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EXPERIMENTALANALYSISOFFABRICATEDMAGNETORHEOLOGICALDAMPER
1VIJAYTRIPATHI,2PROF.U.K.JOSHI
1Researchscholar,FourthSemester,M.E.(Machinedesign)JabalpurEngineeringCollege,Jabalpur(MP)‐482011,India
2AssociateProfessor,DepartmentofMechanicalEngineeringJabalpurEngineeringCollege,Jabalpur(MP)‐482011,India
ABSTRACT
Magnetorheological (MR) fluid damper are semi active control device that have been
applied a wide range of practical vibration control application. In this study, the
methodologyadopted to geta control structure isbasedon the experimental results.An
ExperimenthasbeenconductedtoestablishthebehavioroftheMRdamper.Inthispaper,
the behavior ofMR damper is studied and used in implementing vibration control. The
forcedisplacementandforce‐velocityresponsewithvaryingcurrenthasbeenestablished
for the MR damper. In this paper we investigated theoretically at fabricated
MagnetorheologicaldamperbyusingdifferentMagnetorheologicalfluid.Heretwotypesof
MR fluid developed first by mixing of prepared nano size (fe3o4) iron particle by co
precipitationmethod,secondbyseparationofmagnetictape.Andacomparativestudyhad
donebetweentheseironparticlespreparedMRfluid.Hereanexperimentalperformedon
fabricatedMRdamperanddiscussedthebehaviorofMRdamper.
KEYWORDS: Magnetorheological (MR) fluids; Magnetorheological dampers; Semi‐active
damper;nanoparticle;Magneticfieldintensity.
1. INTRODUCTION
Thesuppressionofmechanicalandstructuralvibrationusingsemi‐activecontrolmethod
hasbeenactivelyworkedbymanyresearchersinlasttwodecades[21].Recently,various
semi‐active suspension systems featuring MR fluid damper have been proposed and
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successfully applied in the real field, especially in vehicle suspension[3] systems
Magnetorheological damper is becoming the most promising vibration controller in the
intelligentsuspensionpresentlyanditwinsthefavorsofvehiclemanufactures,becauseit
takes the advantageous of high strength, good controllability, wide dynamic range, fast
responserate,lowenergyconsumptionandsimplestructure[2].Conventionaldamperhas
constant setting throughout their lifetime, and hence will not be able to operate
satisfactorily in awide range of road conditions. It is for these reasons that semi‐active
systems like MR dampers have attracted the attention of suspension designers and
researchers [2]. Models that can accurately represent the behavior of MR dampers are
essentialinunderstandingtheoperationandworkingprinciplesofthedevice.Suchmodels
can eliminate a great deal of uncertainties during the design process, which can
subsequently enable control strategies for the damper to be developed efficiently and
reliably.Amathematicalmodel isderived from theirphysical features likegeometryand
constructioncanprovideinsightsintothewayvariousparametersaffecttheperformance
ofthedevice[4].
In this paper, the fundamental design method of the MR damper is investigated
theoretically.Amathematicalmodelisusedtocharacterizetheconstitutivebehaviorofthe
MRfluidssubjecttoanexternalmagneticfieldstrength.HereI introducedanewconcept
forgeneratingamagneticfieldinsidethepistoncylinderbyuseofcirculararmaturecore.
Then a theoretical method is developed for analyzing the shear stress by the MR fluid
withintheMRDamper.
1.1PROBLEMSTATEMENTANDOBJECTIVE
ThepreviousstudiesonMRdampershaveshownthattheMRdamperseitherinpassive‐on
or semi‐active controlledmodes couldbemore efficient as comparedwith systemswith
conventionalviscousdampers.Thegoalofthisresearchistoinvestigatethecharacteristics
of theMR damper and a single‐degree‐of freedom (SDOF) systemwith the MR damper
through experimental studies and analyses under harmonic excitation of the base. In
particular,itwillbeexplainedwhythefrequencyshiftofthepeaktransmissibilityforthe
MRdampersystemisdifferentfromthatwiththeviscousdamper.Thetransmissibilitywill
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also be quantified and comparedwith that of the conventional viscous damper through
updating the equivalent damping coefficient with changing driving frequency. Here the
main problem for fabrication of MR Damper is generation of magnetic field inside of
cylinderpiston.[14]
2. PHYSICALSTUDYOFMAGNETORHEOLOGICALDAMPER
2.1MRFLUID
A magneto‐rheological‐fluid is a fluid with rheological behavior which depends on the
strengthof amagnetic field.The rheological status changes reversibly from liquid to the
solid.TheGreekword ‘‘rheos’’means flowingandrheology is thescienceofdeformation
behaviorofmaterialswhichareabletoflow.Normallytherheologicalpropertyofviscosity
changes with other physical properties, such as chemical composition, shear stress and
temperature.Thesefeaturesarenoteasilycontrolledinmostapplicationsbecausetheyare
fixed by the environment in a particular situation. In the case of MR the fluid viscosity
becomes intelligentlycontrollableusingthemagnetic field.Thischangeofviscosityupto
thesolidconditionisreversibleandisthebasicfeatureofMRFtechnology.TheMRFeffect
isthedifferenceinrheologicalpropertieswithandwithoutamagneticfield.[11]
Figure1:BehaviorofMRfluid(a)Withoutmagneticfield(b)Withmagneticfield
There are basically three components in an MR fluid: basic fluid, metal particles and
stabilizingadditives.Thebasefluidhasthefunctionofthecarrierandnaturallycombines
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lubrication (in combination with additives) and damping features. For the highest MRF
effecttheviscosityofthefluidshouldbesmallandalmostindependentoftemperature.
The MR fluid used in this research is prepared in the applied chemistry laboratory of
JabalpurengineeringcollageUniversityof(RGTU)(m.p.)India.HereIpreparedtwotypes
ofmagnetizableironparticlesfirstFeO,Fe2O3ferricoxideparticlesseparatefrommagnetic
tape.AcetoneisuseformeltandseparatesthisFerricoxide.HereIuseoldmusicorvideo
recordstapeit’salowcostsimpleprocessformakingamagnetizableironoxideparticlesin
micro meter range. Second Fe3o4 magnetizable iron oxide particles made by co
precipitationmethod. In thismethod, by adding a1MSodiumHydroxide (NaOH>99%)
solutionintoamixedsolutionof1.28MFerricchloridehexa‐hydrate(FeCl3.6H2O>99%)
and0.64Mferroussulphatetetrahydrate(FeSO4.7H2O>99%)solution(molarratio2:1)
these solution proper mixed on mechanical stirring (500rpm)at room temperature and
thenheatupat80 in3hour’safterthatwashedproperlythendrywithuseofovenand
finally Fe3o4 particle sample is prepared. The size ofmagnetizable particles is nano and
micrometers in average diameter and the carrier fluid is 1000 cps
(1Pa·s=1N·s/m2=1000cps) of veedol front frokoil. So the appearanceof thisMR fluid is
even dark gray and sensitive to themagnetic field. Poiseuillewas derived a formula for
coefficientof the viscosity, fordetermined the viscosityofMR fluid glycerin is usedas a
referencefluidoftheknownproperties.
η= .
.ηg
Where: ρ is Density of themagneto‐rheological fluid, t is out flow time of themagneto‐
rheologicalfluidfromthecapillary,ρgisdensityofthereferencefluid,tgisoutflowtimeof
thereferencefluidfromthecapillary,ηgisviscositycoefficientofthereferencefluid.
2.2MRFLUIDDAMPER
A Magneto‐Rheological (MR) damper is very similar to the traditional damper. The
differenceliesontheuseofamagneto‐rheologicalfluid,whichtypicallyconsistsofmicron
sized,magneticallypolarizableparticlesdispersedinacarriermediumsuchasmineralor
siliconeoil (Bombardet al.,2002).Whenamagnetic field isapplied to the fluid,particle
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chainsareformed,andthefluidbecomessemi‐solid,exhibitingplasticbehavior,changing
the flowpropertiesof the fluid.AMRdamper couldbebuildusing a traditional damper
bodywithmagneticvalvesabletoactovertheMRfluidproperty.Thepeakpowerrequired
tofluidcontrolislessthan30watts,whichcouldallowthedampertooperatecontinuously
formorethananhouronasmallbatter.
Figure2:SchematicdiagramoffabricatedMagnetorheologicalDamper
2.3MAGNETICFIELD
ThemagneticfieldintheMRdampercanbegeneratedwithcoilswoundaroundthepiston
byuseof circulararmature core.Circulararmature core isamainpart forgenerationof
magnetic field onMR Damper, The dimension of these circular armature fins are outer
diameterDO=38MM,innerdiameterDI=12MM,heightH=1MM.Thesupplywireconnecting
this electromagnet is then lead out through the hallow piston shaft. Maximum current
supplyofthiscoilis2amp(0to2amp).Andthetemperaturerangeis(0to70 )
3. EXPERIMENTALPROGRAM
Typically,afabricatedMRdamperconsistsofahydrauliccylinder,magneticcoilsandMR
fluid offering design simplicity as soon is fig.2. This MR damper has a conventional
cylindricalbodyconfigurationfilledwith100mlofMRfluidandcomprisingthepiston,the
magneticcircuitwithacoilresistanceof20Ωandtheaccumulator.Theenclosingcylinder
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is41.4mmindiameterandthedamperis208mmlonginitsextendedpositionwith±25
mmstroke.Thedevicecanoperatewithinacurrentrange from0.0Aup to2.0Awitha
recommendedinputvalueof1.0Aforcontinuousoperationandcandeliverapeakforceof
1000Natavelocityof50mm/swithacontinuousoperatingcurrentlevelof1.0A.TheMR
dampercanreachatleast90%ofmaximumlevelduringa0.0ampto1.0ampstepinputin
lessthan25milliseconds.[4]
Table.1:SinusoidalexcitationparametersfabricatedMRdamper
Parameter Values
Frequencies(Hz) (1.00,2.00,3.00,3.50,4.00,4.50,5.00)
Amplitudes(mm) (1.0,2.0,4.0,6.0,8.0,10.0)
Currentsupplies(A) (0.00,0.10,0.20,0.25,0.50,0.75,1.00)
4. THEORETICAL CONSIDERATION FOR DESIGN OF FABRICATED MR
DAMPER
Thedamperdesignwasdonebasedonthefollowingfacts.Themechanicalenergyrequired
for yielding increases with increase in applied magnetic field intensity which in turn
increasesyieldshearstress. Inthepresenceofmagneticfield,theshearstressassociated
withtheflowofMRfluidcanbepredictedbytheBinghamequations.[23]
τ ηγ.+τ (H)
τ τ .……....……………………..............................(1)
Hereτisthefluidshearstress,τyisthefluid’syieldstressatagivenmagneticfluxdensity
B,η is theplasticviscosity(i.e. viscosityatB=0), andу, is the fluidshear rate.Theabove
equationisusedtodesignadevicewhichworksonthebasisofMRfluid.
MRdampersgenerallyusethepressuredrivenbyflow(valve)modeofthefluid.Thetotal
pressure drop in the MR Damper is evaluated by summing the pressure drop through
viscouscomponentandyieldstresscomponent.[16]
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∆P=∆Pn+∆PY
∆P= + .......................................................................(2)
Here ΔP is the total pressure drop, ΔPη is the viscous pressure loss, ΔPY is the field
dependentyieldstresspressureloss,ηisthefluidviscosity,Qistheflowrate,Listhepole
length,wisthepolewidth,gisthefluidgap,andτyisthefieldyieldstress.
The design ofMR fluid damper is to establish the relation between the damper and the
parametersof thestructureandmagnetic fieldstrength.As themagnetic field isapplied,
thedampingforceFbyMRfluidcanbecalculatedby[8].
Fdamper=Preb(Apiston‐Arod).PcomApiston+frictionSgn(x.)
F= ɳ v sgn v ....................................................(3)
Where v is the speed of piston; f is friction of piston and cylinder; K0 is a coefficient
(0.8−1.0);histhethicknessoftheannularMR luidbetweenthepistonandoutercylinder.
Thevalueofhcanbegivenby
h=R–r.............…......………………….……...…..........…...……….…(4)
If it isassumedthatthevalueof f ismuchsmaller,Eq.(1)and(2)canbemathematically
manipulatedtoyield
F=2πτ Lr + ɳ
........................................................................(5)
Eqn. (3) shows that the damping developed in the cylindrical MR fluid damper can be
divided intoamagnetic fielddependent inducedyieldstresscomponentFYandaviscous
componentFɳ.
ThetotaldampingFisthesumofFBandFɳ.
FY=2πτ Lr ,Fɳ= ɳ
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The active volume of annular MR fluid in the cylindrical MR damper can be obtained
throughtheintegrationtheradiusofannularMRfluidasfollows.
V=2πL rdr............................................................................(6)
Therefore,v=2πrLh
Herewealsofindouttheelectricpowerconsumptionofthedeviceis
J=i2R+β ............................................................................(7)
Where R is resistance, L is inductance, i is current, β is weighting coefficient and J is
objectivefunction.
5. MODELINGOFFABRICATEDMRDAMPER
The Cantilever structure with attached mass is the most widely used configuration for
spring mass device. The stiffness of the structure depends on the loading condition,
material, and cross‐sectional area perpendicular to the direction of vibration. The
governingequationofmotionforthesystemshowninFig.3canbeobtainedfromenergy
balanceequationorD'Alembert'sprinciple.
TheschematicdiagramofthemechanicalmodelproposedinthisworkisshownintheFig.
2.Inthispicture,thevariablexmeansthedisplacementofdamperrodandFisthereaction
force of damper rod under θ displacement andθ. Velocity, the parameters k and c are
respectively the spring stiffness of the accumulator and the damping coefficient of the
viscosity.
Figure3:Mechanicalmodelforcantileverbeamstructure
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Thegoverningequationofmotionofalumpedspringmasssystemcanbewrittenas:
Iθ..+ca2θ.+kb2θ=0...................................................(i)
Thenaturalfrequencyofaspringmasssystemisdefinedby
ωn= = ..................................,,,................(ii)
ThestiffnessKforeachloadingconditionshouldbeinitiallycalculated.Hereforthecaseof
a cantilever beam, the stiffness K is given by K = 3EI/L3, where E is the modulus of
elasticity,Iisthemomentofinertia,andListhelengthofbeam.Themomentofinertiafor
arectangularcross‐sectionalcanbeobtainedfromexpression,I= bh3,wherebandhare
thewidthandthicknessofthebeamintransversedirection,respectively.
Adampingfactorξ, isadimensionlessnumberdefinedastheratioofsystemdampingto
criticaldampingas:Weknowthattheconditionofcriticaldampingvalueofdampingfactor
ξ=1,
ω=ωn,c=cc,= √km.............................................(iii)
5.1SDOFSYSTEMWITHMRDAMPER
ConsideringtheSDOFsystemwithaMRdamper(figure),assumethebaseofthesystem
undergoesharmonicmotion,i.e.
xb(t)=Xbsinωt.
Thenthesystemresponsecanbeexpressedas
xs(t)=Xssin(ωt−φ).
Hereconsidertheequationofmotionofanunderdampedsystemis
x=Xe . sin(ωd.t‐ф)
ThedisplacementtransmissibilityamplitudeXs/Xb
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=
/ =
/
Thephaseangleφcanbeobtainedas
φ=tan−1[
]
6. EXPERIMENTALSET‐UPDETAILS
Theexperimentalset‐upconsistsof(seeFigure4):
1.Vib‐lab instrument it’s a vibration lab instrument manufacture by ARE Educational
Equipment pvt. Ltd. Industrial area miraj Maharashtra, that equipment are used for
measure system vibration. It’s a vibration measuring device which mesure all type of
vibrationlikefree,forcedetc.
2.Variablevoltmeterit’sacontroldevicehereiusedforcontrolthecurrentsupplyonMR
damperwithvariablerange(0to270v)
3.Speedcontrollerit’salsoacontroldeviceusedforcontrolthespeedofDCmotorwhich
aregeneratevibrationonsystemRange(0‐1500rpm)
4.Exciter(DCmotor)isusedforgeneratethevibrationonsystem,manufacturerbypatil
electricco.pvt.Ltd. Itsmaximumspeed is1500rpmandsupplyofcurrentmaximumis
0.7amprange(0to0.7amp).
5.Multimeterisusedforshowtheexactvalueofsupplycurrentwhichgiveonarmature
coilforgeneratethemagneticfieldinsidetheMRDamper.
6.MRDamperit’samaincomponentofourexperimentallanalysisisperformonthese
mechanicalsystemhereIusedaprototypeoffabricatedMRDamper.
7.Recorderit’samechanicalrecordingdevicewhichisrecordtheamplitudevibrationof
system,speedofstripchartrecorderis33mm/sec.
8. LVDT linear variable differential transducer is a one type of transducer which is
measuringlinearvariabledisplacementinbetweentherange(0to25mm).
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Figure4:ExperimentalsetupfortestingofMRdamper
7. RESULTANDDISCUSSION
7.1EFFECTOFAMPLITUDEOFVIBRATIONWITHANDWITHOUTUSEOFMRDAMPER
ATVARIABLELENGTHOFEXCITER
Herethisgraphisshoweffectofamplitudeofvibrationwithchangingthelengthofexciter
with and without use of MR Damper. The variation of amplitude is 0 to 7 mm in this
experimentshowwhenthevariablelengthofexciterisvaryingtheamplitudeofvibration
alsovary.At550mmlengththeamplitudeofvibrationismaximum.
Graph1:ShowtheeffectofamplitudeofvibrationwithandwithoutuseofMRdamperatvariablelengthof
exciter
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Graph2:showthecombinedgraphforshowtheeffectofamplitudeofvibrationwithandwithoutuseofMR
Damperatvariablelengthofexciter
7.2 EFFECT OF MR DAMPER PISTON DISPLECMENT BY VARRING THE SUPPLY
CURRENT
This experiments test show the behavior of MR Damper piston displacement when the
valueof current increase thedisplacement of piston is decrease. Itmeans current is the
mainparameterthatareaffectedthebehaviorofMRDamper.Herethegraphplotbetween
thedisplacementandcurrentatthevariablelengthatthelength500thegraphshowthe
maximumdisplacement.
Graph3:combinedgraphforshowbehaviorofMRdamperpistondisplacementbyvaryingthesupplycurrent
0
0.2
0.4
0.6
0.8
1
1.2
1.4
1.6
1.8
0 0.2 0.4 0.6 0.8 1 1.2
DISPLA
CEM
ENT (M
M)
CURRENT (amp)
Length L= 400MMLength l=500mmLength L=600MM
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7.3 EFFECT OF AMPLITUDE OF VIBRATION ONMR DAMPER BY INCREASING THE
PERCENTAGEOFIRONPARTICLEONMRFLUID
This experiment show the behavior of MR damper by varying the percentage of iron
particleherethisgraphshowwhenthepercentageofironparticleincreasestheamplitude
ofvibrationisgraduallydecreases.Andthe(MRF1)ismoreefficientascampierto(MRF2)
because MRF1 magnetic field intensity is high as compare to MRF2.MRF1 type fluid is
preparedbymixingof feo, fe2o3 ironparticlewhichare separate themagnetic tape.And
MRF2typefluidispreparedbymixingoffe3o4ironparticlewhichispreparedbychemical
co precipitation method.
Graph4:showsthebehaviorofMRdamperbyvaryingthepercentageofironparticle
7.4EFFECTOFFORCE/DISPLACEMENTCHARACTERISTICOFMRDAMPER
Sine vibration with the frequency of 1Hz, 2Hz, and 3Hz, 4Hz was provided by vib‐lab
machine,anditsvibrationamplitudewas(1to20mm)range.Indifferentconditions,atthe
rangefrom0Ato1.0AdirectcurrentwasinputtedtoMRdamper.Experimentaldatawas
collected at intervals of 0.1A and the testing results were showed in graph.5. In our
experiments,theMRdampershowedobviousinitialshearcharacters.Withtheincreaseof
currentandspeed,thedampingforcewasinanincreasetrend,however,itwasnotnotable
withtheincreaseofcurrentafter0.5A;insteadasaturatedperformancewaspresented.
0246810121416
0 5 10 15 20 25 30 35 40 45
AMPLITU
DE (m
m)
PERCENTAGE OF IRON PARTICLE (%)
MRFLUID1
MRFLUID2
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Graph5:Force/displacementcharacteristicofMRdamper(a)Experimentaltest(b)Numericaltest6mm,2Hz
sinusoidalexcitation
8. CONCLUSION
Magnetorheological (MR) fluid dampers have provided technology that has enabled
effective semiactive control in a number of real world applications. Because of their
simplicity,lowinputpower,scalabilityandinherentrobustness.Thedesigncalculationsof
thevolume,thicknessandwidthoftheannularMRfluidwithinthedamperarederived.A
mathematicalmodeloftheMRfluiddamperisadopted.Theequivalentdampingcoefficient
of theMR damper in terms of input voltage, displacement amplitude and frequency are
investigated.TheSDOF isolation systemwith theMRdamper is analyzedby studying its
transmissibility. Also, the relative displacement with respect to the base excitation is
quantifiedandcomparedwiththatofthewithoutMRdamperandwithMRdamper.
1.Itwasshownthat,byminimizingtheobjectivefunction,theyieldstressforce,dynamics
range and conductive time constant are significantly improved at any value of applied
current.Thepowerconsumptionoftheoptimizeddamperwasalsosignificantlyreduced.
2.The ironparticle (feo, fe2o3) ismoreefficient forreductionofvibrationascompare to
useoffe3o4ironparticleonmakingofMRfluid;
3.MRDamperismainlydependedonmagneticfluxdensity.
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4. AS compare to conventional damper use of MR damper plays an important role in
reducing the vibrations because, for every load condition the behavior ofMR damper is
changepositively.
5. Magnetic circuit and structure integrated optimal design of MRF damper was well
completed in our work. Multiple structure parameters and magnetic circuit parameters
weresimultaneouslydesignedatthesametimeanditwaswithhighlyefficiency.
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