memoriu tehnic proiect om

8/10/2019 Memoriu Tehnic Proiect OM

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UNIVERSITATEA TRANSILVANIA DIN BRAOV

1A!ULTATEA DE IN+INERIE #E!ANI!2

Disciplina Organe de Maini

ROIE!T DE AN LA DIS!ILINAOr"ane de #a$ini II

Autor% Student chiopu Sorin te&an +rupa% ,,,,

!oordonatori $tiin3i&ici% ro&* univ* dr* in"* +heor"he #O+AN-Silviu BUTNARIU

Dr* in"* Silviu OA

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CUPRINS

Introducere................................................................................................................................. 6

A. MEMORIUL JUSTIFICATIV.................................................................................................1.Tematica i !c"ema!tructura#$con!tructi%&................................................................................

1.1. Tematica i !'eci(ica)ii de 'roiectare...............................................................................1.*. Sc"ema !tructura#$con!tructi%&........................................................................................1.+. ,m'&r)irea ra'ortu#ui de tran!mitere 'e tre'te. Parametri cineto!tatici............................

*.Ca#cu#u# de 'redimen!ionare a an-renae#or..............................................................................*.1. Ca#cu#u# de 'redimen!ionare a an-renau#ui conic..........................................................

*.*. Ca#cu#u# de 'redimen!ionare a an-renau#ui ci#indric...................................................... *.+. Ca#cu#u# de 'redimen!ionare a ar/ori#or..........................................................................+. Sc"ema cinematic&....................................................................................................................

0.Ca#cu#u# -eometriei an-renau#ui conic......................................................................................Ca#cu#u# -eometriei an-renau#ui ci#indric.................................................................................6. Ca#cu#u# de %eri(icare a an-renau#ui ci#indric 2cu M3ESI4N5................................................Ca#cu#u# (or)e#or din an-renae...................................................................................................

.1. Sc"ema (or)e#or.............................................................................................................. .*. For)e#e din an-renau# conic .......................................................................................... .+. For)e#e din an-renau# ci#indric .....................................................................................7. Ca#cu#u# ar/ori#or...................................................................................................................... 7.1. Sc"ema de 8nc&rcare a ar/ore#ui intermediar................................................................... 7.*. Ca#cu#u# de %eri(icare a ar/ore#ui intermediar 2cu M3ESI4N5........................................9. A#e-erea i %eri(icarea montau#ui cu ru#men)i a# ar/ore#ui intermediar..................................

1:. A#e-erea i %eri(icarea a!am/#&rii 'rin 'an& 'ara#e#& dintre roata conic& i ar/ore#eintermediar.............................................................................................................................

11. A#e-erea i u!ti(icarea !i!temu#ui de un-ere..........................................................................1*. A#e-erea i u!ti(icarea di!'o;iti%e#or de etanare..................................................................


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INTRO3UCERE

Sco'u# 'roiectu#ui de an #a di!ci'#ina Organe de maini e!te !& de;%o#te a/i#it&)i#e'ractice a#e !tuden)i#or de 'roiectare i !inteti;are a cunotin)e#or de mecanic&> re;i!ten)amateria#e#or> te"no#o-ia materia#e#or i re're;entare -ra(ic& 8n decur!u# ani#or I i II> 'recumi modu# 8n care acetia 'ot re;o#%a 8n mod inde'endent o #ucrare de 'roiectare> 'e /a;aa#-oritmi#or> metode#or !'eci(ice i 'ro-rame#or din domeniu.

Reductoare de turaie de u; -enera# !unt tran!mi!ii cu ro)i din)ate care au !co'u#reducerii tura)iei concomitent cu m&rirea 2am'#i(icarea5 momentu#ui de tor!iune !e (o#o!e!cca unit&)i inde'endente 8n di%er!e tran!mi!ii 'ermi)Bnd uti#i;area de motoare de ac)ionare detura)ii mari i -a/arite redu!e 'entru 'roce!e!i!teme de #ucru antrenate cu %ite;e redu!e !erea#i;ea;& 8ntr$o -am& #ar-& de ti'odimen!iuni 8n 8ntre'rinderi !'ecia#i;ate cu e(icien)&economic& ridicat&.

Princi'a#e#e avantaje2ra'ortate #a a#te ti'uri de tran!mi!ii5 care au du! #a uti#i;area 'e!car& #ar-& a tran!mi!ii#or cu ro i din ate !unt?

$ a!i-ur& ra'ort de tran!mitere con!tant

$ au dura/i#itate i !i-uran)& mare 8n (unc)ionare$ au ca'acitate mare de tran!mitere a momentu#ui de tor!iune$ au randamentu# ridicat$ nece!it& 8ntre)inere uoar& 8n e@'#oatare.

Cu toate ace!tea> reductoare#e de tura ie nece!it& 'reci;ie ridicat& de e@ecu ie i monta tran!mit ocuri#e i %i/ra ii#e> iar 8n tim'u# e@'#oat&rii 'roduc ;-omote i %i/ra ii.

Reductoare#e conico$ci#indrice modi(ic& direc)ia de tran!mitere a !arcinii rea#i;ea;&ra'oarte de tran!mitere ma@ime ima@D 0> iar trea'ta conic& !e (o#o!ete totdeauna ca trea't&ra'id& 2cu %ite;a ma@im&5.

Autoru#.


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MEMORIUL TENIC


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Fig. 1.2Schema structural-constructiv general

1.* SCEMA STRUCTURAL$CONSTRUCTIVH

,n (i-. 1.* !e 're;int& !c"ema !tructura#$con!tructi%& -enera#& a reductoare#or conico$ci#indrice 8n dou& tre'te. 3in 'unct de %edere (unc)iona# !e e%iden)ia;& urm&toare e#emente? I

an-rena conic orto-ona# cu dantur& 8nc#init& 2cur/&5 II an-rena ci#indic cu dantur& 8nc#inat& 1I

'inion conic *I roat& conic& 1II 'inion ci#indric *II roat& ci#indric& A1 ar/ore#e de intrare

A* ar/ore#e intermediar A+ ar/ore#e de ieire $ #a-&ru# A a# ar/ore#ui A1 $ #a-&ru# < a#

ar/ore#ui A1 $ #a-&ru# A a# ar/ore#ui A* $ #a-&ru# < a# ar/ore#ui A* $ #a-&ru# A a#

ar/ore#ui A+ $ #a-&ru# < a# ar/ore#ui A+.

3in 'unct de %edere con!tructi%> reductoru# de tura)ie (ormea;& un an!am/#u com'u! din!u/an!am/#e i e#emente con!tructi%e. Su/an!am/#e#e !unt !tructuri inde'endente> care !ee%iden)ia;& 'rintr$un -ru' com'act com'u!> 8n con(i-ura)ie minima#&> din ce# 'u)in dou& e#ementecon!tructi%e !au din a#te !u/an!am/#e i e#emente con!tructi%e> 8n interac)iune 'ermanent&> (ormate

)inBndu$!e cont> cu 'rec&dere> de te"no#o-ii#e de monta> de 8ntre)inere i de e@'#oatare.,n ca;u# reductoare#or conico$ci#indrice din (i-. 1.* !e de(ine!c urm&toare#e !u/an!am/#e? SC

!u/a!am/#u# carca!& $ !u/an!am/#u# ar/ore#ui de intrare> (ormat din 'inionu# conic 21I5 (i@at

'e ar/ore#e de intrare 2A15 care #a rBndu# !&u e!te (i@at 'e dou& #a-&re 2 i 5> !e !'riin& 'e

!u/an!am/#u# carca!a SC $ !u/an!am/#u# ar/ore#ui intermediar> (ormat din roata conic& 2*I5 i

'inionu# ci#indric 21II5 (i@ate 'e ar/ore#e intermediar 2A*5 care #a rBndu# !&u e!te (i@at 'e dou& #a-&re

2 i 5> !e !'riin& 'e !u/an!am/#u# carca!a SC $ !u/an!am/#u# ar/ore#ui de ie ire > (ormat

din roata ci#indric& 2*II

5 (i@at& 'e ar/ore#e de ieire 2A+5 care #a rBndu# !&u e!te (i@at 'e dou& #a-&re 2i 5> !e !'riin& 'e !u/an!am/#u# carca!a SC.

1.+ ,MPHRIREA RAPORTULUI 3E TRANSMITERE PETREPTE. PARAMETRI CINETOSTATICI.

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Fig. 1.3Schema structural a angrenajului conicortogonal

Reductoru# de tura)ie de'roiectat are dou& tre'te2an-renae5. ,n %ederea o/)ineriunei !tructuri o'time 2ro)i#econdu!e c%a!ie-a#e5 !e im'une cara'ortu# de tran!mitere a# tre'tei I

2an-renau# conic5 iI

D :>* iRD *>.Ra'ortu# de tran!mitere a#tre'tei a II$a 2an-renau# ci#indric5e!te?

iIID iR iID 0.

Parametrii (unc)iona#i cineto!tatici 2tura)ia> 'uterea> momentu# de tor!iune5 #a ni%e#u#ar/ori#or reductoru#ui !unt?

n1D niD +::: rotmin> P1D PiD *7 K> Mt1D MtiD 791*Nmm 2ar/ore#e A15

n* D n1iI D 1*:: rotmin> P* D P1ID *6>77 K> Mt* D Mt1iIID *1+9:0>7 Nmm2ar/ore#e A*5n+D n*iIID n12iIiII5 D n1iRD +:: rotmin> P+D P*IID P1IIID P1RD *6>: K>Mt+D Mt* iIIIID Mt1 iIiIIIIID Mt1 iRRD 7*99:>6*0 Nmm 2ar/ore#e A+5.

,n ace!te re#a)ii !$a con!iderat ID :>96 $ randamnetu# an-renau#ui conic> IID :>9 $ randamentu#an-renau#ui ci#indric i RD IIID :>90.

*. CALCULUL 3E PRE3IMENSIONARE A AN4RENAJELOR

*.1CALCULUL 3E PRE3IMENSIONAREA A AN4RENAJULUICONIC

I* Date de proiectare

a. Tura)ia #a intrare 2'inion5? n1D +::: rotmin.Fig. 2.1Schema

funcional a angrenajului conic.b. Puterea #a intrare? P1D *7 K> de unde re;u#t& %a#oarea momentu#ui de tor!iune?

D 89127Nmm 2*.15

c. Ra'ortu# de an-renare? u D *>.d. Un-"iu# dintre a@e#e ro)i#or? D 9:oi !e determin& !emiun-"iuri#e?

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D *1>7o> D 67>*o. 2*.*5

e. Num&ru# de an-renae identice 8n 'ara#e#? Q D1.f. 3urata de (unc)ionare? L"D 1:::: ore.g. Ti'u# danturii? drea't&.h. Condi)ii de (unc)ionare? maina motoare motor a!incron in!ta#a)ia antrenat& uti#a

te"no#o-ic indu!tria#> tem'eratura 2$*:7:5oC caracteri!tici#e mediu#ui 'ra( i ume;ea#&.i. Condi)ii eco#o-ice? uti#i;area de materia#e i te"no#o-ii eco> recic#area materia#e#or> 'rotec)ia

%ie)ii.

II* Ale"erea materialului( tratamentelor termice $i tehnolo"iei

A%Bnd 8n %edere c& !arcina de tran!mi! e!te m&rit& 2T 1D 791* Nmm5 !e ado't& 'entruro)i#e an-renau#ui o)e# de cementare marca *1MoMnCr1* c&ruia i !e a'#ic& tratamentu# decementare com'u! din tratamentu# termoc"imic de car/urare 28m/o-&)irea !tratu#ui !u'er(icia# in

C5 urmat de tratamente#e termice de cire i re%enire oa!&. A!t(e#> !e o/)ine durit&)i#e (#ancuri#ordin)i#or 76: RC 'e adBncimea de :71>* mm i mie;u#ui +::++: cementare i recti(icare dantur&.Pentru ca#cu#u# #a contact 8n (unc)ie de caracteri!tici#e materia#u#ui 2 rD 11:: MPa> :* D

7: MPa> E D *1:::: MPa i D :>+5 i 8n (unc)ie de durit&)i#e im'u!e !e ado't& ten!iunea#imit& #a contact #imD 1+: MPa i ten!iunea #imit& #a 8nco%oiere F#imD 0: MPa.

III* !alculul de predimensionare

3eoarece re#a)ii#e de dimen!ionare a an-renae#or> #a contact i #a 8nco%oiere> con)in (actoricare de'ind de 'arametrii ce urmea;& !& (ie determina)i> 're#iminar> !e (ace un ca#cu# de

'redimen!ionare.A#e-Bnd ca 'arametru de dimen!ionare modu#u# e@terior> 'entru !o#icitarea #a contact>

D +>16 mm> 2*.+5

i 'entru !o#icitarea #a 8nco%oiere>

D *> mm 2*.05

unde> ;1D *: ;* D u;1D : A D 1>* % D 1>* Wd D :>+ NL1D6: n1 L"Q D 1.71:9 cic#uriNL*D6:n1L"Q urD *1: cic#uri X D 1>1 Y D 1>* Z[D :>9* ZD +>0 ZED 19: MPa1* SminD1 ZN1D 1 ZN*D 1 ZN D min 2ZN1> ZN*5D1 PD #imZNSminD 1+: MPa FX D 1>1 FY D 1>*\[D :> \X D :>9 \Sa1 D 1>6 \Sa* D 1>7 \Fa1D *>7 \Fa*D *>+\N1>* D 1> SFminD 1> \ND 1 FP1>* D F#im\N1>* SFminD +:: MPa.

3in re#a)ii#e 2*.+5 i 2*.05 re;u#t& c& !o#icitarea 'rinci'a#& a an-renau#ui e!te #a contact i !econ!ider& 'entru ca#cu#e> 8n continuare> meD +>16 mm.

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IV* roiectarea &ormei constructive*

3in con!iderente (unc iona#e> con!tructi%e i!au te"no#o-ice !$a conce'ut con(i-ura ia ro i#or din ate?

!$a ado'tat con(orm STAS 7** me D 0 mm. deD me;1>* de1D 7: mm> de*D *:: mm

ReD D 1:> mm

/ D ydde1D *0mm.

Fig. 2.1Schema cinematic a angrenajului conic

*.* CALCULUL 3E PRE3IMENSIONAREA A AN4RENAJULUICILIN3RIC

I* Date de proiectare

a. Tura)ia #a intrare 2'inion5? n*D 1*::rotmin.

b. Puterea #a intrare? P*D *6>77 K> deunde re;u#t& %a#oarea momentu#ui detor!iune?

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D *1+9:Nmm 2*.5

c. Ra'ortu# de an-renare? u D 0.Fig. 2.2Schema func ional a angrenajului cilindric

d. Num&ru# de an-renae identice 8n 'ara#e#? Q D1.e. 3urata de (unc)ionare? L"D 1:::: ore.

f. Ti'u# danturii? 8nc#inat&.g. Parametrii -eometrici im'u i? di!tan a dintre a@e a > !tandardi;area di!tan ei dintre a@eun-"iu# de 8nc#inare a danturii diametru# 'inionu#ui !au modu#u# danturii.

h. Condi)ii de (unc)ionare? maina motoare motor a!incron in!ta#a)ia antrenat& uti#ate"no#o-ic indu!tria#> tem'eratura 2$*:7:5oC caracteri!tici#e mediu#ui 'ra( i ume;ea#&.

i. Condi)ii eco#o-ice? uti#i;area de materia#e i te"no#o-ii eco> recic#area materia#e#or> 'rotec)ia%ie)ii.


A%Bnd 8n %edere c& !arcina de tran!mi! e!te m&rit& 2T *D *1+9: Nmm5 !e ado't& 'entru

ro)i#e an-renau#ui o)e# de cementare marca *1MoMnCr1* c&ruia i !e a'#ic& tratamentu# decementare com'u! din tratamentu# termoc"imic de car/urare 28m/o-&)irea !tratu#ui !u'er(icia# inC5 urmat de tratamente#e termice de cire i re%enire oa!&. A!t(e#> !e o/)ine durit&)i#e (#ancuri#ordin)i#or 76: RC 'e adBncimea de :71>* mm i mie;u#ui +::++: cementare i recti(icare dantur&.

Pentru ca#cu#u# #a contact 8n (unc)ie de caracteri!tici#e materia#u#ui 2 rD 11:: MPa> :* D7: MPa> E D *1:::: MPa i D :>+5 i 8n (unc)ie de durit&)i#e im'u!e !e ado't& ten!iunea#imit& #a contact #imD 1+: MPa i ten!iunea #imit& #a 8nco%oiere F#imD 0: MPa.


3eoarece re#a)ii#e de dimen!ionare a an-renae#or> #a contact i #a 8nco%oiere> con)in (actoricare de'ind de 'arametrii ce urmea;& !& (ie determina)i> 're#iminar> !e (ace un ca#cu# de

'redimen!ionare.A#e-Bnd ca 'arametru de dimen!ionare modu#u# e@terior> 'entru !o#icitarea #a contact>

D *>0* mm> 2*.65

i 'entru !o#icitarea #a 8nco%oiere>

D *>6 mm 2*.5

unde> ;1 D ** ;* D u;1 D 77 A D 1>* % D 1>+ Wa D :>0 NL1D6: n1 L"Q D *1: cic#uriNL*D6:n1L"Q urD 171: cic#uri X D 1>1* Y D 1>* Z[D :>90 ZD *>0 ZED 19: MPa1* SminD1>+ ZN1D 1 ZN*D 1 ZN D min 2ZN1> ZN*5D1> SFminD 1>+ PD #imZNSminD 116>9* MPa FX D1>1* FY D 1>* \[D :>7 \X D :>9+ \Sa1 D 1>6 \Sa* D 1>9 \Fa1D *> \Fa*D *>* \N1>* D 1> \ND 1FP1>* D F#im\N1>* SFminD +:: MPa.

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3in re#a)ii#e 2*.65 i 2*.5 re;u#t& c& !o#icitarea 'rinci'a#& a an-renau#ui e!te #a 8nco%oiere i!e con!ider& 'entru ca#cu#e> 8n continuare> m D *>6 mm.

IV* roiectarea &ormei constructive*

3in con!iderente (unc iona#e> con!tructi%e i!au te"no#o-ice !$a conce'ut con(i-ura ia ro i#or din ate?

mnD mco!X D *>* mm> iar con(orm STAS 7** !$a ado'tat mnD + mm.

mm 2STAS 6:5

unde YtD *:>*7] YtD 1:>71].

;d1D 60 mm d*D *6 mm.

/ D yaaD 60 mm.

Fig. 2.3Schema cinematic a angrenajului cilindric

*.+ CALCULUL 3E PRE3IMENSIONAREA A AR


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b. Puteri#e? P1 D Pi D *7 K> P*D *6>77 K> P+ D *6>: K> de unde re;u#t& %a#ori#emomente#or de tor!iune? Mt1 D MtiD 791* Nmm Mt*D *1+9: Nmm Mt+D 7*99:>6*Nmm

c. 3urata de (unc ionare ? L "D 1:::: ored. Condi)ii de (unc)ionare? maina motoare motor a!incron in!ta#a)ia antrenat& uti#a

te"no#o-ic indu!tria#> tem'eratura 2$*:7:5oC caracteri!tici#e mediu#ui 'ra( i ume;ea#&.

e. Condi)ii eco#o-ice? uti#i;area de materia#e i te"no#o-ii eco> recic#area materia#e#or> 'rotec)ia%ie)ii.


Materia#e#e 'entru ar/ori tre/uie !& 8nde'#inea!c& urm&toare#e condi)ii? re;i!ten)& mecanic&ridicat& modu# de e#a!ticitate ridicat 're#ucra/i#itate /un& i co!t redu!. Materia#e#e din care !ee@ecut& ar/orii dre')i !e a#e- (unc)ie de condi)ii#e de re;i!ten)& i ri-iditate im'u!e> de naturaor-ane#or de maini !u!)inute i de ti'u# #a-&re#or 2cu a#unecare !au cu ro!to-o#ire5.

Te"no#o-ia de (a/rica)ie a ar/ori#or i o!ii#or con!t& 8n? !trunirea !u'ra(e)e#or ci#indrice !auconice i a (i#ete#or> (re;area cana#e#or de 'an& !au a cane#uri#or o'era)ii e@ecutate 8nainte detratamentu# termic recti(icarea (u!uri#or> a 'or)iuni#or de ca#are> a !u'ra(e)e#or cane#uri#or o'era)ii e@ecutate du'& tratamentu# termic.

Semi(a/ricate#e 'entru ar/ori i o!ii 'ot (i? /are #aminate> 'entru diametre !u/ 10: mm/are #aminate cu (orare u#terioar& /are #aminate cu matri)are u#terioar&> 8n ca;u# 'roduc)iei de de!erie mare !emi(a/ricate turnate> 8n ca;u# ar/ori#or i o!ii#or de dimen!iuni (oarte mari. E@ecu)iaar/ori#or din /are #aminate cu (orare !au matri)are u#terioar& conduce #a o/)inerea unui !emi(a/ricata'ro'iat de (orma (ina#& a ar/ore#ui cu im'ortante economii de materia#> mano'er& i ener-ie i#a rea#i;area unui (i/ra continuu care urm&rete (orma ar/ore#ui> cu e(ect direct a!u'ra m&ririire;i!ten)ei ace!tuia.

Tab. 2.1!nforma ii sintetice despre material i tratamente termice

"aterialul

#ratamentul termic$duritatea%& sau%R'

#ensiunea de

rupere

#ensiunea de

curgere

#ensiunea admisi(il la solicitarea de)ncovoiere$dup ciclul

Static*!+

,ulsator*!!+lternant simetric

*!!!+

*1MoMnCr1* Cementare11::

MPa7:

MPa+:

MPa1: MPa 1:: MPa


'alculul apro.imativ al diametrelor ar(orilor care susinro)i#e?

unde atD *: MPa.

dA1D + mmdA*D 0 mmdA+D 6 mm.

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+. SCEMA CINEMATICH

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La o roat& conic&> dimen!iuni#e din)i#or conici di(er& atBt 'e 8n)imea dinte#ui> cBt i 'e#&)imea danturii. Pe 8n)imea dinte#ui !e de(ine!c e#emente#e -eometrice 'e conu# de ca' 2indice a5>

'e conu# de di%i;are$ro!to-o#ire 2(&r& indice5 i 'e conu# de 'icior 2indice f5. Pe #&)imea ro)ii>dantura !e de(inete nu 'e !(ere> ci 'e conuri (ronta#e tan-ente #a !(era re!'ecti%& i 'er'endicu#are

'e conuri#e de di%i;are$ro!to-o#ire. Pe #&)imeadanturii e@i!t& o in(initate de conuri (ronta#e

2!u'#imentare5> dar dintre ace!tea intere!ea;&e#emente#e -eometrice 'e conu# !u'#imentar e@terior2cu indice e5> 'e conu# !u'#imentar median 2indicem5 i 'e conu# !u'#imentar interior 2indice i5.

Pe conu# !u'#imentar e@terior !e re'roducee#emente#e !tandardi;ate a#e 'ro(i#u#ui de re(erin)&de #a roata '#an& i modu#u# !tandardi;at. For)e#e i

ca#cu#u# de re;i!ten)& !e e(ectuea;& 'e conu#!u'#imentar median.

Fig. 4.1,arametrii geometrici principali ai angrenajului conic

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*+

E#ementu# -eometric Sim/o# Re#a)ia de ca#cu#

,n)imea e@terioar& a dinte#ui ha h^a me

,n)imea e@terioar& a'icioru#ui dinte#ui

hfe 2ha^+ c

^5me

,n)imea e@terioar& a dinte#ui he hae + hfe

3iametru# de di%i;are e@terior de12 *5 mez12 *5

3iametru# de di%i;are median dm12 *5 d e1 2 *5

1 +dm !in 1

Modu#u# median mm d m1 z1

L&)imea danturii ( dm d m1 2( :>+Re5

Lun-imea median& a -eneratoareide di%i;are

Rm d m1* !in

Lun-imea e@terioar& a -eneratoareide di%i;areR

e Rm _ :> (

Un-"iu# 'icioru#ui dinte#ui f tan f = hfe Re

Un-"iu# ca'u#ui dinte#ui a tana = hae Re

Un-"iu# conu#ui de ca' a12 *5 12 *5 +

Un-"iu# conu#ui de 'icior f 12 *5 12 *5 f

3iametru# cercu#ui de ca' e@terior ae12 *5

e12 *5 + *hae co!12 *5

3iametru# cercu#ui de 'icior e@terior fe12 *5 e12 *5 *hfe co!12 *5

,n)imea e@terioar& a conu#ui de ca' %ae12 *5 Re co!12 *5 hae !in12

,n)imea interioar& a conu#ui de ca' %ai12 *5 %ae12 *5 (co!12*5


20/54

. CALCULUL 4EOMETRIEI AN4RENAJULUI CILIN3RIC

3in !tudiu# cinematic a# an-ren&riire;u#t& c& o (unc)ionare #initit& a unui an-renae!te condi)ionat& de e@i!ten)a unui -rad de

aco'erire / cBt mai mare. Acea!ta !e 'oaterea#i;a dac& !e 8n#ocuie!c din)ii dre')i cu din)i8nc#ina)i. 3in)ii (iind 8nc#ina)i cu un-"iu# 0>an-renarea !e (ace tre'tat> ;-omotu# i %i/ra)ii#ereducBndu$!e.

E#emente#e -eometrice !e de(ine!c 8ndou& '#ane? unu# 'er'endicu#ar 'e a@a ro)ii 2'#an(ronta# t t5 8n care !e de(ine!c dimen!iuni#erea#e i unu# 'er'endicu#ar 'e direc)ia dinte#ui2'#an norma# n$n5> 8n care e#emente#e -eometrice!unt ace#eai ca #a ro)i#e ci#indrice cu din)i dre')i.Fig. 4.1,arametrii geometrici principali

ai angrenajului cilindricCa urmare a de(inirii e#emente#or -eometrice 8n ce#e * '#ane> %or a'are no)iuni#e de modu#

(ronta#mt> 'a! (ronta#pt> i re!'ecti% modu# norma# mn i 'a! norma# pn.mtD mnco!X 'tD 'nco!X

,rincipalele elemente geometrice !unt?$ diametru# de di%i;are> d?

$ 8n)imea ca'u#ui dinte#ui> ha? D1.

- nlimea piciorului dintelui, hf:

$ 8n)imea dinte#ui?

$ diametru# de ca'> da?

$ diametru# de 'icior> df?

$ diametru# cercu#ui de /a;&> d(?

$ diametru# de ro!to-o#ire> d1?

$ diametru# de ca'> da?

- diametru# de 'icior> df?

*0


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6. CALCULUL 3E VERIFICARE A AN4RENAJULUI CILIN3RIC2CU M3ESI4N5

Ca#cu#u# de %eri(icare?S ` SminSFD ma@2SF1>SF*5 ` SFmin.'azuri posi(ile2a. ce#e dou& ine-a#it&)i !unt re!'ectate cu a/ateri redu!e !au ce# 'u)in una cu a/atere redu!&>

!o#icit&ri#e !unt %eri(icate a'ro'iat !au> re!'ecti%> ce# 'u)in una e!te cu %eri(icare a'ro'iat&> ian-renau# nu e!te !u'radimen!ionat maor i !e 'oate trece #a urm&toru# 'a!.

*


22/54

b. ce#e dou& ine-a#it&)i !unt re!'ectate cu a/ateri maore> !o#icit&ri#e !unt %eri(icate> an-renau#e!te !u'radimen!ionat maor i e!te 'o!i/i#> 8n ca;uri /ine de(inite> !& r&mBn& nemodi(icat !au !&!e modi(ice an-renau# (&cBnd o dimenionare.

c. una din inecua)ii nu e!te re!'ectat&> una din !o#icit&ri nu e!te %eri(icat& i !e %a (ace odimen!ionare.

3in ana#i;a in(orma ii#or o(erite de 'ac"etu# M3ESI4N *3ig 45+!e 'oate o/!er%a cu u urin & c&

ce#e dou& ine-a#it& i !unt re!'ectate i !e 'oate trece #a 'a!u# urm&tor? Universitatea Brasov

Program : MDESIGN User : Customer:

Module version: 13.2 Date : 14.04.2010 Proj. Nr:

Spur Gear, Gear Rack

Input data: Spur Gear, Gear RackCalculation method Spur gear

Calculation variants All Calculation standard ISO 6336 Type of toothing External toothingSpur gear geometry

Basic data Normal modulus mn= 3 mm Helical angle b: 10 Centre distance a : 0 mm

Driving element Pinion Input of geometry z1, i Number of teeth (pinion) z1= 22 Number of teeth (wheel) z2= 88 Translation ratio i = 4

Pinion Wheel

Tooth width b =

70

64 mm

Input methode topland shortening Input of k1 and k2

Topland shortening k : 1.5174 1.5174 mmAddendum modification according to DIN 3992/3993

Input methode profile shift coefficients Input of x1 and x2 Profile shift coefficient (pinion) x1= 0.24 Profile shift coefficient (wheel) x2= -2.248Basic gear rack Pinion Wheel

Tip clearance factor cP* = 0.25 0.25 Root fillet radius factor rf P* = 0.25 0.25

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Pressure angle ap= 20 Tooth-tip thickness factor san* = 0.2

Pinion Wheel Tooth-tip height factor haP* = 1 1 Residual fillet undercut spr: 0 0 mm

Cutter data Pinion Wheel

Number of cutter teeth z0: 0 0 Basic gear rack profile shift coefficient x0: 0 0Spur Gear Calculation - Strength

Drive data Load case Nominal load Application factor KA= 1.25 Performance P = 26.88 kW Rotation speed (pinion) n1= 1200 1/min

Lifetime Lh= 10000 hLubrication

Viscosity class for 40 noil= 100cSt Oil temperature oil= 50 C Force level (according to FZG-test) 12 Type of oil distribution Splash lubricationMaterial selection

Pinion - materials (strength values) according to Own assignment

Material designation 21MoMnCr12 Material number 1.0037 Material group Casehardening steel Heat treatment / State trial hardened Standard dimension dNm= 40 mm Standard dimension dNp= 40 mm Ultimate strength for dNm RmN= 1100 N/mm Yield point for dNp RpN= 850 N/mm Tooth root strength !Flim= 450 N/mm Surface durability (pitting) !Hlim= 1530 N/mm

Type of Material

-

Modulus of elasticity E = 210000 N/mm Poisson's ratio n= 0.3 Hardness scale HRC Hardness = 60 Density r= 7850 kg/m Elongation at break Amin= 26 % Yield point ratio Rp/Rm Rp/Rm > 0.75 Linear expansion factor a= 12 10^-6/K

Temperature T = 50 C

Wheel - materials (strength values) according to Own assignment

*


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Material designation 21MoMnCr12

Material number 1.0037 Material group Casehardening steel Heat treatment / State trial hardened Standard dimension dNm= 40 mm

Standard dimension dNp= 40 mm Ultimate strength for dNm RmN= 1100 N/mm Yield point for dNp RpN= 850 N/mm Tooth root strength !Flim= 450 N/mm Surface durability (pitting) !Hlim= 1530 N/mm Type of Material - Modulus of elasticity E = 210000 N/mm Poisson's ratio n= 0.3 Hardness scale HRC Hardness = 60 Density r= 7850 kg/m

Elongation at break Amin= 26 % Yield point ratio Rp/Rm Rp/Rm > 0.75 Linear expansion factor a= 12 10^-6/K

Temperature T = 50 CSpur gear calculation material Pinion Wheel

Structure factor XW= 1 1 Thermal conductivity l= 50 50 N/(s*K) Heat capacity cM= 485 485 N*m/(kg*K) Root roughness Rz= 3.2 3.2 m Tooth flank roughness Rz= 1.6 1.6 mData width load factor

Tooth modification No Bearing span l = 120 mm Eccentricity (pinion) s : 30 mm Shaft diameter at pinion dsh= 45 mm Factor K' = 0.8 Type of helical toothing Simple Face load factor (root stress) KFb: 1.12

Face load factor (contact stress) KHb: 1.12 Face load factor (scuffing load) KBb: 0Transverse load factors

Transverse load factor (root stress) KFa: 1.2 Transverse load factor (contact stress) KHa: 1.2 Transverse load factor (scuffing load) KBa: 0General input Pinion Wheel

Gearing quality 8 8 Design Disk Disk

Inner diameter of rim di: 0 0 mm

*7


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Tooth modification, base relief Ca: 0 0 m Loading type Pulsating Pulsating Pittings allowed? yes yes

Minimal root safety SFmin= 1.5 Minimal flank safety SHmin= 1.3

Minimal scuffing load safety SBmin= 1Standard gauge spur gear

General data Pinion Wheel Deviation of teeth thickness (DIN 3967) b b Tolerances of teeth thickness (DIN 3967) 25 25 Number of teeth dimension k : 0 0 Spherical dimension- and roll diameter DM: 0 0 mm

Deviation of centre distances (DIN 3964) js9Free input deviations Pinion Wheel

Upper deviation of teeth thickness Asne: 0 0 m Lower deviation of teeth thickness Asni: 0 0 m

Machining allowance q : 0 mm Upper deviation of centre distances Aae: 0 m Lower deviation of centre distances Aai: 0 m

Results:

General data

Effective number of teeth ratio u = 4.000Effective translation ratio i = 4.000Transverse pressure angle at = 20.284 Pressure angle at pitch cylinder awt = 10.827 Ground lead bb = 9.391 Zero centre distance ad = 167.545 mmCentre distance a = 160.004 mmProfile shift coefficient (pinion) x1 = 0.2400Profile shift coefficient (wheel) x2 = -2.2480Sum profile shift coefficient xs = -2.0080

Length of path of contact ga = 14.759 mmLength of recess path ga = 10.942 mmLength of approach path gf = 3.818 mmTransverse contact ratio ea = 1.644Overlap ratio eb = 1.179Total contact ratio e" = 2.823

Number of teeth z = 22 88Virtual number of teeth of helical gear zn = 22.950 91.802

Geometrical dataReference diameter d = 67.018

*9


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268.073 mm

Base diameter db = 62.862 251.449 mm

Pitch diameter dw = 64.002 256.006 mm

Root diameter df = 60.958 247.085 mm

V-circle diameter dv = 68.458 254.585 mm

Tip diameter da = 71.423 257.550 mm

Theoretical tip diameter da th = 74.458 260.585 mmRoot form circle diameter dFf = 63.302 253.696 mm

Root form diameter dNf = 63.015 252.811 mm

Specific sliding at point A #A = -2.175Specific sliding at point E #E = -4.175

Tooth thickness on the tip cylinder san = 3.523 2.869 mm

Tooth depth h = 5.233 5.233 mm

Addendum ha = 2.203 -5.261 mm

Dedendum hf = 3.030 10.494 mm

Bottom clearance c = 0.750 0.750 mm

Tip shortening k = 1.5174 1.5174 mm

Normal base pitch pen = 8.856 mmTransverse base pitch pet = 8.977 mmNormal pitch on base cylinder pbn = 8.856 mmTransverse pitch on base cylinder pbt = 8.977 mm

Note:

The topland shortening for pinion k1amounts more than 15% of the tooth depth!The topland shortening for pinion k2amounts more than 15% of the tooth depth!

Cutter data of gear rack

Cutter data pinion type cutter

Number of teeth z0 = 0 0Profile shift coefficient x0 = 0.000 0.000Topland height factor haP0* = 1.250 1.250Root height factor hfP0* = 1.000 1.000Actual topland play ctat = 1.018 0.949 mmReference diameter d0 = 0.000

0.000 mmBase diameter db0 = 0.000

+:


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0.000 mm

Tip diameter da0 = 7.500 7.500 mm

Deddendum diameter (generation) dfE = 60.560 246.549 mm

Centre distance a0 = 34.004 128.912 mm

Zere centre distance ad0 = 33.509 134.036 mm

Pressure angle at pitch cylinder awt0 = 22.433 -12.769

Results of calculation strength

Forces, moment, speed

Transverse tangential load

at reference cylinder Ft = 6383.471 NTransverse tangential load

at pitch cylinder Ftw = 6684.341 NRadial load at pitch cylinder Frw = 1278.393 NAxial load at pitch cylinder Faw = 1178.630 NTooth load at pitch cylinder Fw = 6906.799 NMoment (pinion) T1 = 213.904 N*mMoment (wheel) T2 = 855.617 N*mLine load = 124.677 N/mmPeripheral speed at reference cylinder v = 4.211 m/sPeripheral speed at pitch cylinder vw = 4.021 m/sRotation speed (pinion) n1 = 1200.000 1/minRotation speed (wheel) n2 = 300.000 1/minNumber of loading cycle (pinion) NL1 = 720000000Number of loading cycle (wheel) NL2 =

180000000

General factors

Hekix slope deviation fHb = 20.000 21.000 m

Transverse pitch deviation fpe = 17.000 18.000 m

Profile form deviation ffa = 17.000 19.000 m

Effective meshing slope deviation fpe eff= 16.688 mEffective profile form deviation ffaeff= 17.650 mFlank line deviation Fbx = 36.586 mManufacturing - flank line deviation fma = 21.000 mFlank line deviation through pinion def. fsh = 11.719 mReduced mass / tooth width mred = 0.014 kg/mmIndividual spring rigidity c' = 13.112 N/(mm*m)Meshing spring rigidity c" = 19.448 N/(mm*m)Resonance velocity (pinion) nE1 = 16124.179 1/minResonance velocity (gear) nE2 = 4031.045 1/minBasic velocity NR = 0.074Dynamic factor Kv = 1.079Face load factor (root stress) KFb = 1.120

Face load factor (contact stress) KHb = 1.120Face load factor (scuffing load) KBb = 1.120

+1


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Transverse load factor (root stress) KFa = 1.200Transverse load factor (contact stress) KHa = 1.200Transverse load factor (scuffing load) KBa = 1.200Helix angle factor KB" = 1.268

Pitting load capacity

Zone factor ZH = 3.424Elasticity factor ZE = 191.646Contact ratio factor Ze = 0.780Helix angle factor Zb = 0.992Lubricant factor (static) ZL = 1.000Lubricant factor (dyn.) ZL = 0.966Velocity factor (static) Zv = 1.000Velocity factor (dyn.) Zv = 0.978Roughness factor (static) ZR = 1.000Roughness factor (dyn.) ZR = 1.031Work hardening factor ZW = 1.000

Life factor for contact stress (static) ZNT = 1.600 1.600Life factor for contact stress (dyn.) ZNT = 1.000 1.000Size factor (static) ZX = 1.000 1.000Size factor (dyn) ZX = 1.000 1.000Single pair tooth contact factor ZB = 1.000 ZD = 1.000Pitting stress limit (static) !HG = 2448.000 2448.000 N/mm

Pitting stress limit (dyn) !HG = 1490.786 1490.786 N/mm

Allowable flank pressure (static) !HP = 1883.077 1883.077 N/mm

Allowable flank pressure (dyn) !HP = 1146.758 1146.758 N/mm

Contact stress !H = 932.561 932.561 N/mm

Safety factor for pitting (static) SH = 2.625 2.625Safety factor for pitting (dyn) SH = 1.599 1.599Attainable lifetime Lh = 34016370.240136065480.961 h

Root load capacity

Overlapping factor (root stress) Ye = 0.608Helix angle factor Yb = 0.917Tooth form factor YF = 0.816 2.224Stress correction factor YS = 2.809 1.256Life factor for tooth root stress (static)YNT = 2.500 2.500Life factor for tooth root stress (dyn) YNT = 1.000 1.000Relativ notch sensitivity factor (static) YdrelT= 1.322 0.692Relativ notch sensitivity factor (dyn) YdrelT= 1.005 0.907Relativ survace factor (static) YRrelT= 1.000 1.000Relativ survace factor (dyn) YRrelT= 1.042 1.042Size factor (static) YX = 1.000 1.000

Size factor (dyn) YX = 1.000 1.000Tooth root stress limit (static) !FG = 2973.416

+*


29/54

1557.871 N/mm

Tooth root stress limit (dyn) !FG = 942.765 850.713 N/mm

Allowable root stress (static) !FP = 1982.278 1038.581 N/mm

Allowable root stress (dyn) !FP = 628.510 567.142 N/mm

Tooth root stress !F = 126.643 154.205 N/mm

Safety factor for tooth breakage (static) SF = 23.479 10.103Safety factor for tooth breakage (dyn) SF = 7.444 5.517Attainable lifetime Lh =213349496.394 9.824e+010 hScuffing load capacity

Angle factor Xab = 0.821Lubricant factor XS = 1.000

Flash temperature calculation way

Load distribution factor X$ = 0.143Flash factor XM = 1.589Structur factor XB = 0.682Tangential line force at weigth wBt = 229.140 N/mmScuffing temperature = 428.581 CCorrosion safety factor SB = 481.997

Integral calculation way

Flash factor XM = 1.589Geometry factor (pinion tip) XBE = 0.682Pitch factor XQ = 1.000

Tip relief factor XCa = 1.000Contact ratio factor Xe = 0.254Mass temperature M = 50.399 CIntegral temperature int = 51.255 CScuffing integral temperature intS = 428.581 CCorrosion safety factor SintS = 8.362Scuffing load safety factor SSL = 301.749

Ultimate strength for pinion Rm = 1022.6 mm(for deff= 62.86 mm)

Ultimate strength for gear Rm = 786.1 mm(for deff= 251.45 mm

)Yielding point for pinion Re = 790.2 mm(for deff= 62.86 mm)

Yielding point for gear Re = 607.5 mm(for deff= 251.45 mm)

Results check gauge

Case centre distance a = 160.004 mmMaximum case centre distance amax = 160.054 mmMinimum case centre distance amin = 159.954 mmTheoretical backlash jt = 0.345 mm

Maximum theoretical backlash jt max= 0.428 mmMinimum theoretical backlash jt min= 0.263 mm

++


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Upper deviation of teeth thickness Asne = -125.000 -170.000 mLower deviation of teeth thickness Asni = -165.000 -220.000 mTolerance of teeth thickness Tsn = 40.000 50.000 m

Fluctuation of teeth thickness Rs = 22.000

28.000 mNominal teeth thickness (theoretical) snth = 5.237 -0.197 mmNominal teeth thickness sn = 5.092 -0.392 mm

Maximum nominal teeth thickness sn max= 5.112 -0.367 mmMinimum nominal teeth thickness sn min= 5.072 -0.417 mmBase tangent length (theoretical) Wkth = 23.599 39.103 mmBase tangent length Wk = 23.463 38.920 mm

Maximum base tangent length Wk max= 23.482 38.943 mmMinimum base tangent length Wk min= 23.444 38.897 mm

Number of teeth dimension k = 3 5Measure roller diameter DM = 5.500 5.500 mm

Radial gauge spheres/roller Mrk = 38.047 129.015 mm

Maximum radial gauge spheres/roller Mrke = 38.068 129.459 mmMinimum radial gauge spheres/roller Mrki = 38.026 128.582 mmDiametral gauge spheres Mdk = 76.095 258.030 mm

Diametral gauge roller MdR = 76.095 258.030 mm

Factor of deviation of base tangent lengthAw = 0.940 0.940Factor of deviation radial spheres/roller Amr = 1.047 5.151Factor of deviation diametral roller Amd = 2.093 10.303Factor of deviation diametral spheres Amd = 2.088 10.301

+0


31/54

+


32/54

+6


33/54

Fig. 6.1Rezultate pachet "67S!89

+


34/54

. CALCULUL FOR ELOR 3IN AN4RENAJE

.1 SCEMA FOR ELOR

Fig. 7.1Schema forelor angrenajului conic *a-a$ seciunea a.ial:n-n$ seciune normal:g-g$seciune tangenial dup generatoare+

.* FOR ELE 3IN AN4RENAJUL CONIC

+7


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Re#a)ii#e de ca#cu# a (or)e#or?

OBS% Pentru an-renae conice cu dantur& drea't&> XmD:.

Pentru an-renae conice orto-ona#e> D:.

.+ FOR ELE 3IN AN4RENAJUL CILIN3RIC

+9


36/54

Fig. 7.1Schema forelor 2 a; )n plan a.ial pentru pinion$ b; )n plan frontal pentru angrenaj: c;)n plan normal pentru angrenaj: d- )n plan a.ial pentru roat:

Re#a)ii#e de ca#cu# a (or)e#or?

FtD 6670>+ NFrD 1*6>1 NFaD 117>66 NFnD 69:6>6 N

7. CALCULUL AR de unde re;u#t& %a#oarea momentu#ui de tor!iune? M t*D *1+9:

Nmmc. For e?

Ft*D 6670>+ N Ft+D *:>9 NFr*D 1*6>1 N Fr+D ++7>99 NFa*D 117>6: N Fa+D 70>07 N

d. 3urata de (unc ionare ? L "D 1:::: oree. 3iametre?

d+D 60 mmdm*D 1>1 mm

f. Lun-imi?L1 D*6 mm

L* D:>9+ mmL+ D+7>66 mm

0:


37/54

Fig. 8.1Schema de )ncrcare a ar(orelui intermediar

CALCULUL 3E VERIFICARE A AR iar u#terior !$au e@tra! date#e nece!are ca#cu#u#ui #a-&re#or.

Universitatea Brasov

Program : MDESIGN User : Customer:

Module version: 13.2 Date : 09.12.2013 Proj. Nr:

Shaft calculation base

Input data:

Shaft calculation in accordance with DIN 743 - standard versionGeometry scheme General shaft geometry

Calculation process Dynamic and static strength proof

Type of loading: tension-pressure Dynamically pure cyclic

01

L1 L*L+


38/54

Type of loading: bending Dynamically pure cyclicType of loading: torsion Dynamically pure cyclicFactor for maximum loading (tension-pressure) 1

Factor for maximum loading (bending) 1 Factor for maximum loading (torsion) 1

Specifications about the materialStrength values according to MDESIGN database (DIN 743) Material designation 18MoCrS4 Material number 1.7323Gage diameter dB =11 mm

For the gage diameter Tensile strength !B%(Rm) =1100 N/mm Yield stress !S%(Re) =775 N/mm Cyclic fatigue strength under bending stress !bW%=550 N/mm

Cyclic tension and pressure fatigue strength !zdW%=440 N/mm Cyclic torsional fatigue strength ttW%=330 N/mmYoung's modulus E =215000 N/mm

Shear modulus G =83000 N/mm Density r=7850 kg/mApply surface hardening to Total shaft

Material group Cemented steelsHeat treatment trial hardenedSurface hardening noShaft geometry

Shaft geometry

Nr

.

Da l

mm

Di l

mm

Da r

mm

Di r

mm

L

mm

Rz

m

r

mm

d:

mm

t:

mm

a!zd:

a!b:

att:

nz

d:

nb

:

nt

:

b!zddBK:

b!bdBK:

btdBK:

dB

K: 45 0 45 0 30 1.6 1

44.

6 0 0 0 0 0 0 0 0 0 0 0

2 56 0 56 0 10 6.3 2 0 0 0 0 0 0 0 0 0 0 0 0

371.4

20

71.4

20 68 3.2 2 0 0 0 0 0 0 0 0 0 0 0 0

4 68 0 68 0 10 6.3 1 0 0 0 0 0 0 0 0 0 0 0 0

5 55 0 55 0 55 3.2 1 0 0 0 0 0 0 0 0 0 0 0 0

6 45 0 45 0 48 1.6 0 0 0 0 0 0 0 0 0 0 0 0 0

0*


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Predetermine the diameter determinant for the heat treatment ? no

Calculation of the deflection for point x =0 mm

Shaft speed n :1200 1/min Consideration of dead weight no

Bearing

Nr. Type =

PositionLocation bearing -> 43

2Location bearing 139.93

Specifications about loadings

Axial forces Fax

Nr. Position x Amount = N Radius = mm

Angle69 -847.478 88.85 90

2 139.93 1178.6 32 270

Radial forces Fr

Nr. Position x =Amount = N

Angle69 -6684.53 0

2 69 -338.991 270

3 139.93 -6684.53 0

4 139.93 1276.71 90

0+


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Torsion

Nr. Position x = mm Torsion momentsPower P: kW

Transition69 213905 0 drive

2 139.93 213905 0 takeoff

Specifications about the load/loadings

Loading case Constant mean stress (loading case 1)Change the limit number of loading cycles ? noMinimum safety against fatigue fracture SDmin =1.2

Minimum safety against residual deformation SFmin =1.2 Minimum safety against incipient crack with hard surface SGmin =1.2

Results:

Calculation process: Dynamic and static strength proof

Total shaft length L = 221.000 mmTotal shaft mass m = 4.617 kgMass moment of inertia of the shaft J = 0.00224 kg*mGeometrical moment of inertia of the shaftI =

366.124 cm4

Position of the centre of gravity

in the X-axis xs = 101.842 mmAngle of torsion & = 0.007

Additional shaft data:

Shaft fillet numberl

mm

Ip

cm4

Wt

cm

m

kg

J

kg*m

I

cm4

Wb

cm

1 30.0 40.258 17.892 0.375 0.0001 20.129 8.946

2 10.0 96.550 34.482 0.193 0.0001 48.275 17.241

3 68.0 255.434 71.530 2.138 0.0014 127.717 35.765

4 10.0 209.911 61.739 0.285 0.0002 104.956 30.869

5 55.0 89.836 32.668 1.026 0.0004 44.918 16.334

6 48.0 40.258 17.892 0.599 0.0002 20.129 8.946

Supporting forces:

No. Type Position

x

mm

Radial force

in the Y-

axis

Radial force

in the Z-

axis

Result.

radial force

R

Axial force

in the X-

axis

00


41/54

Ry

N

Rz

NN

Rax

N

1Location bearing

->43.000 4891.506 917.868 4976.878 652.500

2Location bearing

139.930 8477.554 -2533.569 8848.044 -983.622

Resulting maximum bending moment:

Position x = 69.000 mm Amount Mbmax = 137.186 N*mResulting maximum torsional moment:

Position x = 69.000 mm Amount Mtmax = 213.905 N*mResulting maximum tension-pressure-force:

Position x = 43.000 mm Amount Fzdmax = -652.500 NResulting maximum tension-pressure-stress:

Position x = 43.000 mm Amount !zdmax = -0.163 N/mmResulting maximum bending stress:

Position x = 69.000 mm Amount !bmax = 3.836 N/mmResulting maximum torsional stress:

Position x = 139.930 mm Amount ttmax = 6.548 N/mm

Resulting maximum deflection:

Position x = 221.000 mm Amount ymax = 0.001035 mmAngle of the maximum deflection:

Position x = 0.000 mm Amount ' = 0.000775

Minimum safety against yielding:

Position x = 119.340 mm Amount SF = 53.432Minimum safety against fatigue fracture:

Position x = 118.000 mm Amount SD = 15.762Minimum safety against incipient crack with hard surface:

Position x = 118.000 mm Amount SG = 140.350

Material parameter for deff = 71.420 mm

Material designation 18MoCrS4

Material number 1.7323

Tensile strength !B = 733.595 N/mmYield stress !S = 516.851 N/mmCyclic tension and pressure fatigue

0


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strength !zdW = 293.438 N/mmCyclic fatigue strength under bending

stress !bW = 366.798 N/mmCyclic torsional fatigue strength ttW = 220.079 N/mmTechnological dimension factor

(tensile strength) K1Bdeff= 0.667Technological dimension factor

(yield stress) K1Sdeff= 0.667

Parameter of cross-sections:

Tension-pressure force Fzd and tension/pressure stress !zd

No. Type

Position

x

mm

Result.

Fzdx

N

Amplitude

Fzda

N

Mean

Fzdm

N

Maximum

Fzdmax

N

Amplitude

szdaN/mm

Mean

szdmN/mm

Maximum

szdmaxN/mm

1Fillet with

recess30.0 0.000 0.000 0.000 0.000 0.000 0.000 0.000

2 Shaft fillet 40.0 0.000 0.000 0.000 0.000 0.000 0.000 0.000

3 Shaft fillet 108.0 194.978 194.978 0.000 194.978 0.054 0.000 0.054

4 Shaft fillet 118.0 194.978 194.978 0.000 194.978 0.082 0.000 0.082

5 Shaft fillet 173.0 0.000 0.000 0.000 0.000 0.000 0.000 0.000

6

Calculation

results for

point x

0.0 0.000 0.000 0.000 0.000 0.000 0.000 0.000

Bending moment Mb and bending stress !b

No. TypePosition

x

mm

Result.Mbx

N*m

AmplitudeMba

N*m

MeanMbm

N*m

MaximumMbmax

N*m

Amplitudesba

N/mm

Meansbm

N/mm

MaximumsbmaxN/mm

1Fillet with

recess30.0 0.000 0.000 0.000 0.000 0.000 0.000 0.000

2 Shaft fillet 40.0 0.000 0.000 0.000 0.000 0.000 0.000 0.000

3 Shaft fillet 108.0 57.302 57.302 0.000 57.302 1.856 0.000 1.856

4 Shaft fillet 118.0 40.610 40.610 0.000 40.610 2.486 0.000 2.486

5 Shaft fillet 173.0 0.000 0.000 0.000 0.000 0.000 0.000 0.000

6

Calculation

results forpoint x

0.0 0.000 0.000 0.000 0.000 0.000 0.000 0.000

Torsional moment Mt und Torsional stress tt

No. Type

Position

x

mm

Result.

Mtx

N*m

Amplitude

Mta

N*m

Mean

Mtm

N*m

Maximum

Mtmax

N*m

Amplitude

ttaN/mm

Mean

ttmN/mm

Maximum

ttmaxN/mm

1Fillet with

recess30.0 0.000 0.000 0.000 0.000 0.000 0.000 0.000

2 Shaft fillet 40.0 0.000 0.000 0.000 0.000 0.000 0.000 0.000

3 Shaft fillet 108.0 213.905 213.905 0.000 213.905 3.465 0.000 3.465

06


43/54

4 Shaft fillet 118.0 213.905 213.905 0.000 213.905 6.548 0.000 6.548

5 Shaft fillet 173.0 0.000 0.000 0.000 0.000 0.000 0.000 0.000

6

Calculation

results for

point x

0.0 0.000 0.000 0.000 0.000 0.000 0.000 0.000

Calculation results for point x = 0.000 mm

Trend of curve of the transverse force Qx = 0.000 Ndeflection yx = 0.000582 mmAngle of deflection ' = 0.000775

Strength proof:

K2(d) - Geometrical dimension factor

KF - Influence factor of surface roughness

a!, t- Form factors

No. Type

Position

x

mm

Tension-

pressure

K2(d)

Bending

and

torsion

K2(d)

Tension-

pressure,

bending

KFs

Torsion

KFt

Tension-

pressure

aszd

Bending

asbTorsion

at

1Fillet with

recess30.0 1.00 0.88 0.97 0.99 2.89 2.59 1.80

2Shaft

fillet40.0 1.00 0.87 0.90 0.94 2.49 2.25 1.63

3Shaft

fillet108.0 1.00 0.85 0.90 0.94 2.02 1.84 1.39

4Shaft

fillet118.0 1.00 0.87 0.94 0.96 3.08 2.76 1.88

5Shaft

fillet173.0 1.00 0.88 0.97 0.99 2.85 2.57 1.78

6

Calculation

results for

point x

0.0 1.00 0.88 0.97 0.99 - - -

G%- Relative stress dropn!, t- Bearing factor

No. Type

Position

x

mm

Tension-

pressure

Gzd1/mm

Bending

Gb1/mm

Torsion

Gt1/mm

Tension-

pressure

nszd

Bending

nsbTorsion

nt

1 Fillet with recess 30.0 2.50 2.50 1.15 1.14 1.14 1.09

2 Shaft fillet 40.0 1.27 1.27 0.57 1.10 1.10 1.07

3 Shaft fillet 108.0 1.35 1.35 0.57 1.10 1.10 1.07

4 Shaft fillet 118.0 2.49 2.49 1.15 1.14 1.14 1.09

0


44/54

5 Shaft fillet 173.0 2.51 2.51 1.15 1.14 1.14 1.09

6

Calculation

results for point

x

0.0 - - - - - -

b!zddBK, b!bdBK, btdBK - Stress concentration factor at dBK

b!zd, b!b, bt- Stress concentration factorsKv - Influence factor of surface hardening

No

.Type

Positi

on

x

mm

Tensio

n-

pressu

re

bszddBK

Bendin

g

bsbdBK

Torsio

n

btdBK

Tensio

n-

pressu

re

bszd

Bendin

g

bsb

Torsio

n

bt

Tensio

n-

pressu

re

Kvzd

Bendin

g

Kvb

Torsio

n

Kvt

1

Fillet

with

recess

30.0 - - - 2.54 2.28 1.65 1.00 1.00 1.00

2Shaft

fillet40.0 - - - 2.27 2.05 1.53 1.00 1.00 1.00

3Shaft

fillet108.0 - - - 1.84 1.67 1.30 1.00 1.00 1.00

4Shaft

fillet118.0 - - - 2.70 2.42 1.72 1.00 1.00 1.00

5Shaft

fillet173.0 - - - 2.50 2.25 1.63 1.00 1.00 1.00

6

Calculati

on

results

for point

x

0.0 - - - 1.00 1.00 1.00 1.00 1.00 1.00

K!, Kt- Total influence factor!zdWK, !bWK, ttWK - Cyclic fatigue strength of the notched partK2F - Static bearing effect

No

. Type

Positi

on

xmm

Tensio

n-

pressure

Ks

Bendin

gKs

Torsio

nKt

Tensio

n-

pressu

reszdWKN/mm

Bendin

g

sbWKN/mm

Torsio

ns

ttWKN/mm

Tensio

n-

pressure

K2Fzd

Bendin

gK2Fb

Torsio

nK2Ft

1

Fillet

with

recess

30.0 2.56 2.61 1.88 114.50 140.47 116.75 1.00 1.20 1.20

2Shaft

fillet40.0 2.38 2.48 1.83 123.30 148.15 120.31 1.00 1.20 1.20

3Shaft

fillet108.0 1.95 2.07 1.59 150.84 177.26 138.42 1.00 1.20 1.20

4

Shaft

fillet 118.0 2.77 2.86 2.02 106.01 128.09 108.87 1.00 1.20 1.20

07


45/54

5Shaft

fillet173.0 2.52 2.59 1.86 116.29 141.80 118.01 1.00 1.20 1.20

6

Calculati

on

results

for point

x

0.0 1.03 1.16 1.15 286.00 315.69 191.26 1.00 1.20 1.20

"F - Yield point rise!zdFK, !bFK, ttFK - Yield point of the part

No. Type

Position

x

mm

Tension-

pressure

gFzd

Bending

gFbTorsion

gFt

Tension-

pressure

szdFKN/mm

Bending

sbFKN/mm

Torsion

ttFKN/mm

1 Fillet with recess 30.0 1.10 1.10 1.00 568.54 682.24 358.09

2 Shaft fillet 40.0 1.10 1.10 1.00 568.54 682.24 358.09

3 Shaft fillet 108.0 1.10 1.05 1.00 568.54 651.23 358.09

4 Shaft fillet 118.0 1.15 1.10 1.00 594.38 682.24 358.09

5 Shaft fillet 173.0 1.10 1.10 1.00 568.54 682.24 358.09

6Calculation results

for point x0.0 1.00 1.00 1.00 516.85 620.22 358.09

Static safety

No. Type

Position

x

mm

SF

In

Point1

SF1

in

Point2

SF2

1 Fillet with recess 30.0 10000.00 - -

2 Shaft fillet 40.0 10000.00 - -

3 Shaft fillet 108.0 98.87 - -

4 Shaft fillet 118.0 53.55 - -

5 Shaft fillet 173.0 10000.00 - -

6 Calculation results for point x 0.0 10000.00 - -

y- Influence factor of the mean stress sensitivitz

!mv, tmv - Comparative mean stress

No. Type

Positio

n

x

mm

Tension

-

pressur

e

yzdsK

Bendin

g

ybsK

Torsio

n

ytK

smvN/mm

tmvN/mm

smv1N/mm

tmv1N/mm

smv2N/mm

tmv2N/mm

1

Fillet

with

recess

30.0 - - - 0.00 0.00 - - - -

2Shaft

fillet

40.0 - - - 0.00 0.00 - - - -

09


46/54

3Shaft

fillet108.0 0.11 0.14 0.10 0.00 0.00 - - - -

4Shaft

fillet118.0 0.08 0.10 0.08 0.00 0.00 - - - -

5Shaft

fillet173.0 - - - 0.00 0.00 - - - -

6

Calculatio

n results

for point

x

0.0 - - - 0.00 0.00 - - - -

Alternating fatigue strength of the part (rated fatigue limit)

No

. Type

Positi

on

x

mm

Tensio

n-

pressu

re

szdADKN/mm

Bendin

g

sbADKN/mm

Torsio

n

ttADKN/mm

Tensio

n-

pressu

re

inPoint1

szdADK1

N/mm

Bendin

g

in

Point1

sbADK1N/mm

Torsio

n

in

Point1

ttADK1N/mm

Tensio

n-

pressu

re

inPoint2

szdADK2

N/mm

Bendin

g

in

Point2

sbADK2N/mm

Torsio

n

in

Point2

ttADK2N/mm

1

Fillet

with

recess

30.0 - - - - - - - - -

2Shaft

fillet40.0 - - - - - - - - -

3Shaft

fillet

108.0 150.84 177.26 138.42 - - - - - -

4Shaft

fillet118.0 106.01 128.09 108.87 - - - - - -

5Shaft

fillet173.0 - - - - - - - - -

6

Calculati

on

results

for point

x

0.0 - - - - - - - - -

Dynamic safety

No. Type

Position

x

mm

SD

in

Point1

SD1

in

Point2

SD2


2 Shaft fillet 40.0 10000.00 - -

3 Shaft fillet 108.0 36.67 - -

4 Shaft fillet 118.0 15.76 - -

5 Shaft fillet 173.0 10000.00 - -


:


47/54

Safety against incipient crack

with hard surface

No. Type

Position

x

mm

SG

In

Point1

SG1

in

Point2

SG2


2 Shaft fillet 40.0 10000.00 - -

3 Shaft fillet 108.0 333.52 - -

4 Shaft fillet 118.0 140.35 - -

5 Shaft fillet 173.0 10000.00 - -


Fig. 8.2Rezultate calculul ar(orelui intermediar

9. ALE4EREA I VERIFICAREA MONTAJULUI CURULMEN I AL AR77 N Fa1D 117>6: N

R:0 N Fa*D 70>07 Nc. Va#ori#e diametre#or (u!uri#or de monta> dAD 0 mm.d. 3urata de (unc)ionare? L"D 1:::: ore.e. Ti'u# danturii? drea't&.

f. Condi)ii de (unc)ionare? maina motoare motor a!incron in!ta#a)ia antrenat& uti#ate"no#o-ic indu!tria#> tem'eratura 2$*:7:5oC caracteri!tici#e mediu#ui 'ra( i ume;ea#&.

g. Condi)ii eco#o-ice? uti#i;area de materia#e i te"no#o-ii eco> recic#area materia#e#or> 'rotec)ia%ie)ii.

II* Ale"erea schemei de monta4 i a rulmen ilor*

3in ana#i;a date#or de intrare 'recum i a recomand&ri#or din #iteratura de !'ecia#itate re;u#t&?$ (or)e#e de 8nc&rcare !unt redu!e? (or)a radia#& mare> (or)a a@ia#& mare$ din con!iderente de e(icien)& te"no#o-ic& #e-ate de 're#ucrarea a#e;ae#or 8n carca!& !e

ado't& ru#men i identici$ !e ado't& !i!temu# de #&-&ruire cu dou& #a-&re care 'reiau !arcini#e a@ia#e> (iecare 'e cBte un

!en! 2interior$e@terior5.

1


48/54

Fig. .1Schema de montaj a rulmen ilor ar(orelui intermediar

In(orma)ii de!'re ru#mentu# ado'tat?- ti'u# ru#mentu#ui? ru#ment radia#$a@ia# cu ro#e conice

- !im/o#? +:+:9- dimen!iuni 'rinci'a#e?

3 D 1:: mm d D 0 mm< D * mm T D *>* mma D *1 mm r D 1> mm

- ca'acitatea dinamic&> C? 11*::: N- ca'acitatea !tatic&> C:? 1*::: N- (actorii de ca#cu#? e D :>+

\ D 1>0

III* Schema de calcul

Fig. .23or ele de )ncrcare a lagrelor

51a,61a.781a!sens "a#$1a,(1a.%&FaAD *9:>* N Fa76 N FrAD RAD 096>77N Fr9 N' D +>++ 'entru ru#men ii cu ro#e conice.n*D 1*:: rotminL"D 1:::: ore

D 1067>1** ore> unde

L"e( L"> %eri(icare 8nde'#init& 8nde'&rtat.

*


49/54

1:. ALE4EREA I VERIFICAREA ASAM recic#area materia#e#or> 'rotec)ia (ieii)

II* Ale"erea materialului( tratamentelor termice i tehnolo"ieiSe ado't&> o)e# 'entru con!truc)ii mecanice> E++ 2OL6:5 con(orm SR EN 1::*$* 2STAS::*5?

Ten!iunea admi!i/i#& #a !tri%ire? a!D 1*: MPa

Ten!iunea admi!i/i#& #a (or(ecare? a( D1:: MPa

III* Ale"erea &ormei penei i a dimensiunilor sec iunii transversale

3imen!iuni#e 'enei i a#e cana#e#or din ar/ore i /utuc !e ado't& 8n (unc)ie de %a#oareadiametru#ui tron!onu#ui ar/ore#ui 'e care !e montea;& 'ana> dAD 0mm> din STAS 1::0.

Schia penei 6iametrular(orelui

6imensiunile penei3orma 0:> 0> :> 6> 6+> :>7:> 9:> 1::> 11:> 1*> 10:> 16:mm

IV* Dimensionare i veri&icare*

'alculul de dimensionare din condi ia de rezisten la strivire2 6ate cunoscute2Mt*D *1+9: Nmm momentu# de tor!iune tran!mi!d D dAD 0 mm diametru# ar/ore#uia!D 1*: MPa ten!iunea admi!i/i#& de !tri%ire

+


50/54

" D 9 mm 8n)imea 'eneiL/ D 6: mm $ #un-imea /utucu#ui.

Rela ia de calcul2

D 1>6: mm

#cD1>6: mmL/D 6: mm> !e ado't& o !in-ur& 'an& #STD : mm.

'alculul de verificare la forfecare26ate cunoscute2Mt*D *1+9: Nmm momentu# de tor!iune tran!mi!d D dAD 0 mm diametru# ar/ore#uia(D 1:: MPa ten!iunea admi!i/i#& de !tri%ire

/ D 10 mm #&)imea 'enei#STD : mm #un-imea din !tandard

Rela ia de calcul2

11. ALE4EREA I JUSTIFICAREA SISTEMULUI 3E UN4ERE

I* Adoptarea v9sco)it' ii i tipul lu:ri&iantului*

VB!co;itatea cinematic& a u#eiu#ui !e determin& 8n (unc ie de %ite;a 'eri(eric& aan-renau#ui ci#indric?

LuBnd 8n con!iderare %B!co;itatea u#eiu#ui> !$a ado'tat u#eiu# indu!tria# T() 12* +,.

II* !alculul termic*

Fig. 11.1Schema de calcul termic

3in ecua)ia de ec"i#i/ru termic>

!au

0

a!A

tc "d

M0#

=


51/54


52/54

BIBLIO+RA1IE

1. Ju#a> A. .a. Or-ane de maini> %o#. I>II. Uni%er!itatea din 1976> 1979.*. Mo-an> 4". .a. Or-ane de maini. Teorie$Proiectare$A'#ica ii> Ed Uni%er!it& ii Tran!i#%ania din

*:1* 2(ormat e#ectronic5.+. Mo#do%ean> 4". .a. An-renae ci#indrice i conice. Ca#cu# i con!truc)ie. Ed. Lu@Li/ri!>

*::1.0. Mo#do%ean> 4". .a. An-renae ci#indrice i conice. Metodici de 'roiectare. Ed. Lu@Li/ri!>

*::*.. R&du#e!cu> C. Or-ane de maini> %o#. I> II> III. Uni%er!itatea Tran!i#%ania din 197.6. ^^^ Cu#e-ere de norme i e@tra!e din !tandarde 'entru 'roiectarea e#emente#or com'onente a#e

maini#or> %o#. I. i II. Uni%er!itatea din 1970.

6


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3ESENE


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