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Date initiale:
Puterea motorului electric:
Pm 5.55:= kW
Turatia motorului electric:
nm 2200:= rot/min
Raportul total de transmitere:
itot 5.85:=
Considerăm raportul de transmitere a transmisiei prin curele(preliminar):
itc 1.6:=
Se adoptă: ψa 0.3:=
i12
itot
itc
:=
Raportul real de transmitere:
i12 3.656=
Se adoptă:
i12STAS 3.55:= (conform STAS 822)
u12teoretic i12STAS:=
u12teoretic 3.55=
Materiale: pinion 41MoCr11 HB = 3000 MPa
roată 40Cr10 HB = 2700 MPa
Se adoptă: z1 27:= dinti
z2 z1 u 12teoretic⋅:=
z2 95.85= dinti
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Adoptăm: z2 96:= dinti
Raportul real de transmitere al angrenajului:
u12
z2
z1
:= u12 3.556=
Verificarea abaterii de la raportul de transmitere:
εu12
u12teoretic u12−
u12teoretic
100⋅:=
εu12 0.156−= % este în intervalul -2,5%....2,5%
Recalculăm raportul de transmitere a transmisiei cu curele trapezoidale:
itc
itot
u12
:=
itc 1.645=
Calculul turaţiilor arborilor :
n1
nm
itc
:= n1 1.337 103
×= rot/min
n2
nm
itc u 12⋅
:= n2 376.068= rot/min
P
Calculul puterilor:
Se adoptă: ηc 0.96:= ηtc 0.92:= ηrul 0.99:=
P1 Pm η tc⋅ ηrul⋅:= P1 5.055= kW
P2 Pm η tc⋅ ηc⋅ ηrul2
⋅:= P2 4.804= kW
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Calculul momentelor de torsiune:
T1
3 107
⋅ P1⋅
π n 1⋅:= T1 3.61 10
4×= N*mm
T2
3 107
⋅ P2⋅
π n 2⋅:= T2 1.22 105
×= N*mm
Predimensionarea angrenajului
Parametrii de referinta se calculeaza conform STAS 821.
αn
20 π⋅
180:= αn 0.3490659= radiani unghiul de angrenare in plan normal
has 1:= coeficientul inaltimii capului de referinta in plan normal
cns 0.25:= coeficientul jocului de referinta la capul dintelui, in plannormal
σFlim1 580:= MPaσHlim1 760:= MPa
σFlim2 560:= MPaσHlim2 720:= MPa
Calculul lui z 1 critic
ZE 189.8:=
β 8 π⋅
180:= Zβ cos β( ):= Zβ 0.995=
ZH 2.49 Zβ⋅:= ZH 2.478=
Durata de functionare impusa:
Lh1 8000:= ore Lh2 8000:= ore
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Numărul de roţi cu care vine în contact pinionul, respectiv roata:
χ 1 1:= χ 2 1:=
NL1 60 n1⋅ Lh1⋅ χ 1⋅:= NL1 6.418 108
×= rezultă Z N1 1:= Y N1 1:=
Z N2 1:= Y N2 1:= NL2 60 n2⋅ Lh2⋅ χ 2⋅:= NL2 1.805 10
8×= rezultă
Zw 1:=
Tensiunile admisibile:
σHP1 0.87 σHlim1⋅ Z N1⋅ Zw⋅:=
σHP1
661.2= MPa
σHP2 0.87 σHlim2⋅ Z N2⋅ Zw⋅:=
σHP2 626.4= MPa
σHP σHP1 σHP1 σHP2<if
σHP2 otherwise
:=σHP 626.4= MPa
σ021 800:= MPa σ022 750:= MPa
zn1
z1
cos β( )( )3
:= zn1 27.804= zn2
z2
cos β( )3
:= zn2 98.858=
YSa1 1.59:= YSa2 1.79:= pentru x1 = 0 si x2 = 0
Yδ1 0.997:= Yδ2 1:=
σFP1 0.8 σFlim1⋅ Y N1⋅ Yδ1⋅:= σFP1 462.608= MPa
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σFP2 0.8 σFlim2⋅ Y N2⋅ Yδ2⋅:= σFP2 448= MPa
σFP σFP1 σFP1 σFP2<if
σFP2 otherwise
:=σFP 448= MPa
Fz1cr 1.25 ZE Zβ⋅ ZH⋅( )2⋅
σFP1
σHP2
⋅ u12 1+
u12
⋅ 1
cos β( )⋅:= Fz1cr 417.636=
z1critic este foarte mare, de aici rezulta ca solicitarea principala este de presiune de contact.
K A 1.25:=
Distanta axiala si modulul necesar:
awnec 0.875 u12 1+( )⋅
3
T1 K A⋅ ZE ZH⋅ Zβ⋅( )2⋅
ψa σHP2
⋅ u12⋅
⋅:= awnec 114.361= mm
mnnec
2 awnec⋅ cos β( )⋅
z1 z2+:= mnnec 1.841= mm
Din STAS 822-82 se alege:
mn 2:= mm
amn z1 z2+( )⋅
2 cos β( )⋅:= a 124.209= mm
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Se alege din STAS 655-82
aw 125:= mm
aw a−
mn
0.396=
Latimea rotilor dintate
b ψa aw⋅:=
b 37.5= mm
Unghiul de presiune de referinta in plan frontalȘ
αt atantan αn( )cos β( )
:=
αt 0.352= αtgrade αt
180
π⋅:= αtgrade 20.181= grade
Unghiul de angrenare in pan frontal:
αwt acos a
aw
cos αt( )⋅
:= αwt 0.369= αwtgrade αwt
180
π⋅:= αwtgrade 21.145=
Ecuatiile fundamentale ale angrenajului:
invαwt tan αwt( ) αwt−:=
invαwt 0.01772174=
invαt tan αt( ) αt−:=
invαt 0.01532644=
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Suma coefic ientilor deplasarilor de profil in plan normal:
xsn
invαwt invαt−( ) z1 z2+( )⋅
2 tan αn( )⋅:=
xsn 0.405=
Coeficientii deplasarilor de profil in plan frontal:
xst xsn cos β( )⋅:=
xst 0.401=
xn1
xsn
20.5
xsn
2−
log u12( )
logz1 z2⋅
100 cos β( )( )6
⋅
⋅+:=
xn1 0.316=
xn2 xsn xn1−:=
xn2 0.088=
Coeficienţii deplasărilor de profil trebuie sa fie mai mari sau egali decât valorile minime
xn1min
14 zn1−
17:=
xn1min 0.812−=
xn1 xn1min− 1.128=
xn2min
14 zn2−
17:=
xn2min 4.992−=
xn2 xn2min− 5.08=
xt1 xn1 cos β( )⋅:= xt1 0.313=
xt2 xn2 cos β( )⋅:= xt2 0.088=
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Diametrele cercurilor de divizare:
d1
mn z 1⋅
cos β( ):=
d1 54.531= mm
d2 mn
z2
cos β( )⋅:=
d2 193.887= mm
Diametrele cercurilor de bază:
d b1
d1
cos αt( )
⋅:= d b1
51.183= mm
d b2 d2 cos αt( )⋅:= d b2 181.984= mm
Diametrele cercurilor de rostogolire:
dw1 d1
cos αt( )cos αwt( )
⋅:=
dw1 54.878= mm
dw2 d2
cos αt( )cos αwt( )
⋅:=
dw2 195.122= mm
Se verifică:
dw1 dw2+
2125=
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Diametrele cercurilor de picior:
df1 mn
z1
cos β( )2 has cns+ xn1−( )⋅−
⋅:=
df1 50.8= mm
df2 mn
z2
cos β( )2 has cns+ xn2−( )⋅−
⋅:=
df2 189.241= mm
Diametrele cercurilor de cap:
da1 2 aw⋅ mn
z2
cos β( )2 has⋅− 2 xn2⋅+
⋅−:=
da1 59.759= mm
da2 2 aw⋅ mn
z1
cos β( )2 has⋅− 2 xn1⋅+
⋅−:=
da2 198.204= mm
αat1 acosd1
da1
cos αt( )⋅
:=
αat1grade αat1
180
π⋅:=
αat1 0.542376= radiani
αat1grade 31.076= grade
αat2 acosd2
da2
cos αt( )⋅
:= αat2 0.407374=
αat2grade αat2180
π⋅:= αat2grade 23.341=
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invαat1 tan αat1( ) αat1−:=
invαat1 0.06028808=
invαat2 tan αat2( ) αat2−:=
invαat2 0.02413865=
Coarda constanta normala a dintilor:
sn1 0.5 π⋅ 2 xn1⋅ tan αn( )⋅+( ) mn⋅:=
sn1 3.602= mm
sn2 0.5 π⋅ 2 xn2⋅ tan αn( )⋅+( ) mn⋅:=
sn2 3.27= mm
st1
0.5 π⋅ 2 xt1⋅ tan αt( )⋅+( ) mn⋅
cos β( ):=
st1 3.637= mm
st2
0.5 π⋅ 2 xt2⋅ tan αt( )⋅+( ) mn⋅
cos β( ):=
st2 3.302= mm
βa1 atanda1
d1
tan β( )⋅
:=
βa1 0.152816= radiani
βa1grade βa1
180
π⋅:=
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βa1grade 8.756= grade
βa2 atanda2
d2
tan β( )⋅
:=
βa2 0.142694= radiani
βa2grade βa2
180
π⋅:=
βa2grade 8.176= grade
sat1 invαt invαat1−( ) mn z 1⋅
cos β( )⋅ st1+
cos αt( )cos αat1( )
⋅:=
sat1 1.299= mm
sat2 invαt invαat2−( ) mn z 2⋅
cos β( )⋅ st2+
cos αt( )cos α
at2( )
⋅:=
sat2 1.629= mm
san1 sat1 cos βa1( )⋅:=
san1 1.284= mm
san2 sat2 cos βa2( )⋅:=
san2 1.613= mm
grosimea dintelui pe cercul de cap trebuie sa fie san >= coef * mn , unde coef = 0.25 pentru
danturi imbunatatite si coef = 0.4 pentru danturi cementate.
san2 0.25 mn⋅− 1.113=
san1 0.25 mn⋅− 0.784=
Gradul de acoperire:
εαda1
2d b1
2− da2
2d b2
2−+ 2 aw⋅ sin αwt( )⋅−
2 π⋅ mn⋅ cos αt( )⋅
cos β( )⋅:=
εα 1.611=
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εα 1.3− 0.311=
εβ b sin β( )⋅
π mn⋅:=
εβ 0.831=
εγ εα εβ+:=
εγ 2.442=
β b atand b1
d1
tan β( )⋅
:= β bgrade β b
180
π⋅:= β bgrade 7.515=
β b 0.131156=
βw atandw1
d1
tan β( )⋅
:=
βw
0.140504= radiani
βwgrade βw
180
π⋅:=
βwgrade 8.05= grade
Elementele angrenajului echivalent
zn1
z1
cos β b( )( )2cos β( )⋅
:=
zn1 27.74=
zn2
z2
cos β b( )( )2cos β( )⋅
:=
zn2 98.63=
dn1 mn zn1⋅:=
dn1 55.48= mm
dn2 mn zn2⋅:=
dn2 197.261= mm
d bn1 dn1 cos αn( )⋅:=
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d bn1 52.134= mm
d bn2 dn2 cos αn( )⋅:=
d bn2 185.364= mm
dan1 dn1 da1+ d1−:= dan1 60.708= mm dan2 dn2 da2+ d2−:= dan2 201.578= mm
αwn acoscos αwt( ) cos β b( )⋅
cos βw( )
:=
αwn 0.365738= radiani
αwngrade αwn
180
π⋅:=
αwngrade 20.955= grade
awn
a
cos β b( )( )2
cos αn( )cos αwn( )
⋅:=
awn 127.159= mm
εαn
dan12
d bn12
− dan22
d bn22
−+ 2 awn⋅ sin αwn( )⋅−
2 π⋅ mn⋅ cos αn( )⋅:=
εαn 1.639=
Dimensionarea şi verificarea angrenajului
Viteza periferica a rotilor:
v1
π d 1⋅ n1⋅
60000:= v1 3.818= m/s
Clasa de precizie: 8; danturare prin frezare cu freza melc,
Ra1,2 = 0.8 pentru flanc si Ra1,2 = 1.6 pentru zona de racordare.
Tip lubrifiant: TIN 125 EP STAS 10588-76 avand vascozitatea cinematica 125-140 mm2/s (cSt) [
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Zβ cos β( ):= Zβ 0.995=Yβmin 1 0.25 εβ⋅−( ) εβ 1≤if
0.75 otherwise
:=Yβmin 0.792=
Yβ 1 εβ3 β⋅
2 π⋅⋅−:= Yβ 0.945=
Yβ Yβmin Yβ Yβmin<if
Yβ otherwise
:=Yβ 0.945=
ZH
2 cos β b( )⋅
cos αt( )( )2tan αwt( )⋅
:=ZH 2.412=
YFa1 2.15:=
YFa2 2.08:=
zn1 27.74=
xn1 0.316=
zn2 98.63=
xn2 0.088=
YSa1 1.82:=
YSa2 1.95:=
Yδ1 1:=
Yδ2 1.02:=
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Zε
4 εα−
31 εβ−( )⋅
εβ
εα+ εβ 1<if
1
εαotherwise
:=
Zε 0.806=
Yε 0.25 0.75
εαn
+:=
Yε 0.708=
v1 z 1⋅
1001.031= treapta de precizie 8
K vα 1.06:=
K vβ 1.04:=
K v K vβ εβ K vβ K vα−( )⋅− εβ 1<if
K vβ otherwise
:=
K v 1.057=
ψd
b
d1
:= ψd 0.688=
K Hβ 1.1:=
K Fβ 1.17:=
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f pbr 21:=
Ft
2 T1⋅
d1
:=
Ft 1.324 103
×= N
qα 4 0.1f pbr 4−
Ft
b
+
⋅:=
qα 2.326=
K Hα 1 2 qα 0.5−( )⋅ 1
Zε2
1−
⋅+:=
K Hα 2.963=
K Fα qα εα⋅:=
K Fα 3.747=
ZL 1.05:=
Pentru flancuri
R a1 0.8:= R a2 0.8:=
R z1 4.4 R a10.97
⋅:= R z1 3.544=
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R z2 4.4 R a20.97
⋅:= R z2 3.544=
R z100
R z1 R z2+
2
100
aw
⋅:= R z100 3.17=
ZR 0.98:=
Pentru razele de racordare:
R a1 1.6:= R a2 1.6:=
R z1 4.4 R a10.97
⋅:= R z1 6.941=
R z2 4.4 R a20.97
⋅:= R z2 6.941=
YR1 1.02:= YR2 1.02:= [Anexa 11]
v1 3.818= Zv 0.92:= [Anexa 13]
Zx 1:=
Yx1 1:= Yx2 1:= [Anexa 14]
SHmin 1.15:= SFmin 1.25:=
σHP1
σHlim1 Z N1⋅ ZL⋅ ZR ⋅ Zv⋅ Zw Zx⋅
SHmin
:=
σHP1 625.632= MPa
σHP2
σHlim2 Z N2⋅ ZL⋅ ZR ⋅ Zv⋅ Zw Zx⋅
SHmin
:=
σHP2 592.704= MPa
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σHP σHP1 σHP1 σHP2<if
σHP2 otherwise
:=
σHP 592.704= MPa
σFP1
σFlim1 Y N1⋅ Yδ1⋅ YR1⋅ Yx1⋅
SFmin
:=
σFP1 473.28= MPa
σFP2
σFlim2 Y N2⋅ Yδ2⋅ YR2⋅ Yx2⋅
SFmin
:=
σFP2 466.099= MPa
σFP σFP1 σFP1 σFP2<if
σFP2 otherwise
:=
σFP 466.099= MPa
Recalcularea lăţimii:
ψa
z2
z1
1+
3
aw3
T1 K A⋅ K v⋅ K Hβ⋅ K Hα⋅ ZE ZH⋅ Zε⋅ Zβ⋅( )2⋅
2 σHP2
⋅ z2
z1
⋅
⋅ cos αt( )
cos αwt( )
2
⋅:= ψa 0.412=
b ψa aw⋅:= b 51.467= Adoptam : b2 54:= b1 58:=
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Recalcularea gradului de acoperire axial ş i total:
εβ b2 sin β( )⋅
π mn⋅:=
εβ 1.196=
εγ εα εβ+:=
εγ 2.807=
Verificarea la solicitarea de încovoiere
σF1
T1 z 1⋅ z2
z1
1+
2
⋅ K A K v⋅ K Fβ⋅ K Fα⋅( )⋅ Yε⋅ Yβ⋅ YFa1⋅ YSa1⋅
2 b1⋅ aw2
⋅ cos β( )⋅
cos αt( )cos αwt( )
2
⋅:=
σF1 172.858= MPa
σFP1 473.28= MPa
σF2 σF1
b1
b2⋅
YFa2
YFa1⋅
YSa2
YSa1⋅:=
σF2 192.447= MPa
σFP2 466.099= MPa
Elementele de control
αWt1 acosz1 cos αt( )⋅
z1 2 xn1⋅ cos β( )⋅+
:=
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αWt1 0.409= radiani
αWt1grade αWt1
180
π⋅:=
αWt1grade 23.462= grade
αWt2 acosz2 cos αt( )⋅
z2 2 xn2⋅ cos β( )⋅+
:=
αWt2 0.357=
αWt2grade αWt2
180
π⋅:=
αWt2grade 20.463=
N1prov 0.5z1
π
tan αWt1( )
cos β( )( )2
2 xn1⋅ tan αn( )⋅
z1
− invαt−
⋅+:=
N1prov 4.099=
N1 floor N1prov( ) N1prov floor N1prov( )− 0.5<if
floor N1prov( ) 1+( ) otherwise
:=
N1 4=
N2prov 0.5z2
π
tan αWt2( )
cos β( )( )2
2 xn2⋅ tan αn( )⋅
z2
− invαt−
⋅+:=
N2prov 11.639=
N2 floor N2prov( ) N2prov floor N2prov( )− 0.5<if
floor N2prov( ) 1+( ) otherwise
:=
N2 12=
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W Nn1 2 xn1⋅ mn⋅ sin αn( )⋅ mn cos αn( )⋅ N1 0.5−( ) π⋅ z1 invαt⋅+⋅+:=
W Nn1 21.875= mm
W Nn2 2 xn2⋅ mn⋅ sin αn( )⋅ mn cos αn( )⋅ N2 0.5−( ) π⋅ z2 invαt⋅+⋅+:=
W Nn2 70.785= mm
W Nt1
W Nn1
cos β b( ):=
W Nt1 22.065= mm
W Nt2 W Nn2
cos β b( ):=
W Nt2 71.398= mm
ρWt1 0.5 W Nt1⋅:=
ρWt1 11.032= mm
ρWt2 0.5 W Nt2⋅:=
ρWt2 35.699= mm
ρAt1 aw sin αwt( )⋅ 0.5 d b2⋅ tan αat2( )⋅−:=
ρAt1 5.828= mm
ρEt2 aw sin αwt( )⋅ 0.5 d b1⋅ tan αat1( )⋅−:=
ρEt2 29.669= mm
ρat1 0.5 da1⋅ sin αat1( )⋅:=
ρat1 15.423= mm
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ρat2 0.5 da2⋅ sin αat2( )⋅:=
ρat2 39.264= mm
Pentru măsurarea cotei peste dinţi trebuie să fie îndeplinitecondiţiile:
diferenţele de mai jos trebuie să fie pozitive
cond1 b1 W Nn1 sin β b( )⋅− 5−:=
cond1 50.139=
cond2 b2 W Nn2 sin β b( )⋅− 5−:=
cond2 39.743=
cond3 ρWt1 ρAt1−:=
cond3 5.205=
cond4 ρat1 ρWt1−:=
cond4 4.391=
cond5 ρWt2 ρEt2−:=
cond5 6.03=
cond6 ρat2 ρWt2−:=
cond6 3.565=
Coarda constantă şi înalţimea la coarda constantă:
scn1 mn 0.5 π⋅ cos αn( )( )2⋅ xn1 sin 2 αn⋅( )⋅+⋅:=
scn1 3.181= mm
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scn2 mn 0.5 π⋅ cos αn( )( )2⋅ xn2 sin 2 αn⋅( )⋅+⋅:=
scn2 2.888= mm
sct1 scn1
cos β( )
cos β b( )( )2⋅:=
sct1 3.205= mm
sct2 scn2
cos β( )
cos β b( )( )2⋅:=
sct2 2.909= mm
hcn1 0.5 da1 d1− scn1 tan αn( )⋅−( )⋅:=
hcn1 2.036= mm
hcn2 0.5 da2 d2− scn2 tan αn( )⋅−( )⋅:=
hcn2 1.633= mm
hct1 0.5 da1 d1− sct1 tan αt( )⋅−( )⋅:=
hct1 2.025= mm
hct2 0.5 da2 d2− sct2 tan αt( )⋅−( )⋅:=
hct2 1.624= mm
Stabilirea si verificarea ungerii
Vitezele roţii conduse:
v2
π d 2⋅ n2⋅
60000:= v2 3.818= m/s
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Distantele de la suprafata liberă a uleiului la axa roţilor:
k 3 v2 2≤if
6 otherwise
:=k 6=
Hmin
k 2−
3
da2
2⋅:=
Hmin 132.136= mm
Hmax 0.95df2
2⋅:=
Hmax 89.889= mm
Forma constructiva a rotii conduse
d 45:= mm
δ 3 mn⋅ 6=:= mm
δ1 0.5 52⋅ 26=:= mm
Se adopta:
δ1 18:= mm
dc 1.6 d⋅ 72=:= mm
l 1.1 d⋅:=
l 50:= mm
de df2 2 δ⋅− 177.241=:= mm
de 176:= mm
dg
de dc+( )2
124=:= mm
d0 32:= mm
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Calculul fortelor din angrenaj
NFt2 2
T2
dw2
⋅ 1250.405=:= Ft1 Ft2:=
Fr1
Ft1
tan αwn( )
⋅ 478.865=:= N Fr1
Fr2
:= Fr2
Fa1 Ft1 tan βw( )⋅ 176.852=:= N Fa2 Fa1:=
Fn1
2
Ft12
478.862
+ Fa12
+ 1350.592=:= N Fn2 Fn1:=
Calculul reactiunilor si momentelor incovoietoare
l1 52:= mm S 18:= mm
l2 52:= mm
V2
Ft1
2625.203=:=
H2
487.865 l2⋅ Fa1
dw1
2⋅− S l1⋅−
l2
376.545=:= N
H1
487.865 l2⋅ S l1 2 l2⋅+( )⋅− Fa1
dw1
2⋅+
2 l2⋅ 263.593=:= N
V1
Ft1
2625.203=:= N
FR1 H12
V12
+ 678.498=:= N FR2 H22
V22
+ 729.839=:= N
MiH2 S l1⋅ 936=:= NmmMiH32 H2− l2⋅ 19580.321−=:= Nmm
MiH31 S l1 l2+( )⋅ H1 l 2⋅− 11834.819−=:= NmmMiV3 V1 l 2⋅ 32510.542=:= Nmm
Arbies d2 193.887=
l3 54:= mm
H4
487.865 l3⋅ Fa2
dw2
2⋅−
2 l3⋅ 84.174=:= N V4
Ft2
2625.203=:= N
V3
Ft2
2625.203=:= N
H3
487.865 l3⋅ Fa2
dw2
2⋅−
2 l3⋅ 84.174=:= N
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FR3 H32
V32
+ 630.844=:= N FR4 H42
V42
+ 630.844=:= N
MiH21 H3 l 3⋅ 4545.406=:= N
MiH22 H4 l 3⋅ 4545.406=:= NMiV2 V3 l 3⋅ 33760.948=:= N
Verificarea arborilor
Solicitari compuse
Arbint dint 30:= T1 36100.491=
α 0.277:= alternantpulsatorie
Mi3 MiH312
MiV32
+ 34597.663=:= Wz
π d int3
⋅
32 2650.719=:=
σech3
Mi32
α T1⋅( )2+
Wz
13.586=:= MPa valoarea este <140.. 150 MPa
Arbies dies 42:= mm T2 121990.778=
b pana 10:= t pana 4.5:=
Mi2 MiH222 MiV22+ 34065.56=:=
Wz πdies
3
32⋅
b pana t pana⋅ 45 t pana−( )2⋅
2 45⋅− 6453.447=:= mm 3
σech2
Mi22
1.5 T2⋅( )2+
Wz
28.842=:= MPa <140.. 150 MPa
Verificarea penelor
T1 36100.491= h pana 5:= dc 30:= mm
l pana 50:= mm b pana 6:= mm
lc l pana b pana− 44=:= mm
σs
4 T2⋅
h pana l c⋅ dc⋅ 73.934=:= τf
2 T1⋅
b pana l pana⋅ dc⋅ 8.022=:= MPa
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T2 121990.778= h pana 8:= dc 42:= mm
l pana 65:= mm b pana 10:= mm
lc l pana b pana− 55=:= mm
σs
4 T2⋅
h pana l c⋅ dc⋅ 26.405=:= MPa
τf
2 T2⋅
b pana l pana⋅ dc⋅ 8.937=:= MPa
Verificarea la incalzire
P1 5.055= kW ηc 0.96= λ 1 12:= ψ 0.15:=
t0 20:= gr C S 1:=
tP1 1 ηc−( )⋅ 10
3⋅
λ 1 1 ψ+( )⋅ S⋅ t0+ 34.652=:= gr. C
Proiectarea transmisiei prin curele
itc 1.645=D p1 160:= mm
D p2
D p1
itc
97.246=:= mm
0.7 D p1 D p2+( ) A p≤ 2 D p1 D p2+( )⋅≤ 0.7 D p1 D p2+( ) 180.072=
2 D p1 D p2+( )⋅ 514.492=A p 250:= mm
γ 2 asinD p2 D p1−
2 A p⋅
⋅ 0.252−=:= γg γ
180
π⋅ 14.42−=:=
β1 180 γg− 194.42=:=
Dm
D p1 D p2+
2128.623=:=
L p 2 A p⋅ π Dm⋅+ D p2 D p1−( )2
4 A p⋅+ 908.019=:= mm
L 1000:= cL 0.9:=
p 0.25 L⋅ 0.393 D p1 D p2+( )⋅− 148.902=:=
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q 0.125 D p2 D p1−( )2⋅ 492.259=:=
A p p p2
q−+ 296.142=:= mm
vπ D p1⋅ nm⋅
60 1000⋅ 18.431=:=
m
s
cf 1.2:= cβ 0.96:= P0 2.11:=
z0
cf Pm⋅
cL cβ⋅ P0⋅ 3.653=:= curele
cz 0.95:=
zz0
cz
3.846=:= z 4:=
f 2 v
L⋅ 10
3⋅ 36.861=:= f 80≤ 1=
F 103 Pm
v⋅ 301.128=:=
S 2 F⋅ 602.257=:=
X 0.03 L⋅ 30=:=
Y 0.015 L⋅ 15=:=
Curele trapezoidale de tipSPZ
l p 8.5:= n 2.5:= m 9:= f 8:=
e 12:= r 0.5:=
α 0.277=
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