostatic analysis of a pinch mode magnetorheological valve | |
| Dong et al. | Design and multiobjective optimization of magnetorheological damper considering the consistency of magnetic flux density | |
| Gomis-Bellmunt et al. | Linear electromagnetic actuator modeling for optimization of mechatronic and adaptronic systems | |
| Kciuk et al. | Special application magnetorheological valve numerical and experimental analysis | |
| Mahrenholz et al. | Analytical coupled modeling and model validation of hydraulic on/off valves | |
| Dong et al. | Design of a new damper based on magnetorheological fluids | |
| Huina et al. | Multi‐objective optimal design and performance of magnetorheological damper | |
| Wang et al. | A model of giant magnetostrictive actuator used in automobile engine fuel injection system | |
| Yang et al. | Structural design and experimental study of multi-ring and multi-disc magnetorheological valve | |
| Safarzadeh et al. | Optimal design of magnetorheological fluid damper based on response surface method | |
| Gołdasz | Electro-mechanical analysis of a magnetorheological damper with electrical steel laminations | |
| Gołdasz | Magnetostatic study of a dual-gap MR valve | |
| Hu et al. | Design and performance evaluation of a magnetorheological valve with mosquito-coil-plate fluid flow channels |
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 |