Gear Design 1

8/2/2019 Gear Design 1

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HomeDrive_IndexGearsGearboxes

Spur Gears

Introduction.....StaEquations.....ModContactRatio.....FProcess.....Interna

Thenotesbelow onaseparatep

IntroductionIntroductionIntroductionIntroduction

Gearsaremachi normallywitha iscalledthegea

alongoneside-i practicetheacti matingteethacti throughouttheismaintainedfix teethcomeintomovingatconst driventooththe selectedforthe Consideroneen otherendofthe andbothcylinde

figurebelow). marked.Asthe cylinderasitwr stringunwraps.

on on this page has not been checked by an indtion at your own risk.

ROYMECH

ndards.....Terminology.....SpurGearDesign.....le.....PressureAngle.....orces-Torquesetc.....StrengthDurabilitycalcs...lGears.....TableofLewisFormFactors.....

relatetospurgears.Notesspecifictohelicalg geHelicalGears

ineelementsusedtotransmitrotarymotionbetw onstantratio.Thepinionisthesmallestgearan

rwheel..Arackisarectangularprismwithgear

tisineffectagearwheelwithaninfinitepitchcir nofgearsintransmittingmotionisacamaction ngascams.Geardesignhasevolvedtosucha

otionofeachcontactingpairofteeththevelocit edandthevelocityratioisstillfixedaseachsub ontact.Whentheteethactionissuchthatthed ntangularvelocityproducesaproportionalcons actionistermedaconjugateaction.Theteeths earteethistheinvoluteprofile.

dofapieceofstringisfastenedtotheODofon stringisfastenedtotheODofanothercylinderp rsarerotatedintheoppositedirectionstotensio

hepointonthestringmidwaybetweenthecylind lefthandcylinderrotatesCCWthepointmoves

pson.Thepointmovesawayfromtherightha Thepointtracestheinvoluteformofthegeartee

pendent

Materials.....Basic

..Design

earsareincluded

entwoshafts, dthelargergear

teethmachined

lediameter.In eachpairof

levelthat ratioofthegears

equentpairof rivingtooth

tantvelocityofthe apeuniversally

cylinderandthe ralleltothefirst thestring(see

erPis owardsthis

ndcylinderasthe th.


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Thelinesnormaltothepointofcontactofthegearsalwaysintersectsthecentrelinejoiningthegearcentresatonepointcalledthepitchpoint.Foreachgearthecirclepassingthroughthepitchpointiscalledthepitchcircle.Thegearratioisproportionaltothediametersofthetwopitchcircles.Formetricgears(asadoptedbymostoftheworldsnations)thegearproportionsarebasedonthemodule.

m=(PitchCircleDiameter(mm))/(Numberofteethongear).

IntheUSAthemoduleisnotusedandinsteadtheDiametricPitchd pisused

dp=(NumberofTeeth)/DiametricalPitch(inches)

Profileofastandard1mmmodulegearteethforagearwithInfiniteradius(Rack).

Othermoduleteethprofilesaredirectlyproportion.e.g.2mmmoduleteethare2xthisprofile

Manygearstrainsareverylowpowerapplicationswithanobjectoftransmittingmotionwithminiumtorquee.g.watchandclockmechanisms,instruments,toys,musicboxesetc.Theseapplicationsdonotrequiredetailedstrengthcalculations.

StanStanStanStandardsdardsdardsdards

AGMA2001-C95orAGMA-2101-C95FundamentalRatingfactorsandCalculationMethodsforinvoluteSpurGearandHelicalGearTeeth

BS436-4:1996,ISO1328-1:1995..Spurandhelicalgears.Definitionsandallowablevaluesofdeviationsrelevanttocorrespondingflanksofgearteeth


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BS436-5:1997,ISO1328-2:1997..Spurandhelicalgears.Definitionsandallowablevaluesofdeviationsrelevanttoradialcompositedeviationsandrunoutinformation

BSISO6336-1:1996..Calculationofloadcapacityofspurandhelicalgears.Basicprinciples,introductionandgeneralinfluencefactors

BSISO6336-2:1996..Calculationofloadcapacityofspurandhelicalgears.Calculationofsurfacedurability(pitting)

BSISO6336-3:1996..Calculationofloadcapacityofspurandhelicalgears.Calculationoftoothbendingstrength

BSISO6336-5:2003..Calculationofloadcapacityofspurandhelicalgears.Strengthandqualityofmaterials

Ifitisnecessarytodesignagearboxfromscratchthedesignprocessinselectingthegearsizeisnotcomplicated-thevariousdesignformuleahaveallbeendevelopedovertimeandareavailableintherelevantstandards.Howeversignificanteffort,judgementandexpertiseisrequiredindesigningthewholesystemincludingthegears,shafts,bearings,gearbox,lubrication.Forthesame

dutymanydifferentgearoptionsareavailableforthetypeofgear,thematerialsandthequality.Itisalwayspreferabletoprocuregearboxesfromspecialisedgearboxmanufacturers

TerminologyTerminologyTerminologyTerminology----spurgearsspurgearsspurgearsspurgears

Diametralpitch(dp)......Thenumberofteethperoneinchofpitchcirclediameter.

Module.(m)......Thelength,inmm,ofthepitchcirclediameterpertooth.

Circularpitch(p)......Thedistancebetweenadjacentteethmeasuredalongtheareatthepitchcirclediameter

Addendum(ha)......Theheightofthetoothabovethepitchcirclediameter.

Centredistance(a)......Thedistancebetweentheaxesoftwogearsinmesh.

Circulartooththickness(ctt)......Thewidthofatoothmeasuredalongtheareatthepitchcirclediameter.

Dedendum(hf)......Thedepthofthetoothbelowthepitchcirclediameter.

Outsidediameter(Do)......Theoutsidediameterofthegear.

BaseCirclediameter(Db)......Thediameteronwhichthe

involuteteethprofileisbased. Pitchcircledia(p)......Thediameterofthepitchcircle. Pitchpoint......Thepointatwhichthepitchcirclediameters

oftwogearsinmeshcoincide.

Pitchtoback......Thedistanceonarackbetweenthepitchcirclediameterlineandtherearfaceoftherack.

Pressureangle......Theanglebetweenthetoothprofileatthepitchcirclediameterandaradiallinepassingthroughthesamepoint.

Wholedepth......Thetotaldepthofthespacebetweenadjacentteeth.


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SpurGearDesignSpurGearDesignSpurGearDesignSpurGearDesign

Thespurgearisissimplesttypeofgearmanufacturedandisgenerallyusedfortransmissionofrotarymotionbetweenparallelshafts.Thespurgearisthefirstchoiceoptionforgearsexceptwhenhighspeeds,loads,andratiosdirecttowardsotheroptions.Othergeartypesmayalsobepreferredtoprovidemoresilentlow-

vibrationoperation.Asinglespurgearisgenerallyselectedtohavearatiorangeofbetween1:1and1:6withapitchlinevelocityupto25m/s.Thespurgearhasanoperatingefficiencyof98-99%.Thepinionismadefromahardermaterialthanthewheel.Agearpairshouldbeselectedtohavethehighestnumberofteethconsistentwithasuitablesafetymargininstrengthandwear.Theminimumnumberofteethonagearwithanormalpressureangleof20desgreesis18.Thepreferrednumberofteethareasfollows

12 13 14 15 16 18 20 22 24 25 28 30 32 34 3840 45 50 54 6064 70 72 75 80 84 90 96 100 120 140 150 180200 220 250


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MaterialsusedforgearsMaterialsusedforgearsMaterialsusedforgearsMaterialsusedforgears

Mildsteelisapoormaterialforgearsasasithaspoorresistancetosurface

loading.Thecarboncontentforunhardenedgearsisgenerally0.4%(min)with0.55%(min)carbonforthepinions.Dissimilarmaterialsshouldbeusedforthemeshinggears-thisparticularlyappliestoalloysteels.Alloysteelshavesuperiorfatiguepropertiescomparedtocarbonsteelsforcomparablestrengths.Forextremelyhighgearloadingcasehardenedsteelsareusedthesurfacehardeningmethodemployedshouldbesuchtoprovidesufficientcasedepthforthefinalgrindingprocessused.

Material Notes applications

Ferrousmetals

Cast IronLow Cost easy tomachine with highdamping

Large moderatepower, commercialgears

Cast SteelsLow cost,reasonablestrength

Power gears withmedium rating tocommercial quality

Plain-Carbon SteelsGood machining,can be heattreated

Power gears withmedium rating tocommercial/mediumquality

Alloy Steels

Heat Treatable toprovide higheststrength and

durability

Highest powerrequirement. Forprecision and high

precisiont

Stainless Steels (Aust)Good corrosionresistance. Non-magnetic

Corrosionresistance with lowpower ratings. Up toprecision quality

Stainless Steels (Mart)

Hardenable,Reasonablecorrosionresistance,magnetic

Low to mediumpower ratings Up tohigh precisionlevels of quality

Non-Ferrousmetals

Aluminium alloys

Light weight, non-corrosive andgoodmachinability

Light dutyinstrument gears upto high precisionquality

Brass alloys

Low cost, non-corrosive,excellentmachinability

low costcommercial qualitygears. Quality up tomedium precision

Bronze alloys

Excellentmachinability, lowfriction and goodcompatability withsteel

For use with steelpower gears.Quality up to highprecision

Magnesium alloys Light weight withpoor corrosion

Ligh weight lowload gears. Quality


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resistance up to mediumprecision

Nickel alloys

Low coefficient ofthermalexpansion. Poor

machinability

Special gears forthermal applicationsto commercial

quality

Titanium alloys

High strength, forlow weight, goodcorrosionresistance

Special light weighthigh strength gearsto medium precision

Di-cast alloysLow cost with lowprecision andstrength

High production,low quality gears tocommercial quality

Sintered powder alloysLow cost, lowquality, moderatestrength

High production,low quality tomoderatecommercial quality

Nonmetals

Acetal (DelrinWear resistant,low waterabsorbtion

Long life , low loadbearings tocommercial quality

Phenolic laminatesLow cost, lowquality, moderatestrength

High production,low quality tomoderatecommercial quality

NylonsNo lubrication, nolubricant, absorbswater

Long life at lowloads to commercialquality

PTFE

Low friction and

no lubrication

Special low friction

gears tocommercial quality

EquationsforbasicgearrelationshipsEquationsforbasicgearrelationshipsEquationsforbasicgearrelationshipsEquationsforbasicgearrelationships

Itisacceptabletomarginallymodifytheserelationshipse.gtomodifytheaddendum/dedendumtoallowCentreDistanceadjustments.Anychangesmodificationswillaffectthegearperformanceingoodandbadways...

Addendum ha=m=0.3183pBase Circlediameter

Db = d.cos

Centredistance

a = ( d g + d p) / 2

Circular pitch p = m.Circular tooththickness

ctt = p/2

Dedendum h f= h - a = 1,25m = 0,3979 pModule m = d /zNumber ofteeth z = d / mOutside D o = (z + 2) x m


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diameterPitch circlediameter

d = z . m ... (d g = gear & d p = pinion )

Wholedepth(min)

h = 2.25 . m

Top landwidth(min) t o = 0,25 . m

Module(m)Module(m)Module(m)Module(m)

Themoduleistheratioofthepitchdiametertothenumberofteeth.Theunitofthemoduleismilli-metres.Belowisadiagramshowingtherelativesizeofteethmachinedinarackwithmodulerangingfrommodulevaluesof0,5mmto6mm

Thepreferredmodulevaluesare

0,50,811,251,52,5345681012162025324050

NormalPressureangleNormalPressureangleNormalPressureangleNormalPressureangle

Animportantvariableaffectingthegeometryofthegearteethisthenormalpressureangle.Thisisgenerallystandardisedat20

o.Otherpressureangles

shouldbeusedonlyforspecialreasonsandusingconsideredjudgment.Thefollowingchangesresultfromincreasingthepressureangle

Reductioninthedangerofundercuttingandinterference Reductionofslippingspeeds Increasedloadingcapacityincontact,seizureandwear Increasedrigidityofthetoothing

Increasednoiseandradialforces

Gearsrequiredtohavelownoiselevelshavepressureangles15oto17.5

o

ContactRatioContactRatioContactRatioContactRatio

Thegeardesignissuchthatwheninmeshtherotatinggearshavemorethanonegearincontactandtransferringthetorqueforsomeofthetime.Thispropertyiscalledthecontactratio.Thisisaratioofthelengthoftheline-of-actiontothebasepitch.Thehigherthecontactratiothemoretheloadissharedbetweenteeth.Itis

goodpracticetomaintainacontactratioof1.2orgreater.Undernocircumstancesshouldtheratiodropbelow1.1.


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Acontactratiobetween1and2meansthatpartofthetimetwopairsofteethareincontactandduringtheremainingtimeonepairisincontact.Aratiobetween2and3means2or3pairsofteetharealwaysincontact.Suchashighcontactratiogenerallyisnotobtainedwithexternalspurgears,butcanbedevelopedinthemeshingofaninternalandexternalspurgearpairorspeciallydesignednon-

standardexternalspurgears.

(Rgo2 - Rgb

2 )1/2 + (Rpo2 - Rpb

2 )1/2 - a sin

contact ratio m =

p cos

Rgo=Dgo/2..RadiusofOutsideDiaofGearRgb=Dgb/2..RadiusofBaseDiaofGearRpo=Dpo/2..RadiusofOutsideDiaofPinionRpb=Dpb/2..RadiusofBaseDiaofPinionp=circularpitch.a=(dg+dp)/2=centerdistance.

SpurgearForces,torques,velocities&PowersSpurgearForces,torques,velocities&PowersSpurgearForces,torques,velocities&PowersSpurgearForces,torques,velocities&Powers

F=toothforcebetweencontactingteeth(atanglepressureangletopitchlinetangent.(N)

Ft=tangentialcomponentoftoothforce(N) Fs=Separatingcomponentoftoothforce =Pressureangle d1=PitchCircleDia-drivinggear(m) d2=PitchCircleDia-drivengear(m) 1=Angularvelocityofdrivergear(Rads/s) 2=Angularvelocityofdrivengear(Rads/s) z1=Numberofteethondrivergear z2=Numberofteethondrivengear P=powertransmitted(Watts) M=torque(Nm) =efficiency

Tangential force on gears F t = F cos

Separating force on gears F s = F t tan

Torque on driver gear T 1 = F t d 1 / 2

Torque on driver gear T 2 = F t d 2 / 2

Speed Ratio = 1 / 2 = d 2 / d 1 = z 2 /z 1

Input Power P 1 = T1 . 1

Output Power P 2 =.T 1 . 2


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SpurgearStrengthanddurabilitycalculationsSpurgearStrengthanddurabilitycalculationsSpurgearStrengthanddurabilitycalculationsSpurgearStrengthanddurabilitycalculations

Designingspurgearsisnormallydoneinaccordancewithstandardsthetwomostpopularseriesarelistedunderstandardsabove:

Thenotesbelowrelatetoapproximatemethodsforestimatinggearstrengths.Themethodsarereallyonlyusefulforfirstapproximationsand/orselectionofstockgears(reflinksbelow).Detaileddesignofspurandhelicalgearsisbestcompletedusingthestandards.Booksareavailableprovidingthenecessaryguidance.Softwareisalsoavailablemakingtheprocessveryeasy.Averyreasonablypricedandeasytousepackageisincludedinthelinksbelow(Mitcalc.com)Thedeterminationofthecapacityofgearstotransfertherequiredtorqueforthedesiredoperatinglifeiscompletedbydeterminingthestrengthofthegearteethinbendingandalsothedurabilityi.eoftheteeth(resistancetowearing/bearing/scuffingloads)..Theequationsbelowarebasedonmethods

usedbyBuckingham..

Bending

ThebasicbendingstressforgearteethisobtainedbyusingtheLewisformula

=Ft/(ba.m.Y)

Ft=Tangentialforceontooth =ToothBendingstress(MPa) ba=Facewidth(mm) Y=LewisFormFactor m=Module(mm)

Note:TheLewisformulaisoftenexpressedas

=Ft/(ba.p.y)

Wherey=Y/andp=circularpitch

Whenagearwheelisrotatingthegearteethcomeintocontactwithsomedegreeofimpact.Toallowforthisavelocityfactor(Kv)isintroducedintotheequation.ThisisgivenbytheBarthequation...

V=thepitchlinevelocity=d./2(m/s)


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TheLewisformulaisthusmodifiedasfollows

=Kv.Ft/(ba.m.Y)

SurfaceDurability

This calculation involves determining the contact stress between the gearteeth and uses the Herz Formula

w=2.F/(.b.l)

w = largest surface pressureF = force pressing the two cylinders (gears) togetherl = length of the cylinders (gear)

b = halfwidth =

d 1 ,d 2 Are the diameters for the two contacting cylinders.1, 2 Poisson ratio for the two gear materialsE 1 ,E 2 Are the Young's Modulus Values for the two gears

To arrive at the formula used for gear calculations the following changes are

madeF is replaced by F t/ cos d is replaced by 2.rl is replaced by WThe velocity factor K v as described above is introduced.Also an elastic constant Z E is created

When the value of E used is in MPa then the units of Cp are MPa = KPa


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The resulting formula for the compressive stress developed is as shownbelow

The dynamic contact stress c developed by the transmitted torque must beless than the allowable contact stress Se...

Note: Values for Allowable stress values Se and ZE for some materials areprovided at Gear Table

r1 = d1 sin /2r2 = d2 sin /2Important Note: The above equations do not take into account the variousfactors which are integral to calculations completed using the relevant

standards. These equations therefore yield results suitable for first estimatedesign purposes only...

DesignProcessDesignProcessDesignProcessDesignProcessToselectgearsfromastockgearcatalogueordoafirstapproximationforageardesignselectthegearmaterialandobtainasafeworkingstresse.gYieldstress/FactorofSafety./Safefatiguestress

Determinetheinputspeed,outputspeed,ratio,torquetobetransmitted Selectmaterialsforthegears(pinionismorehighlyloadedthangear) Determinesafeworkingstresses(uts/factorofsafetyoryieldstress/factorofsafetyor

Fatiguestrength/Factorofsafety)

DetermineAllowableenduranceStressSe Selectamodulevalueanddeterminetheresultinggeometryofthegear Usethelewisformulaandtheenduranceformulatoestablishtheresultingfacewidth Ifthegearproportionsarereasonablethen-proceedtomoredetailedevaluations Iftheresultingfacewidthisexcessive-changethemoduleormaterialorbothandstart

again

Thegearfacewidthshouldbeselectedintherange9-15xmoduleorforstraightspurgears-upto60%ofthepiniondiameter.

InternalGearsInternalGearsInternalGearsInternalGearsAdvantages:

1. Geometryidealforepicyclicgeardesign2. Allowscompactdesignsincethecenterdistanceislessthanforexternalgears.3. Ahighcontactratioispossible.4. Goodsurfaceenduranceduetoaconvexprofilesurfaceworkingagainstaconcave

surface.

Disadvantages:

1. Housingandbearingsupportsaremorecomplicated,becausetheexternalgearnestswithintheinternalgear.

2. Lowratiosareunsuitableandinmanycasesimpossiblebecauseofinterferences.3. Fabricationislimitedtotheshapergeneratingprocess,andusuallyspecialtoolingis


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required.

LewisformfactorLewisformfactorLewisformfactorLewisformfactor.Tableoflewisformfactorsfordifferenttoothformsandpressureangles

NoTeeth

Load Near Tip of TeethLoad at Near Middle ofTeeth

14 1/2 deg 20 deg FD 20 deg Stub 25 deg 14 1/2 deg 20 deg FD

Y y Y y Y y Y y Y y Y y

10 0,176 0,056 0,201 0,064 0,261 0,083 0,238 0,076

11 0,192 0,061 0,226 0,072 0,289 0,092 0,259 0,082

12 0,21 0,067 0,245 0,078 0,311 0,099 0,277 0,088 0,355 0,113 0,415 0,132

13 0,223 0,071 0,264 0,084 0,324 0,103 0,293 0,093 0,377 0,12 0,443 0,141

14 0,236 0,075 0,276 0,088 0,339 0,108 0,307 0,098 0,399 0,127 0,468 0,149

15 0,245 0,078 0,289 0,092 0,349 0,111 0,32 0,102 0,415 0,132 0,49 0,156

16 0,255 0,081 0,295 0,094 0,36 0,115 0,332 0,106 0,43 0,137 0,503 0,16

17 0,264 0,084 0,302 0,096 0,368 0,117 0,342 0,109 0,446 0,142 0,512 0,163

18 0,27 0,086 0,308 0,098 0,377 0,12 0,352 0,112 0,459 0,146 0,522 0,166

19 0,277 0,088 0,314 0,1 0,386 0,123 0,361 0,115 0,471 0,15 0,534 0,17

20 0,283 0,09 0,32 0,102 0,393 0,125 0,369 0,117 0,481 0,153 0,544 0,17321 0,289 0,092 0,326 0,104 0,399 0,127 0,377 0,12 0,49 0,156 0,553 0,176


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22 0,292 0,093 0,33 0,105 0,404 0,129 0,384 0,122 0,496 0,158 0,559 0,178

23 0,296 0,094 0,333 0,106 0,408 0,13 0,390 0,124 0,502 0,16 0,565 0,18

24 0,302 0,096 0,337 0,107 0,411 0,131 0,396 0,126 0,509 0,162 0,572 0,182

25 0,305 0,097 0,34 0,108 0,416 0,132 0,402 0,128 0,515 0,164 0,58 0,185

26 0,308 0,098 0,344 0,109 0,421 0,134 0,407 0,13 0,522 0,166 0,584 0,186

27 0,311 0,099 0,348 0,111 0,426 0,136 0,412 0,131 0,528 0,168 0,588 0,187

28 0,314 0,1 0,352 0,112 0,43 0,137 0,417 0,133 0,534 0,17 0,592 0,188

29 0,316 0,101 0,355 0,113 0,434 0,138 0,421 0,134 0,537 0,171 0,599 0,191

30 0,318 0,101 0,358 0,114 0,437 0,139 0,425 0,135 0,54 0,172 0,606 0,193

31 0,32 0,101 0,361 0,115 0,44 0,14 0,429 0,137 0,554 0,176 0,611 0,194

32 0,322 0,101 0,364 0,116 0,443 0,141 0,433 0,138 0,547 0,174 0,617 0,196

33 0,324 0,103 0,367 0,117 0,445 0,142 0,436 0,139 0,55 0,175 0,623 0,198

34 0,326 0,104 0,371 0,118 0,447 0,142 0,44 0,14 0,553 0,176 0,628 0,235 0,327 0,104 0,373 0,119 0,449 0,143 0,443 0,141 0,556 0,177 0,633 0,201

36 0,329 0,105 0,377 0,12 0,451 0,144 0,446 0,142 0,559 0,178 0,639 0,203

37 0,33 0,105 0,38 0,121 0,454 0,145 0,449 0,143 0,563 0,179 0,645 0,205

38 0,333 0,106 0,384 0,122 0,455 0,145 0,452 0,144 0,565 0,18 0,65 0,207

39 0,335 0,107 0,386 0,123 0,457 0,145 0,454 0,145 0,568 0,181 0,655 0,208

40 0,336 0,107 0,389 0,124 0,459 0,146 0,457 0,145 0,57 0,181 0,659 0,21

43 0,339 0,108 0,397 0,126 0,467 0,149 0,464 0,148 0,574 0,183 0,668 0,213

45 0,34 0,108 0,399 0,127 0,468 0,149 0,468 0,149 0,579 0,184 0,678 0,216

50 0,346 0,11 0,408 0,13 0,474 0,151 0,477 0,152 0,588 0,187 0,694 0,221

55 0,352 0,112 0,415 0,132 0,48 0,153 0,484 0,154 0,596 0,19 0,704 0,224

60 0,355 0,113 0,421 0,134 0,484 0,154 0,491 0,156 0,603 0,192 0,713 0,227

65 0,358 0,114 0,425 0,135 0,488 0,155 0,496 0,158 0,607 0,193 0,721 0,23

70 0,36 0,115 0,429 0,137 0,493 0,157 0,501 0,159 0,61 0,194 0,728 0,232

75 0,361 0,115 0,433 0,138 0,496 0,158 0,506 0,161 0,613 0,195 0,735 0,234

80 0,363 0,116 0,436 0,139 0,499 0,159 0,509 0,162 0,615 0,196 0,739 0,235

90 0,366 0,117 0,442 0,141 0,503 0,16 0,516 0,164 0,619 0,197 0,747 0,238

100 0,368 0,117 0,446 0,142 0,506 0,161 0,521 0,166 0,622 0,198 0,755 0,24150 0,375 0,119 0,458 0,146 0,518 0,165 0,537 0,171 0,635 0,202 0,778 0,248

200 0,378 0,12 0,463 0,147 0,524 0,167 0,545 0,173 0,64 0,204 0,787 0,251

300 0,38 0,122 0,471 0,15 0,534 0,17 0,554 0,176 0,65 0,207 0,801 0,255

Rack 0,39 0,124 0,484 0,154 0,55 0,175 0,566 0,18 0,66 0,21 0,823 0,262

Links to Gear Design

1. Excelcalcs;...Siteincludesnumberofexcel

basedgearcalculationsheets.(annualsubscription)


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2. OnDrives-precisiongears...SupplierofGears/Gearboxes,Includingtechnicalinfo(download)

3. GearDesign...AcomprehensivesourceofGearDesignInformation

4. Efunda...Efunda->DesignCentre->Gears..

SomeusefulNotes.5. GearDesignTopics...Asiteproviding

amazingmotiongraphicsofdifferentgeartypes

6. SEWEurodrive...AlltheinformationonGearboxesyouwillneed

7. QualityTransmissionComponents...SupplierwithdownloadableGearDesignHandbook

8. StockDriveProducts=SterlingInstruments...Supplierwithlargequantityofdownloadabledriveinformation

9. Mitcalc...Excelbasedsoftwareincludingcodedgeardesign

10.Lenze...Drivesystemsupplierwithgearedmotorsection11.DavallGears...UKSupplierofstockgearsand

gearboxes12.Muffettgears...UKSupplierofstockgearsand

gearboxes13.GearDesignLectureNotes...Plymouth.ac.uk-

UsefulNotesongearstrengthdesign14.GearStress(PDF)...Averyuseful

downloadablepaperbasedonAGMAstandardsforgeardesign

15.DRGears...Onestopresourceforgearmanufacturers

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Gear Design 1

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