editionfourthmechanics of materials beer • johnston • dewolf
TRANSCRIPT
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Design of a Transmission Shaft
• If power is transferred to and from the shaft by gears or sprocket wheels, the y g p ,shaft is subjected to transverse loading as well as shear loading.
• Normal stresses due to transverse loads may be large and should be included in d t i ti f i h idetermination of maximum shearing stress.
• Shearing stresses due to transverse loads are usually small and contribution to maximum shear stresscontribution to maximum shear stress may be neglected.
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 1
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Design of a Transmission Shaft• At any section,
MMMI
Mczym +==σ 222where
JTcI
m
zym
=τ
• Maximum shearing stress,
( )22
22 TcMc ⎞
⎜⎛⎞
⎜⎛⎞
⎜⎛σ ( )2max
2 section,-crossannular or circular afor
22
JI
JTc
IMc
mm
=
⎠⎞
⎜⎝⎛+
⎠⎞
⎜⎝⎛=+
⎠⎞
⎜⎝⎛= τστ
22max TM
Jc
+=τ
• Shaft section requirement,
TMJ max22 ⎟⎠⎞⎜
⎝⎛ +
⎞⎜⎛
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 2
allc τmax
min
⎠⎝=⎠⎞
⎜⎝⎛
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Sample Problem 8.3
SOLUTION:
• Determine the gear torques and corresponding tangential forces.
i d i d• Find reactions at A and B.
• Identify critical shaft section from d b di di
Solid shaft rotates at 480 rpm and transmits 30 kW from the motor to
torque and bending moment diagrams.
• Calculate minimum allowable shaft ditransmits 30 kW from the motor to
gears G and H; 20 kW is taken off at gear G and 10 kW at gear H. Knowing that σ = 50 MPa determine the
diameter.
that σall = 50 MPa, determine the smallest permissible diameter for the shaft.
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 3
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Sample Problem 8.3SOLUTION:
• Determine the gear torques and corresponding tangential forces.
( ) mN597Hz82
kW302
⋅===E fPT
ππ ( )
kN73.3m0.16
mN597Hz822
=⋅
==E
EE r
TF
f ππ
( )kW10
kN63.6mN398Hz82
kW20=⋅== CC FT
π
( ) kN49.2mN199Hz82
kW10=⋅== DD FT
π
• Find reactions at A and BFind reactions at A and B.
kN90.2kN80.2
kN22.6kN932.0
==
==
zy
zy
BB
AA
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 4
zy
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Sample Problem 8.3• Identify critical shaft section from torque and
bending moment diagrams.
( )mN1357
5973731160 222max
222
⋅=
++=++ TMM zy
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 5
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Sample Problem 8.3• Calculate minimum allowable shaft diameter.
222 ++ TMMJ
36m101427mN 1357 −×=⋅
=
++=
all
zy TMMcJ
τ
m1014.27MPa50
×==
For a solid circular shaft,
m1014.272
363 ×== −ccJ π
For a solid circular shaft,
mm7.512 == cd
m25.85m02585.0 ==c
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 6
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Stresses Under Combined Loadings
• Wish to determine stresses in slender structural members subjected to jarbitrary loadings.
• Pass section through points of interest. g pDetermine force-couple system at centroid of section required to maintain equilibriumequilibrium.
• System of internal forces consist of three force components and threethree force components and three couple vectors.
D t i t di t ib ti b• Determine stress distribution by applying the superposition principle.
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 7
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Stresses Under Combined Loadings
• Axial force and in-plane couple vectors contribute to normal stress distribution in the section.
• Shear force components and twisting• Shear force components and twisting couple contribute to shearing stress distribution in the section.
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 8
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Stresses Under Combined Loadings
• Normal and shearing stresses are used to determine principal stresses, maximum p p ,shearing stress and orientation of principal planes.
• Analysis is valid only to extent that conditions of applicability of superpositionconditions of applicability of superposition principle and Saint-Venant’s principle are met.
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 9
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Sample Problem 8.5
SOLUTION:
• Determine internal forces in Section EFG.
• Evaluate shearing stress at H
• Evaluate normal stress at H.
• Calculate principal stresses and maximum shearing stress
• Evaluate shearing stress at H.
Three forces are applied to a short steel post as shown. Determine the principle stresses, principal planes and
maximum shearing stress. Determine principal planes.
principle stresses, principal planes and maximum shearing stress at point H.
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 10
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Sample Problem 8.5SOLUTION:
• Determine internal forces in Section EFG.
( )( ) ( )( )m200.0kN75m130.0kN50
kN75kN50kN 30
−=
−==−=
x
zx
M
VPV
( )( ) mkN3m100.0kN300
mkN5.8
⋅===
⋅−=
zy MM
Note: Section properties,
( )( ) 23106514000400 −A ( )( )
( )( ) 463121
23
m1015.9m140.0m040.0
m106.5m140.0m040.0−×==
×==
xI
A
( )( ) 463121 m10747.0m040.0m140.0 −×==zI
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 11
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Sample Problem 8.5• Evaluate normal stress at H.
−++= xzy
bMaMPσ
( )( )m107470
m020.0mkN3m105 6
kN504623- ×
⋅+
×=
++
−
xzy IIA
σ
( )( )m1015.9
m025.0mkN5.8m10747.0m105.6
46×
⋅−
××
−
( ) MPa66.0MPa2.233.8093.8 =−+=
• Evaluate shearing stress at H.g
( )( )[ ]( )
m10585
m0475.0m045.0m040.036
11
×=
==
−
yAQ
( )( )( )( )m040.0m1015.9
m105.85kN75
m105.85
46
36
×
×==
×
−
−
tIQV
x
zyzτ
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 12
( )( )MPa52.17
0 0.005.9
=
x
MECHANICS OF MATERIALS
FourthEdition
Beer • Johnston • DeWolf
Sample Problem 8.5• Calculate principal stresses and maximum
shearing stress. i i i l lDetermine principal planes.
=+== MPa4.3752.170.33 22max Rτ
−=−=−=
=+=+=
MPa4.74.370.33
MPa4.704.370.33
min
max
ROC
ROC
σ
σ
°=
°===
9813
96.2720.33
52.172tan pp
p
CDCY
θ
θθ
98.13pθ
=
MP470
MPa4.37maxτ
°
−=
=
9813
MPa4.7
MPa4.70
min
max
θ
σ
σ
© 2006 The McGraw-Hill Companies, Inc. All rights reserved. 8 - 13
°= 98.13pθ