CN105160053B - A kind of optimum design method for the magnetorheological damping unit that performance is oriented to - Google Patents
A kind of optimum design method for the magnetorheological damping unit that performance is oriented to Download PDFInfo
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- CN105160053B CN105160053B CN201510392628.5A CN201510392628A CN105160053B CN 105160053 B CN105160053 B CN 105160053B CN 201510392628 A CN201510392628 A CN 201510392628A CN 105160053 B CN105160053 B CN 105160053B
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Abstract
The present invention relates to a kind of optimum design methods for the magnetorheological damping unit that performance is oriented to, and include the following steps：Obtain demand and required data of the user to performance, determine exterior design parameter and interior design parameter to be optimized, it carries out dimensionless processing and determines specific value or range, 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 within the scope of given draw ratio, 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.；This method can be applied to outside coil（It is interior）It sets in formula annular damper gap, accurate, reliable, clearly nondimensionalization parameter influence curve is provided to the performance evaluation of magnetorheological damping unit, realizes the optimization design to magnetorheological damping unit.
Description
Technical field
The present invention relates to magnetorheological fluids and hydraulic damping cell parameters optimization design field, relate more specifically to a kind of performance
The optimum design method of the magnetorheological damping unit of guiding.
Background technology
Magnetorheological damping unit is a kind of hydraulic control unit designed using magnetorheological fluid effect, is MR valve and magnetic
Core component in rheological damper can control the magnetic loaded in magnetorheological fluid by changing the electric current in magnet exciting coil
, to change the damping characteristic of fluid, reach flow and pressure drop control.There is the magnetic of circular ring shape 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 magnetorheological fluid
Product increases, and clipped position is appropriate, and magnetic field utilization rate greatly improves, and the response time is greatly reduced, and compares the magnetic current of other structures
Variable damping unit, has a wide range of application, function admirable, has very high practicability.However, the design ginseng of magnetorheological fluid damp unit
It is several that working performance is had a very big impact, in the case where volume is limited and meets user's application demand, how optimization design
Parameter makes the performance of magnetorheological damping unit 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 smaller structure space
The excellent working performance of energy；Second is that selecting suitable structure size according to actual application environment and performance requirement.However, magnetic current
Variable damping unit has the influence of coupling since it covers three machinery, electromagnetism, fluid fields between its complicated parameter,
Therefore propose that a kind of mathematical optimization models clear, accurate, that practicability is high are significant to the development of magnetorheological damping unit.
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 has ignored magnetic saturation phenomenon, simplifies 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 from magnetic circuit modeling analyze and obtained not with FInite Element
Magnetic induction intensity under same parameter, however magnetorheological damping performance depends not only on magnetic circuit, is more damped flow passage structure
It influences.Nguyen et al. has established the dynamic regulation range of MR valve, the performance indicators such as inlet and outlet pressure drop, to unicoil stream
Analysis is optimized in road and twin coil runner respectively, and the constrained optimization problem of single goal is changed into nothing by penalty
The unconstrained optimization problem of dimension.But this method, the magnetic saturation effect in magnetorheological damping runner is not accounted for, and
Interference problem that may be present between electromagnetism.
Invention content
Patent of the present invention provides a kind of optimum design method for the magnetorheological damping unit that performance is oriented to.This method integrates
Consider machinery, electromagnetism, fluid three aspect factor, establish the analysis model of magnetorheological damping unit performance, and be layered by parameter,
Cumbersome parameter is classified as interior design parameter and exterior design parameter.Further handled by nondimensionalization, it is established that with
Active damping pressure drop is the Optimized model under the multi-constraint condition of object function, can both solve the optimal of interior design parameter
Solution, while analyzing the sensibility that exterior design parameter influences performance.
The technical solution adopted by the present invention to solve the technical problems is as follows：
A kind of optimum design method for the magnetorheological damping unit that performance is oriented to, this method are hindered for coil external annular
Buddhist nun gap magnetorheological damping unit, coil external annular damper gap magnetorheological damping unit includes coiling sleeve, circle
Perimeter surface sets reeded spool, coil, upper magnetic conduction annulus, lower magnetic conduction annulus, cylinder body, piston rod etc.；Piston rod, spool, around
Line sleeve, coil, cylinder body are sequentially coaxially installed from inside to outside；Upper magnetic conduction annulus, coiling sleeve, lower magnetic conduction annulus erect from top to bottom
Straight installation, upper magnetic conduction annulus is coaxially mounted to spool upper outer, lower magnetic conduction annulus is coaxially mounted to spool lower outer, above leads
It is respectively formed circular ring shape fluid course between magnetic annulus and spool, between lower magnetic conduction annulus and spool；Piston rod by with outside
Attachment device cooperation ensures the positioning accuracy of piston rod, spool；Coil is wound on coiling sleeve；The side of cylinder body is provided with lead
The conducting wire in hole, coil is drawn from the fairlead；The coiling sleeve uses non-magnet material, upper magnetic conduction annulus, lower magnetic conduction circle
Ring, upper magnetic conduction disk, lower magnetic conduction disk, cylinder body are all made of permeability magnetic material；This approach includes the following steps：
Step 1：Obtain the H of magnetorheological fluidMR-τy(magnetic field intensity-shear yield stress) characteristic, BMR-HMR(magnetic induction is strong
Degree-magnetic field intensity) characteristic, magnetorheological fluid viscosity coefficient ηMRF, magnetorheological fluid saturation magnetic field intensity HMRF,sat, selected lead
The relative permeability μ of magnetic materialsteel, magnetic conductive media saturation induction density Bsteel,sat, space permeability μ0, magnetic current variable resistance
The maximum functional flow Q and maximum excitation electric current I of Buddhist nun's unit；Copper wire sectional area Aω, copper conductor electricalresistivityρω；Outer surface of cylinder block
Radius R.Performance requirement required by user, including active pressure drop demand Δ PA,τref, passive pressure drop demand Δ PA,ηref, dynamic
Adjustment factor demand λref, response time demand Tinref；
Step 2：The external dimensions design parameter for determining nondimensionalization, includes the draw ratio of damping unitConsider
Damping unit it is practical, in the range of 0.5~3, wherein L is upper magnetic conduction annulus upper surface and lower magnetic conduction annulus lower surface for setting
The distance between；
Determine and calculate the external electromagnetic design parameter φ of nondimensionalizationIWith external fluid design parameter φQ, whereinτy,satFor the saturation shear yield stress of magnetorheological fluid, the shear yielding of magnetorheological fluid
Stress can be by formulaIt obtains, c0、c1、c2、c3、c4For magnetorheological fluid
Fitting parameter (according to supplier provide τyMRF-HMRFObtain), therefore,
Step 3：It determines interior design parameter to be optimized, includes the thickness L of upper magnetic conduction disk and lower magnetic conduction diska, spool
Minimum exradius Rc, circular ring shape fluid course width ta, cylinder body thickness th；Piston rod radius RS, the wall thickness of coiling sleeve
tb1, the gap width t of coil and cylinder bodyb2, the difference t of spool maximum exradius and minimum exradiusb3, and by it is above-mentioned wait for it is excellent
Change interior design Parameter Switch into Dimensionless Form, and sets specific value or range.
Wherein, the width t of circular ring shape fluid courseaWith the ratio between outer surface of cylinder block radius R φtaRange be about 0.02~
0.15；The width t of disc fluid courserWith the ratio between outer surface of cylinder block radius R φtrRange be about 0.02~0.15；Spool
Minimum exradius RCWith the range φ of the ratio between outer surface of cylinder block radius RRcAbout 0.25~0.7；Magnetic conduction disc thickness LaWith it is upper
The ratio between the distance between magnetic conduction annulus upper surface and lower magnetic conduction annulus lower surface L φLaRange be about 0.1~0.4；Cylinder body thickness
thWith the ratio between outer surface of cylinder block radius R φthRange be about 0.1~0.4；Piston rod radius RSWith outer surface of cylinder block radius R it
Compare φRSRange be about 0~0.4, the wall thickness t of coiling sleeveb1With the ratio between outer surface of cylinder block radius R φtb1Range about
It is 0~0.15, the gap width t of coil and cylinder bodyb2With the ratio between outer surface of cylinder block radius R φtb2Range be about 0~0.15；Valve
The difference t of core maximum exradius and minimum exradiusb3With the ratio between outer surface of cylinder block radius R φtb3Range be about 0~0.15；
Step 4：Establish the magnetic field intensity H in annulus damping clearanceMR,a, shear yield stress τy,aComputation model, tool
Body is 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 obtains main flux loop magnetic flux phi according to the H-B relationships of each section of material in magnetic field law and circuit0, 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 magnetic conductive mediaj,sat(when medium is permeability magnetic material, then Bj,sat
=Bsteel,sat, when medium is magnetorheological fluid, then Bj,sat=BMRF,sat), then calculate the saturation magnetic flux Φ of this sectionj=Bj, sat.Sj；Wherein SjFor the magnetic flux area of jth section.With ΦjOn the basis of Φ0, in conjunction with each section of magnetic flux area, recalculate each section
Magnetic induction intensityMagnetic induction density B until making each sectionjMeet Bj≤Bj,sat, by each section of magnetic induction intensity
Each section of magnetic field intensity is obtained,Wherein b0、b1、b2、b3、b4For magnetorheological fluid
Fitting parameter；
This makes it possible to obtain the magnetic induction intensity of circular ring shape runnerThe magnetic field intensity of circular ring shape runnerThe Shear Yield Stress of Magnetorheological Fluids of circular ring shape runnerSMR,aFor the magnetic flux area at annular fluid flow gap；
Step 5 establishes performance computation model, according to dimensionless group φQ、φI、φLR, in annular fluid flow gap
Magnetic field intensity HMR,a, shear yield stress τy,a, further obtain the active damping pressure drop Δ P of damping unitA,τ, passive damping pressure
Δ P dropsA,η, dynamic regulation coefficient lambda, sensitive time constant Tin, resistance coil heat power consumption E, wherein
E=n π ρωφωcφwhφdcφI 2RHMR,sat 2 (4b)
In formula, φwc=1- φRc-φta-φth-φtb1-φtb2-φtb3, φwh=φLR/n-2φLaφLR/n-2φtb1,
φRd=φRc+0.5φta+φtb3, φdc=1+ φRc-φth+φtb1-φtb2+φtb3+φta；caFor 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 PA,τInverse be object function, i.e. Jopt=1/ Δ PA,τ, with the parameter area and not in step 1 and two
Equation (6b) is structure constraint, with Δ PA,η≤ΔPA,ηref、Tin≤TinrefWith λ >=λrefFor performance constraints；It treats
Optimize interior design variable and assigns initial value；
Using global optimization approach, the optimal value of the interior design parameter under specific exterior design parameter and corresponding is obtained
Meet the optimal performance of above-mentioned constraints.
Step 7：To external design parameter φLR, N number of point (including endpoint), φ are chosen from its rangeLR 1~φLR N, make
Its range N-1 deciles, to φLR 1~φLR NIn it is each value use step 6, acquisition meet Δ PA,η≤ΔPA,ηref、Tin≤Tinref
And λ >=λrefThe optimal design parameter φ of performance constraints and structure constraintRc, φth, φta, φLaValue and root
According to the optimal performance that formula (1b)-(5b) is calculated, final output φLR~φth, φLR~φRc, φLR~φta, φLR~φLa
4 Optimal Parameters curves and φLR~Δ PA,τ、φLR~Δ PA,η、φLR~λ, φLR~E, φLR~Tin5 optimization performances
Curve.
If changing the value of R without Optimal Curve, return to step one due to being unsatisfactory for performance constraints, step is repeated
One to six, obtain Optimal Curve.
Step 8：According to given damping unit radius R, in conjunction with the Optimal Parameters curve that step 7 obtains, after optimization
Dimensionless group be converted into dimensional parameters, obtain τh、τa、τb1、τb2、τb3、RS、RC、L、LaEtc. parameters, complete damping unit
Optimization design.
A kind of optimum design method for the magnetorheological damping unit that performance is oriented to, this method is for the built-in annular resistance of coil
Buddhist nun gap magnetorheological damping unit, the built-in annular damper gap magnetorheological damping unit of coil include coiling sleeve, change
Spool, coil, cylinder body, piston rod after making etc.；Piston rod, spool, coiling sleeve, coil, cylinder body are from inside to outside sequentially coaxially
Installation；Spool is coaxially mounted to outside piston rod；Spool circumferential surface is equipped with groove, and coiling sleeve is coaxially mounted to the recessed of spool
At slot；Circular ring shape fluid course is respectively formed between spool upper and lower ends and cylinder body.Coil is wound on coiling sleeve；The one of cylinder body
Side is provided with fairlead, and the conducting wire of coil is drawn from the fairlead；The coiling sleeve uses non-magnet material, spool, cylinder body
It is all made of permeability magnetic material；This approach includes the following steps：
Step 1：Obtain the H of magnetorheological fluidMR-τy(magnetic field intensity-shear yield stress) characteristic, BMR-HMR(magnetic induction is strong
Degree-magnetic field intensity) characteristic, magnetorheological fluid viscosity coefficient ηMRF, magnetorheological fluid saturation magnetic field intensity HMRF,sat, selected lead
The relative permeability μ of magnetic materialsteel, magnetic conductive media saturation induction density Bsteel,sat, space permeability μ0, magnetic current variable resistance
The maximum functional flow Q and maximum excitation electric current I of Buddhist nun's unit；Copper wire sectional area Aω, copper conductor electricalresistivityρω；Outer surface of cylinder block
Radius R.Performance requirement required by user, including active pressure drop demand Δ PA,τref, passive pressure drop demand Δ PA,ηref, dynamic
Adjustment factor demand λref, response time demand Tinref；
Step 2：The external dimensions design parameter for determining nondimensionalization, includes the draw ratio of damping unitConsider
Damping unit it is practical, in the range of 0.5~3, wherein L is the distance between spool upper surface and lower surface for setting；
Determine and calculate the external electromagnetic design parameter φ of nondimensionalizationIWith external fluid design parameter φQ, whereinτy,satFor the saturation shear yield stress of magnetorheological fluid, the shear yielding of magnetorheological fluid
Stress can be by formulaIt obtains, c0、c1、c2、c3、c4For the quasi- of magnetorheological fluid
Parameter is closed, therefore,
Step 3：Determine interior design parameter to be optimized, including spool upper surface and between magnetic sleeve upper surface away from
From, spool lower surface with around the distance between magnetic sleeve lower surface La；Valve core outer surface least radius Rc, circular ring shape fluid course
Width ta, cylinder body thickness th；The wall thickness t of coiling sleeveb1, coil outer surface and gap width around magnetic sleeve outer surface
tb3, and by above-mentioned interior design Parameter Switch to be optimized at Dimensionless Form, and set specific value or range.
Wherein, the width t of circular ring shape fluid courseaWith the ratio between outer surface of cylinder block radius R φtaRange be about 0.02~
0.15；Valve core outer surface least radius RcWith the range φ of the ratio between outer surface of cylinder block radius RRcAbout 0.25~0.7；Cylinder body thickness
thWith the ratio between outer surface of cylinder block radius R φthRange be about 0.1~0.4；Piston rod radius RSWith outer surface of cylinder block radius R it
Compare φRsRange be about 0~0.4, the ratio between wall thickness and outer surface of cylinder block radius R of coiling sleeve φtb1Range be about 0
~0.15, coil outer surface and gap width t around magnetic sleeve outer surfaceb3With the ratio between outer surface of cylinder block radius R φtb3Range
About 0~0.15；
Step 4：Establish the magnetic field intensity H in annulus damping clearanceMR,a, shear yield stress τy,aComputation model, tool
Body is 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 obtains main flux loop magnetic flux phi according to the H-B relationships of each section of material in magnetic field law and circuit0, 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 magnetic conductive mediaj,sat(when medium is permeability magnetic material, then Bj,sat
=Bsteel,sat, when medium is magnetorheological fluid, then Bj,sat=BMRF,sat), then calculate the saturation magnetic flux Φ of this sectionj=
Bj,sat·Sj；Wherein SjFor the magnetic flux area of jth section.With ΦjOn the basis of Φ0, in conjunction with each section of magnetic flux area, recalculate each
The magnetic induction intensity of sectionMagnetic induction density B until making each sectionjMeet Bj≤Bj,sat, by each section of magnetic induction intensity
Each section of magnetic field intensity is can be obtained,Wherein b0、b1、b2、b3、b4For magnetic current
Become the fitting parameter of liquid；
This makes it possible to obtain the magnetic induction intensity of circular ring shape runnerThe magnetic field intensity of circular ring shape runnerThe Shear Yield Stress of Magnetorheological Fluids of circular ring shape runnerSMR,aFor the magnetic flux area at annular fluid flow gap；
Step 5 establishes performance computation model, according to dimensionless group φQ、φI、φLR, in annular fluid flow gap
Magnetic field intensity HMR,a, shear yield stress τy,a, further obtain the active damping pressure drop Δ P of damping unitA,τ, passive damping pressure
Δ P dropsA,η, dynamic regulation coefficient lambda, sensitive time constant Tin, resistance coil heat power consumption E, wherein
E=n π ρωφωcφwhφdcφI 2RHMR,sat 2 (4c)
In formula, φwc=1- φRc-φta-φth-φtb1-φtb3, φwh=φLR/n-2φLaφLR/n-2φtb1, φRd=
1-φth-0.5φta, φdc=1+ φRc-φth-φta+φtb1-φtb3；caFor correction factor, value 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 PA,τInverse be object function, i.e. Jopt=1/ Δ PA,τ, with the parameter area and not in step 1 and two
Equation (6c) is structure constraint, with Δ PA,η≤ΔPA,ηref、Tin≤TinrefWith λ >=λrefFor performance constraints；It treats
Optimize interior design variable and assigns initial value；
Using global optimization approach, the optimal value of the interior design parameter under specific exterior design parameter and corresponding is obtained
Meet the optimal performance of above-mentioned constraints.
Step 7：To external design parameter φLR, N number of point (including endpoint), φ are chosen from its rangeLR 1~φLR N, make
Its range N-1 deciles, to φLR 1~φLR NIn it is each value use step 6, acquisition 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 (1c)-(5c), final output φLR~φth, φLR~φRc, φLR~φta, φLR~
φLa4 Optimal Parameters curves and φLR~Δ PA,τ、φLR~Δ PA,η、φLR~λ, φLR~E, φLR~Tin5 optimizations
Performance curve.
If changing the value of R without Optimal Curve, return to step one due to being unsatisfactory for performance constraints, step is repeated
One to six, obtain Optimal Curve.
Step 8：According to given damping unit radius R, in conjunction with the Optimal Parameters curve that step 7 obtains, after optimization
Dimensionless group be converted into dimensional parameters, obtain τh、τa、τb1、τb3、RS、RC、L、LaEtc. parameters, complete damping unit optimization
Design.
The present invention has the advantage that compared with technical background：
The structure size 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.However, state
The inside and outside optimum design method to magnetorheological damping unit only rests in qualitative structural analysis level, and only to single parameter
Analysis is optimized, mostly selects a certain numerical value in general scope by rule of thumb.Therefore, the present invention has the following technical effects：
1. the present invention to start in terms of fluid, structure, electromagnetism three to magnetorheological damping unit establish it is complete, accurate,
Reliable analysis model, and establish accurate working performance 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 working performance；
3. the parameter of model is classified as two classes, i.e. interior design parameter phi by the present inventionta、φth、φRs、φRc、φta、φtb、
φLaAnd exterior design parameter phiLR(structure is related), φI(electromagnetism is related), φF(fluid is related), keeps model further bright
It is clear；
4. the present invention both can be applicable to coil external or built-in annular damper gap magnetorheological damping unit, versatility
It is high.
5. the present invention is in practical application, can constrain external design parameter according to the limitation of external environment, application
Range is wide.
Description of the drawings
Fig. 1 is magnetorheological damping unit optimization design method flow chart；
Fig. 2 is coil external annular damper gap magnetorheological damping cellular construction dimension model schematic diagram；
Fig. 3 is the built-in annular damper gap magnetorheological damping cellular construction dimension model schematic diagram of coil；
In figure, coiling sleeve 1, spool 2, coil 3, circular ring shape fluid course 8, cylinder body 11, piston rod 12.
Specific implementation mode
Below by embodiment, invention is further described in detail.
As shown in Fig. 2, coil external annular damper gap magnetorheological damping unit includes coiling sleeve 1, circumferential surface
If reeded spool 2, coil 3, upper magnetic conduction annulus, lower magnetic conduction annulus, cylinder body 11, piston rod 12 etc.；Piston rod 12, spool 2,
Coiling sleeve 1, coil 3, cylinder body 11 are sequentially coaxially installed from inside to outside；Upper magnetic conduction annulus, coiling sleeve 1, lower magnetic conduction annulus by
Top to bottm is vertically-mounted, and upper magnetic conduction annulus is coaxially mounted to 2 upper outer of spool, lower magnetic conduction annulus is coaxially mounted under spool 2
Side is external, and circular ring shape fluid course 8 is respectively formed between upper magnetic conduction annulus and spool 2, between lower magnetic conduction annulus and spool 2；It is living
Stopper rod 12 ensures the positioning accuracy of piston rod 12, spool 2 by coordinating with external connection device；Coil 3 is wound on coiling sleeve 1
On；The side of cylinder body 11 is provided with fairlead, and the conducting wire of coil 3 is drawn from the fairlead；The coiling sleeve 1 is using non-magnetic
Material, upper magnetic conduction annulus, lower magnetic conduction annulus, upper magnetic conduction disk, lower magnetic conduction disk, cylinder body 11 are all made of permeability magnetic material；
The optimum design method of coil external annular damper gap magnetorheological damping unit is as follows：
Step 1：Obtain the H of magnetorheological fluidMR-τy(magnetic field intensity-shear yield stress) characteristic, BMR-HMR(magnetic induction is strong
Degree-magnetic field intensity) characteristic, magnetorheological fluid viscosity coefficient ηMRF, magnetorheological fluid saturation magnetic field intensity HMRF,sat, selected lead
The relative permeability μ of magnetic materialsteel, magnetic conductive media saturation induction density Bsteel,sat, space permeability μ0, magnetic current variable resistance
The maximum functional flow Q and maximum excitation electric current I of Buddhist nun's unit；Copper wire sectional area Aω, copper conductor electricalresistivityρω；11 appearance of cylinder body
The radius R in face.Performance requirement required by user, including active pressure drop demand Δ PA,τref, passive pressure drop demand Δ PA,ηref, it is dynamic
State adjustment factor demand λref, response time demand Tinref；
Step 2：The external dimensions design parameter for determining nondimensionalization, includes the draw ratio of damping unitConsider
Damping unit it is practical, in the range of 0.5~3, wherein L is upper magnetic conduction annulus upper surface and lower magnetic conduction annulus lower surface for setting
The distance between；
Determine and calculate the external electromagnetic design parameter φ of nondimensionalizationIWith external fluid design parameter φQ, whereinτy,satFor the saturation shear yield stress of magnetorheological fluid, the shear yielding of magnetorheological fluid
Stress can be by formulaIt obtains, c0、c1、c2、c3、c4For magnetorheological fluid
Fitting parameter (according to supplier provide τyMRF-HMRFObtain), therefore,
Step 3：It determines interior design parameter to be optimized, includes the thickness L of upper magnetic conduction disk and lower magnetic conduction diska, spool
Minimum exradius Rc, circular ring shape fluid course width ta, cylinder body thickness th；Piston rod radius RS, the barrel thickness of coiling sleeve 1
Spend tb1, the gap width t of coil 3 and cylinder body 11b2, the difference t of spool 2 maximum exradius and minimum exradiusb3, and will be upper
Interior design Parameter Switch to be optimized is stated into Dimensionless Form, and sets specific value or range.
Wherein, the width t of circular ring shape fluid courseaWith the ratio between 11 appearance radius surface R of cylinder body φtaRange be about 0.02~
0.15；The width t of disc fluid courserWith the ratio between 11 appearance radius surface R of cylinder body φtrRange be about 0.02~0.15；Valve
Core minimum exradius RCWith the range φ of the ratio between 11 appearance radius surface R of cylinder bodyRcAbout 0.25~0.7；Magnetic conduction disc thickness La
With the ratio between the distance between upper magnetic conduction annulus upper surface and lower magnetic conduction annulus lower surface L φLaRange be about 0.1~0.4；Cylinder body
Thickness thWith the ratio between 11 appearance radius surface R of cylinder body φthRange be about 0.1~0.4；Piston rod radius RSWith 11 outer surface of cylinder body
The ratio between radius R φRSRange be about 0~0.4, the wall thickness t of coiling sleeve 1b1The ratio between with 11 appearance radius surface R of cylinder body
φtb1Range be about 0~0.15, the gap width t of coil 3 and cylinder body 11b2With the ratio between 11 appearance radius surface R of cylinder body φtb2's
Range is about 0~0.15；The difference t of spool 2 maximum exradius and minimum exradiusb3The ratio between with 11 appearance radius surface R of cylinder body
φtb3Range be about 0~0.15 (when it is implemented, RS、φtb1、φtb2、φtb3It is respectively taken within its scope according to actual conditions
One fixed value)；
Step 4：Establish the magnetic field intensity H in annulus damping clearanceMR,a, shear yield stress τy,aComputation model, tool
Body is 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 obtains main flux loop magnetic flux phi according to the H-B relationships of each section of material in magnetic field law and circuit0, 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 magnetic conductive mediaj,sat(when medium is permeability magnetic material, then Bj,sat
=Bsteel,sat, when medium is magnetorheological fluid, then Bj,sat=BMRF,sat), then calculate the saturation magnetic flux Φ of this sectionj=
Bj,sat·Sj；Wherein SjFor the magnetic flux area of jth section.With ΦjOn the basis of Φ0, in conjunction with each section of magnetic flux area, recalculate each
The magnetic induction intensity of sectionMagnetic induction density B until making each sectionjMeet Bj≤Bj,sat, by each section of magnetic induction intensity
Each section of magnetic field intensity is can be obtained,Wherein b0、b1、b2、b3、b4For magnetic current
Fitting parameter (the H provided according to supplier of liquid is providedMRF-BMRFIt obtains)；
This makes it possible to obtain the magnetic induction intensity of circular ring shape runnerThe magnetic field intensity of circular ring shape runnerThe Shear Yield Stress of Magnetorheological Fluids of circular ring shape runnerSMR,aFor the magnetic flux area at annular fluid flow gap；
Step 5 establishes performance computation model, according to dimensionless group φQ、φI、φLR, in annular fluid flow gap
Magnetic field intensity HMR,a, shear yield stress τy,a, further obtain the active damping pressure drop Δ P of damping unitA,τ, passive damping pressure
Δ P dropsA,η, dynamic regulation coefficient lambda, sensitive time constant Tin, resistance coil heat power consumption E, wherein
E=n π ρωφωcφwhφdcφI 2RHMR,sat 2 (4b)
In formula, φwc=1- φRc-φta-φth-φtb1-φtb2-φtb3, φwh=φLR/n-2φLaφLR/n-2φtb1,
φRd=φRc+0.5φta+φtb3, φdc=1+ φRc-φth+φtb1-φtb2+φtb3+φta；caFor 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 PA,τInverse be object function, i.e. Jopt=1/ Δ PA,τ, with the parameter area and not in step 1 and two
Equation (6b) is structure constraint, with Δ PA,η≤ΔPA,ηref、Tin≤TinrefWith λ >=λrefFor performance constraints；It treats
Optimize interior design variable and assigns initial value；
Using global optimization approach, the optimal value of the interior design parameter under specific exterior design parameter and corresponding is obtained
Meet the optimal performance of above-mentioned constraints.
Step 7：To external design parameter φLR, N number of point (including endpoint), φ are chosen from its rangeLR 1~φLR N, make
Its range N-1 deciles, to φLR 1~φLR NIn it is each value use step 6, acquisition meet Δ PA,η≤ΔPA,ηref、Tin≤Tinref
And λ >=λrefThe optimal design parameter φ of performance constraints and structure constraintRc, φth, φta, φLaValue and root
According to the optimal performance that formula (1b)-(5b) is calculated, final output φLR~φth, φLR~φRc, φLR~φta, φLR~φLa
4 Optimal Parameters curves and φLR~Δ PA,τ、φLR~Δ PA,η、φLR~λ, φLR~E, φLR~Tin5 optimization performances
Curve.
If changing the value of R without Optimal Curve, return to step one due to being unsatisfactory for performance constraints, step is repeated
One to six, obtain Optimal Curve.
Step 8：According to given damping unit radius R, in conjunction with the Optimal Parameters curve that step 7 obtains, after optimization
Dimensionless group be converted into dimensional parameters, obtain τh、τa、τb1、τb2、τb3、RS、RC、L、LaEtc. parameters, complete damping unit
Optimization design.
As shown in figure 3, the built-in annular damper gap magnetorheological damping unit of coil include coiling sleeve 1, it is improved
Spool 2, coil 3, cylinder body 11, piston rod 12 etc.；Piston rod 12, spool 2, coiling sleeve 1, coil 3, cylinder body 11 from inside to outside according to
It is secondary to be co-axially mounted；Spool 2 is coaxially mounted to outside piston rod 12；2 circumferential surface of spool is equipped with groove, and coiling sleeve 1 is coaxially pacified
Mounted in the groove of spool 2；It is respectively formed circular ring shape fluid course 8 between 2 upper and lower ends of spool and cylinder body 11.Coil 3 is wound on
On coiling sleeve 1；The side of cylinder body 11 is provided with fairlead, and the conducting wire of coil 3 is drawn from the fairlead；The coiling sleeve 1
Using non-magnet material, spool 2, cylinder body 11 are all made of permeability magnetic material；The built-in annular damper gap magnetorheological damping list of coil
The optimum design method of member is as follows：
The step 1：Obtain the H of magnetorheological fluidMR-τy(magnetic field intensity-shear yield stress) characteristic, BMR-HMR(magnetic strength
Answer intensity-magnetic field intensity) characteristic, magnetorheological fluid viscosity coefficient ηMRF, magnetorheological fluid saturation magnetic field intensity HMRF,sat, it is selected
With the relative permeability μ of permeability magnetic materialsteel, magnetic conductive media saturation induction density Bsteel,sat, space permeability μ0, magnetic current
The maximum functional flow Q and maximum excitation electric current I of variable damping unit；Copper wire sectional area Aω, copper conductor electricalresistivityρω；Cylinder body 11
The radius R of outer surface.Performance requirement required by user, including active pressure drop demand Δ PA,τref, passive pressure drop demand Δ
PA,ηref, dynamic regulation coefficient demand λref, response time demand Tinref；
Step 2：The external dimensions design parameter for determining nondimensionalization, includes the draw ratio of damping unitConsider
Damping unit it is practical, in the range of 0.5~3, wherein L is the distance between 2 upper surface of spool and lower surface for setting；
Determine and calculate the external electromagnetic design parameter φ of nondimensionalizationIWith external fluid design parameter φQ, whereinτy,satFor the saturation shear yield stress of magnetorheological fluid, the shear yielding of magnetorheological fluid
Stress can be by formulaIt obtains, c0、c1、c2、c3、c4It is magnetorheological
Fitting parameter (the τ provided according to supplier of liquidyMRF-HMRFObtain), therefore,
Step 3：Determine interior design parameter to be optimized, including 2 upper surface of spool and between 1 upper surface of magnetic sleeve
Distance, 2 lower surface of spool with around the distance between 1 lower surface of magnetic sleeve La；2 outer surface least radius R of spoolc, circular ring shape liquid stream
Channel width ta, cylinder body thickness th；The wall thickness t of coiling sleeve 1b1, 3 outer surface of coil and between 1 outer surface of magnetic sleeve
Gap width tb3, and by above-mentioned interior design Parameter Switch to be optimized at Dimensionless Form, and set specific value or range.
Wherein, the width t of circular ring shape fluid courseaWith the ratio between 11 appearance radius surface R of cylinder body φtaRange be about 0.02~
0.15；2 outer surface least radius R of spoolcWith the range φ of the ratio between 11 appearance radius surface R of cylinder bodyRcAbout 0.25~0.7；Cylinder body
Thickness thWith the ratio between 11 appearance radius surface R of cylinder body φthRange be about 0.1~0.4；12 radius R of piston rodSWith 11 appearance of cylinder body
The ratio between radius surface R φRsRange be about 0~0.4, the ratio between wall thickness and 11 appearance radius surface R of cylinder body of coiling sleeve 1 φtb1
Range be about 0~0.15,3 outer surface of coil and gap width t around 1 outer surface of magnetic sleeveb3With 11 appearance radius surface R of cylinder body
The ratio between φtb3Range be about 0~0.15 (when it is implemented, RS、φtb1、φtb3One is respectively taken within its scope according to actual conditions
Fixed value)；；
Step 4：Establish the magnetic field intensity H in annulus damping clearanceMR,a, shear yield stress τy,aComputation model, tool
Body is 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 obtains main flux loop magnetic flux phi according to the H-B relationships of each section of material in magnetic field law and circuit0, 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 magnetic conductive mediaj,sat(when medium is permeability magnetic material, then Bj,sat
=Bsteel,sat, when medium is magnetorheological fluid, then Bj,sat=BMRF,sat), then calculate the saturation magnetic flux Φ of this sectionj=
Bj,sat·Sj；Wherein SjFor the magnetic flux area of jth section.With ΦjOn the basis of Φ0, in conjunction with each section of magnetic flux area, recalculate each
The magnetic induction intensity of sectionMagnetic induction density B until making each sectionjMeet Bj≤Bj,sat, by each section of magnetic induction intensity
Each section of magnetic field intensity is can be obtained,Wherein b0、b1、b2、b3、b4For magnetic current
Fitting parameter (the H provided according to supplier of liquid is providedMRF-BMRFIt obtains)；
This makes it possible to obtain the magnetic induction intensity of circular ring shape runnerThe magnetic field intensity of circular ring shape runnerThe Shear Yield Stress of Magnetorheological Fluids of circular ring shape runnerSMR,aFor the magnetic flux area at annular fluid flow gap；
Step 5 establishes performance computation model, according to dimensionless group φQ、φI、φLR, in annular fluid flow gap
Magnetic field intensity HMR,a, shear yield stress τy,a, further obtain the active damping pressure drop Δ P of damping unitA,τ, passive damping pressure
Δ P dropsA,η, dynamic regulation coefficient lambda, sensitive time constant Tin, resistance coil heat power consumption E, wherein
E=n π ρωφωcφwhφdcφI 2RHMR,sat 2 (4c)
In formula, φwc=1- φRc-φta-φth-φtb1-φtb3, φwh=φLR/n-2φLaφLR/n-2φtb1, φRd=
1-φth-0.5φta, φdc=1+ φRc-φth-φta+φtb1-φtb3；caFor correction factor, value 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 PA,τInverse be object function, i.e. Jopt=1/ Δ PA,τ, with the parameter area and not in step 1 and two
Equation (6c) is structure constraint, with Δ PA,η≤ΔPA,ηref、Tin≤TinrefWith λ >=λrefFor performance constraints；It treats
Optimize interior design variable and assigns initial value；
Using global optimization approach, the optimal value of the interior design parameter under specific exterior design parameter and corresponding is obtained
Meet the optimal performance of above-mentioned constraints.
Step 7：To external design parameter φLR, N number of point (including endpoint), φ are chosen from its rangeLR 1~φLR N, make
Its range N-1 deciles, to φLR 1~φLR NIn it is each value use step 6, acquisition 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 (1c)-(5c), final output φLR~φth, φLR~φRc, φLR~φta, φLR~
φLa4 Optimal Parameters curves and φLR~Δ PA,τ、φLR~Δ PA,η、φLR~λ, φLR~E, φLR~Tin5 optimizations
Performance curve.
If changing the value of R without Optimal Curve, return to step one due to being unsatisfactory for performance constraints, step is repeated
One to six, obtain Optimal Curve.
Step 8：According to given damping unit radius R, in conjunction with the Optimal Parameters curve that step 7 obtains, after optimization
Dimensionless group be converted into dimensional parameters, obtain τh、τa、τb1、τb3、RS、RC、L、LaEtc. parameters, complete damping unit optimization
Design.
Claims (1)
1. a kind of optimum design method for the magnetorheological damping unit that performance is oriented to, this method is used for coil external annular damper
The optimization design of gap magnetorheological damping unit, coil external annular damper gap magnetorheological damping unit includes coiling
Sleeve (1), circumferential surface set reeded spool (2), coil (3), upper magnetic conduction annulus, lower magnetic conduction annulus, cylinder body (11), piston
Bar (12)；Piston rod (12), spool (2), coiling sleeve (1), coil (3), cylinder body (11) are sequentially coaxially installed from inside to outside；On
Magnetic conduction annulus, coiling sleeve (1), lower magnetic conduction annulus are vertically-mounted from top to bottom, and upper magnetic conduction annulus is coaxially mounted on spool (2)
External, the lower magnetic conduction annulus in side is coaxially mounted to spool (2) lower outer, between upper magnetic conduction annulus and spool (2), lower magnetic conduction annulus
Circular ring shape fluid course (8) is respectively formed between spool (2)；Piston rod (12) ensures to live by with external connection device coordinating
The positioning accuracy of stopper rod (12), spool (2)；Coil (3) is wound on coiling sleeve (1)；The side of cylinder body (11) is provided with fairlead,
The conducting wire of coil (3) is drawn from the fairlead；The coiling sleeve (1) uses non-magnet material, upper magnetic conduction annulus, lower magnetic conduction
Annulus, upper magnetic conduction disk, lower magnetic conduction disk, cylinder body (11) are all made of permeability magnetic material；It is characterized in that, this method includes following step
Suddenly：
Step 1：Obtain magnetic field intensity-shear yield stress characteristic H of magnetorheological fluidMR-τy, magnetic induction intensity-magnetic field intensity it is special
Property BMR-HMR, magnetorheological fluid viscosity coefficient ηMR, magnetorheological fluid saturation magnetic field intensity HMR,sat, selected permeability magnetic material phase
To magnetic permeability μsteel, magnetic conductive media saturation induction density Bsteel,sat, space permeability μ0, magnetorheological damping unit is most
Big working flow Q and maximum excitation electric current I；Copper wire sectional area Aω, copper conductor electricalresistivityρω；The radius of cylinder body (11) outer surface
R；Performance requirement required by user, including active pressure drop demand Δ PA,τref, passive pressure drop demand Δ PA,ηref, dynamic regulation system
Number demand λref, response time demand Tinref；Wherein, HMRFor magnetic field intensity, τyFor shear yield stress, BMRMagnetic induction intensity；
Step 2：The external dimensions design parameter for determining nondimensionalization, includes the draw ratio of damping unitConsider damping
Unit it is practical, set in the range of 0.5~3, wherein L is between upper magnetic conduction annulus upper surface and lower magnetic conduction annulus lower surface
Distance；
Determine and calculate the external electromagnetic design parameter φ of nondimensionalizationIWith external fluid design parameter φQ, whereinτy,satFor the saturation shear yield stress of magnetorheological fluid, the shear yielding of magnetorheological fluid
Stress is by formulaIt obtains, c0、c1、c2、c3、c4Join for the fitting of magnetorheological fluid
Number, therefore,
Step 3：It determines interior design parameter to be optimized, includes the thickness L of upper magnetic conduction disk and lower magnetic conduction diska, spool minimum
Exradius Rc, circular ring shape fluid course width ta, cylinder body thickness th；Piston rod radius RS, the wall thickness of coiling sleeve (1)
tb1, the gap width t of coil (3) and cylinder body (11)b2, the difference t of spool (2) maximum exradius and minimum exradiusb3, and
By above-mentioned interior design Parameter Switch to be optimized at Dimensionless Form, and set specific value or range；
Wherein, the width t of circular ring shape fluid courseaWith the ratio between cylinder body (11) appearance radius surface R φtaRanging from 0.02~
0.15；The width t of disc fluid courserWith the ratio between cylinder body (11) appearance radius surface R φtrRanging from 0.02~0.15；Valve
Core minimum exradius RCWith the range φ of the ratio between cylinder body (11) appearance radius surface RRcIt is 0.25~0.7；Magnetic conduction disc thickness La
With the ratio between the distance between upper magnetic conduction annulus upper surface and lower magnetic conduction annulus lower surface L φLaRanging from 0.1~0.4；Cylinder body is thick
Spend thWith the ratio between cylinder body (11) appearance radius surface R φthRanging from 0.1~0.4；Piston rod radius RSWith cylinder body (11) outer surface
The ratio between radius R φRSRanging from 0~0.4, the wall thickness t of coiling sleeve (1)b1The ratio between with cylinder body (11) appearance radius surface R
φtb1Ranging from 0~0.15, the gap width t of coil (3) and cylinder body (11)b2The ratio between with cylinder body (11) appearance radius surface R
φtb2Ranging from 0~0.15；The difference t of spool (2) maximum exradius and minimum exradiusb3With cylinder body (11) outer surface half
The ratio between diameter R φtb3Ranging from 0~0.15；
Step 4：Establish the magnetic field intensity H in annulus damping clearanceMR,a, shear yield stress τy,aComputation model, specifically such as
Under：
Main flux loop is segmented by magnetic conductive media and magnetic flux area shape, the magnetic flux area of each section of calculating, magnetic force line length,
Main flux loop magnetic flux phi is obtained according to the H-B relationships of each section of material in magnetic field law and circuit0, to obtain each section of magnetic
InductionAnd by magnetic induction intensity compared with the saturation induction density of this section of magnetic conductive media, if the magnetic of jth section
Induction is more than the saturation induction density B of this section of magnetic conductive mediaj,sat, then the saturation magnetic flux Φ of this section is calculatedj=
Bj,sat·Sj；Wherein SjFor the magnetic flux area of jth section；With ΦjOn the basis of Φ0, in conjunction with each section of magnetic flux area, recalculate each
The magnetic induction intensity of sectionMagnetic induction density B until making each sectionjMeet Bj≤Bj,sat, by each section of magnetic induction intensity
Each section of magnetic field intensity is obtained,Wherein b0、b1、b2、b3、b4It is magnetorheological
The fitting parameter of liquid；
Thus the magnetic induction intensity of circular ring shape runner is obtainedThe magnetic field intensity of circular ring shape runnerThe Shear Yield Stress of Magnetorheological Fluids of circular ring shape runnerSMR,aFor the magnetic flux area at annular fluid flow gap；
Step 5 establishes performance computation model, 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, further obtain the active damping pressure drop Δ P of damping unitA,τ, passive damping pressure drop Δ
PA,η, dynamic regulation coefficient lambda, sensitive time constant Tin, resistance coil heat power consumption E, wherein
E=n π ρωφωcφwhφdcφI 2RHMR,sat 2 (4b)
In formula, φwc=1- φRc-φta-φth-φtb1-φtb2-φtb3, φwh=φLR/n-2φLaφLR/n-2φtb1, φRd
=φRc+0.5φta+φtb3, φdc=1+ φRc-φth+φtb1-φtb2+φtb3+φta；caFor correction factor, value 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 PA,τInverse be object function, i.e. Jopt=1/ Δ PA,τ, with the parameter area and inequality in step 1 and two
(6b) is structure constraint, with Δ PA,η≤ΔPA,ηref、Tin≤TinrefWith λ >=λrefFor performance constraints；To be optimized
Interior design variable assigns initial value；
Using global optimization approach, the optimal value of the interior design parameter under specific exterior design parameter and corresponding satisfaction are obtained
The optimal performance of above-mentioned constraints；
Step 7：To external design parameter φLR, N number of point including endpoint, φ are chosen from its rangeLR 1~φLR N, make
Its range N-1 deciles, to φLR 1~φLR NIn it is each value use step 6, acquisition meet Δ PA,η≤ΔPA,ηref、Tin≤Tinref
And λ >=λrefThe optimal design parameter φ of performance constraints and structure constraintRc, φth, φta, φLaValue and root
According to the optimal performance that formula (1b)-(5b) is calculated, final output φLR~φth, φLR~φRc, φLR~φta, φLR~φLa4
Optimal Parameters curve and φLR~Δ PA,τ、φLR~Δ PA,η、φLR~λ, φLR~E, φLR~Tin5 optimization performances
Curve；
If changing the value of R without Optimal Curve, return to step one due to being unsatisfactory for performance constraints, step 1 is repeated extremely
Six, obtain Optimal Curve；
Step 8：According to given damping unit radius R, in conjunction with the Optimal Parameters curve that step 7 obtains, by the nothing after optimization
Dimensional parameters have been converted into dimensional parameters, obtain th、ta、tb1、tb2、tb3、RS、RC、L、LaParameter is completed damping unit optimization and is set
Meter.
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| CN103810337A (en) * | 2014-02-11 | 2014-05-21 | 上海电力学院 | Novel modeling method for magnetorheological damper |
| 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 |
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| CN103810337A (en) * | 2014-02-11 | 2014-05-21 | 上海电力学院 | Novel modeling method for magnetorheological damper |
| 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 |
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