Mathcad - RCBV1505

7/21/2019 Mathcad - RCBV1505

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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


⋅:=

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( )⋅


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

7/21/2019 Mathcad - RCBV1505


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

7/21/2019 Mathcad - RCBV1505


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=

7/21/2019 Mathcad - RCBV1505


Mathcad - RCBV1505

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