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14–1. A material is subjected to a general state of plane
stress. Express the strain energy density in terms of the
elastic constants E, G, and n and the stress components sx ,
sy , and txy .
sy
txy
sx
‘Strain Energy Due to Normal Stresses: We will consider the application of normal
stresses on the element in two successive stages. For the first stage, we apply only sx
on the element. Since sx is a constant, from Eq. 14-8, we have
s2x V
s2x
dV =
2E
Lv 2E
(Ui)1 =
When sy is applied in the second stage, the normal strain ex will be strained by
ex ¿ = -vey = -
vsy
E
. Therefore, the strain energy for the second stage is
s2y
(Ui)2 =
Lv 2E
=
Lv 2E
¢
Since sx and sy are constants,
B
(Ui)2 =
s2y
+ sx ex ¿ ≤ dV
+ sx a -
vsy
E
b R dV
V
(s2 - 2vsx sy)
2E y
Strain Energy Due to Shear Stresses: The application of txy does not strain the
element in normal direction. Thus, from Eq. 14–11, we have
(Ui)3 =
t2xy
Lv 2G
dV =
t2xy V
2G
The total strain energy is
Ui = (Ui)1 + (Ui)2 + (Ui)3
=
t2xy V
s2x V
V
+
(s2y - 2vsx sy) +
2E
2E
2G
=
t2xy V
V
(s2x + s2y - 2vsx sy) +
2E
2G
and the strain energy density is
t2xy
Ui
1
=
(s2x + s2y - 2vsx sy) +
V
2E
2G
Ans.
1159
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14–2. The strain-energy density must be the same whether
the state of stress is represented by sx , sy , and txy , or
by the principal stresses s1 and s2 . This being the case,
equate the strain–energy expressions for each of these two
cases and show that G = E>[211 + n2].
U =
U =
v
1 2
1
(s2x + s2y) - sxsy +
t R dV
E
2 G xy
Lv 2 E
B
1
v
(s21 + s22) s s R dV
B
E 1 2
Lv 2 E
Equating the above two equations yields.
1
v
1 2
1
v
(s2x + s2y) sxsy +
txy =
(s21 + s22) s s
2E
E
2G
2E
E 1 2
However, s1, 2 =
sx + sy
2
;
A
a
sx - sy
2
(1)
2
2
b + txy
Thus, A s21 + s22 B = s2x + s2y + 2 t2xy
s1 s2 = sxsy - t2xy
Substitute into Eq. (1)
v
1 2
1
v
v 2
1
t =
(s2 + s2y + 2t2xy) ss +
t
A s2 + s2y B - sxsy +
2E x
E
2 G xy
2E x
E x y
E xy
t2xy
v 2
1 2
txy =
+
t
2G
E
E xy
1
v
1
=
+
2G
E
E
1
1
=
(1 + v)
2G
E
G =
E
2(1 + v)
QED
1160
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14–3. Determine the strain energy in the stepped
rod assembly. Portion AB is steel and BC is
brass. Ebr = 101 GPa, Est = 200 GPa, (sY)br = 410 MPa,
(sY)st = 250 MPa.
100 mm
A
B
30 kN
30 kN
1.5 m
Referring to the FBDs of cut segments in Fig. a and b,
+ ©F = 0;
:
x
NBC - 20 = 0
+ ©F = 0;
:
x
NAB - 30 - 30 - 20 = 0
NBC = 20 kN
NAB = 80 kN
p
The cross-sectional area of segments AB and BC are AAB = (0.12) = 2.5(10 - 3)p m2 and
4
p
ABC = (0.0752) = 1.40625(10 - 3)p m2.
4
(Ui)a = ©
NAB 2LAB
NBC 2LBC
N2L
=
+
2AE
2AAB Est
2ABC Ebr
=
C 80(103) D 2 (1.5)
2 C 2.5(10 - 3)p D C 200(109) D
= 3.28 J
+
C 20(103) D 2(0.5)
2 C 1.40625(10 - 3) p D C 101(109) D
Ans.
This result is valid only if s 6 sy.
sAB =
80(103)
NAB
= 10.19(106)Pa = 10.19 MPa 6 (sy)st = 250 MPa
=
AAB
2.5(10 - 3)p
O.K.
sBC =
20 (103)
NBC
= 4.527(106)Pa = 4.527 MPa 6 (sy)br = 410 MPa
=
ABC
1.40625(10 - 3) p
O.K.
1161
0.5 m
75 mm
C 20 kN
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*14–4. Determine the torsional strain energy in the A-36
steel shaft. The shaft has a diameter of 40 mm.
900 N⭈m
200 N⭈m
0.5 m
Referring to the FBDs of the cut segments shown in Fig. a, b and c,
TAB = 300 N # m
300 N⭈m
0.5 m
©Mx = 0;
TAB - 300 = 0
©Mx = 0;
TBC - 200 - 300 = 0
©Mx = 0;
TCD - 200 - 300 + 900 = 0 TCD = -400 N # m
0.5 m
TBC = 500 N # m
The shaft has a constant circular cross-section and its polar moment of inertia is
p
J = (0.024) = 80(10 - 9)p m4.
2
(Ui)t = ©
TAB 2 LAB
TBC 2LBC
TCD LCD
T2L
=
+
+
2GJ
2GJ
2GJ
2GJ
=
1
2 C 75(10 ) 80 (10 - 9)p D
9
c3002 (0.5) + 5002 (0.5) + (-400)2 (0.5) d
= 6.63 J
Ans.
Determine the strain energy in the rod assembly.
Portion AB is steel, BC is brass, and CD is aluminum.
Est = 200 GPa, Ebr = 101 GPa, and Eal = 73.1 GPa.
•14–5.
15 mm
A
20 mm
2 kN B
25 mm
D
5 kN C
2 kN
5 kN
3 kN
300 mm
N2 L
Ui = ©
2AE
=
[3 (103) ]2 (0.3)
2 (p4 )(0.0152)(200)(109)
+
[7 (103) ]2 (0.4)
2(p4 )(0.022)(101)(109)
+
[-3 (103) ]2 (0.2)
2
(p4 )(0.0252)(73.1)(109)
= 0.372 N # m = 0.372 J
Ans.
1162
400 mm
200 mm
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14–6. If P = 60 kN, determine the total strain energy
stored in the truss. Each member has a cross-sectional area
of 2.511032 mm2 and is made of A-36 steel.
2m
B
C
Normal Forces. The normal force developed in each member of the truss can be
determined using the method of joints.
1.5 m
Joint A (Fig. a)
+ ©F = 0;
:
x
FAD = 0
+ c ©Fy = 0;
FAB - 60 = 0
D
FAB = 60 kN (T)
P
Joint B (Fig. b)
+ c ©Fy = 0;
3
FBD a b - 60 = 0
5
FBD = 100 kN (C)
+ ©F = 0;
:
x
4
100 a b - FBC = 0
5
FBC = 80 kN (T)
Axial
Strain
Energy.
LBD = 222 + 1.52 = 2.5 m
(Ui)a = ©
=
A = 2.5 A 103 B mm2 = 2.5 A 10 - 3 B m2
and
N2L
2AE
2 C 2.5 A 10
1
-3
B D C 200 A 109 B D
c C 60 A 103 B D 2 (1.5) + C 100 A 103 B D 2 (2.5)
+ C 80 A 103 B D 2 (2) d
= 43.2 J
Ans.
This result is only valid if s 6 sY. We only need to check member BD since it is
subjected to the greatest normal force
sBD =
A
100 A 103 B
FBD
=
= 40 MPa 6 sY = 250 MPa
A
2.5 A 10 - 3 B
O.K.
1163
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14–7. Determine the maximum force P and the
corresponding maximum total strain energy stored in the
truss without causing any of the members to have
permanent deformation. Each member has the crosssectional area of 2.511032 mm2 and is made of A-36 steel.
2m
B
C
1.5 m
D
Normal Forces. The normal force developed in each member of the truss can be
determined using the method of joints.
Joint A (Fig. a)
+ ©F = 0;
:
x
FAD = 0
+ c ©Fy = 0;
FAB - P = 0
FAB = P (T)
Joint B (Fig. b)
+ c ©Fy = 0;
3
FBD a b - P = 0
5
+ ©F = 0;
:
x
4
1.6667Pa b - FBC = 0
5
FBD = 1.6667P (C)
FBC = 1.3333P(T)
Axial Strain Energy. A = 2.5 A 103 B mm2 = 2.5 A 10 - 3 B m2. Member BD is critical
since it is subjected to the greatest force. Thus,
sY =
FBD
A
250 A 106 B =
1.6667P
2.5 A 10 - 3 B
P = 375 kN
Ans.
Using the result of P
FBD = 625 kN
FAB = 375 kN
FBC = 500 kN
Here, LBD = 21.52 + 22 = 2.5 m.
(Ui)a = ©
=
N2L
=
2AE
1
2 C 2.5 A 10 - 3 B D C 200 A 109 B D
c C 375 A 103 B D 2 (1.5) + C 625 A 103 B D 2 (2.5) + C 500 A 103 B D 2 (2) d
= 1687.5 J = 1.6875 kJ
Ans.
1164
A
P
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*14–8. Determine the torsional strain energy in the A-36
steel shaft. The shaft has a radius of 30 mm.
4 kN⭈m
3 kN⭈m
0.5 m
T2L
1
Ui = ©
=
[02(0.5) + ((3)(103))2(0.5) + ((1)(103))2(0.5)]
2JG
2JG
=
=
0.5 m
0.5 m
2.5(106)
JG
2.5(106)
75(109)(p2 )(0.03)4
= 26.2 N # m = 26.2 J
Ans.
Determine the torsional strain energy in the A-36
steel shaft. The shaft has a radius of 40 mm.
•14–9.
12 kN⭈m
6 kN⭈m
Internal Torsional Moment: As shown on FBD.
Torsional
Strain
Energy:
With
polar
moment
p
J =
A 0.044 B = 1.28 A 10 - 6 B p m4. Applying Eq. 14–22 gives
2
of
inertia
T2L
Ui = a
2GJ
=
1
C 80002 (0.6) + 20002 (0.4) +
2GJ
=
45.0(106) N2 # m3
GJ
=
0.5 m
8 kN⭈m
A -100002 B (0.5) D
45.0(106)
75(10 )[1.28(10 - 6) p]
9
= 149 J
Ans.
1165
0.4 m
0.6 m
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14–10. Determine the torsional strain energy stored in the
tapered rod when it is subjected to the torque T. The rod is
made of material having a modulus of rigidity of G.
L
2r0
Internal Torque. The internal torque in the shaft is constant throughout its length as
shown in the free-body diagram of its cut segment, Fig. a,
Torsional Strain Energy. Referring to the geometry shown in Fig. b,
r = r0 +
T
r0
r0
(x) =
(L + x)
L
L
The polar moment of inertia of the bar in terms of x is
J(x) =
4
pr0 4
p 4
p r0
(L + x)4
r =
c (L + x) d =
2
2 L
2L4
We obtain,
L
(Ui)t =
T2dx
dx =
L0 2GJ
L0
L
=
=
=
L
dx
T2L4
pr0 4G L0 (L + x)4
T2 dx
2G B
pr0 4
2L4
(L + x)4 R
L
T2L4
1
B
R
`
pr0 4G
3(L + x)3 0
7 T2L
24pr0 4 G
Ans.
1166
r0
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14–11. The shaft assembly is fixed at C. The hollow
segment BC has an inner radius of 20 mm and outer radius
of 40 mm, while the solid segment AB has a radius of
20 mm. Determine the torsional strain energy stored in the
shaft. The shaft is made of 2014-T6 aluminum alloy. The
coupling at B is rigid.
600 mm
20 mm
600 mm
C
40 mm
B
60 N⭈m
Internal Torque. Referring to the free-body diagram of segment AB, Fig. a,
©Mx = 0;
TAB = -30 N # m
TAB + 30 = 0
Referring to the free-body diagram of segment BC, Fig. b,
©Mx = 0;
TBC + 30 + 60 = 0
TAB = -90 N # m
p
Torsional Strain Energy. Here, JAB = A 0.024 B = 80 A 10 - 9 B p m4
2
p
JBC = A 0.044 - 0.024 B = 1200 A 10 - 9 B p m4,
2
(Ui)t = ©
=
and
TAB 2LAB
TBC 2LBC
T2L
=
+
2GJ
2GJAB
2GJBC
(-30)2(0.6)
2 C 27 A 109 B D C 80 A 10 - 9 B p D
= 0.06379 J
+
(-90)2(0.6)
2 C 27 A 109 B D C 1200 A 10 - 9 B p D
Ans.
1167
A
20 mm
30 N⭈m
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*14–12. Consider the thin-walled tube of Fig. 5–28. Use
the formula for shear stress, tavg = T>2tAm, Eq. 5–18, and
the general equation of shear strain energy, Eq. 14–11, to
show that the twist of the tube is given by Eq. 5–20,
Hint: Equate the work done by the torque T to the strain
energy in the tube, determined from integrating the strain
energy for a differential element, Fig. 14–4, over the volume
of material.
Ui =
t2 dV
Lv 2 G
but t =
T
2 t Am
Thus,
Ui =
T2
dV
2
2
Lv 8 t AmG
L
=
2
dV
dA
dA
T2
T2
TL
=
dx =
2
2
2
2
2
2
8 A m G Lv t
8 A m G LA t L0
8 A mG LA t
However, dA = t ds. Thus,
Ui =
ds
T2L
2
8 AmG L t
Ue =
1
Tf
2
Ue = Ui
ds
T2L
1
Tf =
2
8 A2mG L t
f =
ds
TL
4 A2mG L t
QED
1168
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Determine the ratio of shearing strain energy to
bending strain energy for the rectangular cantilever beam
when it is subjected to the loading shown. The beam is made
of material having a modulus of elasticity of E and Poisson’s
ratio of n.
•14–13.
P
L
a
a
b
h
Section a – a
Internal Moment. Referring to the free-body diagram of the left beam’s cut
segment, Fig. a,
+ c ©Fy = 0;
-V - P = 0
V = -P
+ ©MO = 0;
M + Px = 0
M = -Px
Shearing Strain Energy. For the rectangular cross section, the form factor is fs =
6
5
6
2
2
L (-P) dx
L
fsV dx
3P2L
5
3P2
(Ui)v =
dx =
=
=
2GA
2G(bh)
5bhG L0
5bhG
L0
L0
L
However, G =
E
, then
2(1 + v)
(Ui)v =
6(1 + v)P2L
5bhE
Bending Strain Energy.
L
(Ui)b =
M2dx
=
L0 2EI
L0
L
(-Px)2dx2
2Ea
1
bh3 b
12
6P2
6P2 x3 L
2P2L3
2
x
dx
=
=
¢
≤
`
bh3E L0
bh3E 3 0
bh3E
L
=
Then, the ratio is
6(1 + v)P2L
3(1 + v) h 2
(Ui)v
5bhE
=
a b
=
2
3
(Ui)b
5
L
2P L
bh3E
Ans.
From this result, we can conclude that the proportion of the shearing strain energy
stored in the beam increases if the depth h of the beam’s cross section increases but
(Ui)v
1
= 0.009. the
decreases if L increases. Suppose that v = and L = 10h, then
2
(Ui)b
shearing strain energy is only 0.09% of the bending strain energy. Therefore, the
effect of the shearing strain energy is usually neglected if L 7 10h.
1169
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14–14. Determine the bending strain-energy in the beam
due to the loading shown. EI is constant.
M0
A
L0
Ui =
L
C
B
2
M dx
2EI
=
1
c
2EI L0
=
M20L
24EI
L>2
L
—
2
a
L
—
2
L>2
2
2
-M0
M0
a
x1 b dx1 +
x2 b dx2]
L
L
L0
Ans.
Note: Strain energy is always positive regardless of the sign of the moment function.
14–15. Determine the bending strain energy in the beam.
EI is constant.
P
P
Referring to the FBD of the entire beam, Fig. a,
a + ©MB = 0;
Pa
L
3L
b + Pa
b - Ay (L) = 0
4
4
L
4
Ay = P
Using the coordinates, x1 and x2, the FBDs of the beam’s cut segments in Figs. b and
c are drawn. For coordinate x1,
a + ©Mc = 0;
M(x1) - Px1 = 0
M(x1) = Px1
For coordinate x2 coordinate,
a + ©Mc = 0;
M(x2) - Pa
L
b = 0
4
L
(Ui)b = ©
1
M2dx
=
c2
2EI
2EI
L0
L0
M(x2) =
L>4
(Px1)2dx1 +
L
4
PL
4
L0
L>2
a
PL 2
b dx2 d
4
L
=
1
P2 3
P2L2 2
c2 a
x1 b ` +
x ` d
2EI
3
16 2 0
0
=
P2L3
48EI
Ans.
1170
L
2
L
4
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*14–16. Determine the bending strain energy in the A-36
structural steel W10 * 12 beam. Obtain the answer using
the coordinates 1a2 x1 and x4, and 1b2 x2 and x3.
6 kip
x1
x4
x2
12 ft
Support Reactions: As shown on FBD(a).
Internal Moment Function: As shown on FBD(b), (c), (d) and (e).
Bending Strain Energy:
Using coordinates x1 and x4 and applying Eq. 14–17 gives
L
Ui =
M2dx
L0 2EI
1
c
2EI L0
12ft
=
1
c
2EI L0
12ft
=
=
L0
(-3.00x1)2 dx1 +
9.00x21dx1 +
3888 kip2 # ft3
EI
L0
6ft
(-6.00x4)2 dx4 d
6ft
36.0x24 dx4 d
For W10 * 12 wide flange section, I = 53.8 in4.
Ui =
3888(123)
29.0(103)(53.8)
= 4.306 in # kip = 359 ft # lb
Ans.
b) Using coordinates x2 and x3 and applying Eq. 14–17 gives
L
Ui =
M2dx
L0 2EI
1
c
2EI L0
12ft
=
1
c
2EI L0
12ft
=
=
(3.00x2 - 36.0)2dx2 +
L0
6ft
(6.00x3 - 36.0)2 dx3 d
A 9.00x22 - 216x + 1296 B dx2 +
3888 kip2 # ft3
EI
L0
6ft
A 36.0x23 - 432x + 1296 B dx3 d
For W 10 * 12 wide flange section, I = 53.8 in4.
Ui =
3888(123)
29.0(103)(53.8)
= 4.306 in # kip = 359 ft # lb
Ans.
1171
x3
6 ft
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Determine the bending strain energy in the A-36
steel beam. I = 99.2 (106) mm4.
•14–17.
9 kN/m
6m
Referring to the FBD of the entire beam, Fig. a,
1
(9)(6)(2) - Ay (6) = 0
2
a + ©MB = 0;
Ay = 9 kN
Referring to the FBD of the beam’s left cut segment, Fig. b,
a + ©M0 = 0;
M(x) +
1 3
a xb (x) (x>3) - 9x = 0
2 2
M(x) = a 9x 1
M2 dx
=
2EI L0
L0 2EI
6m
a 9x -
1
2EI L0
6m
a 81x2 +
L
(Ui)b =
=
=
=
For
A
36
1 3
x b
4
steel,
1 3 2
x b dx
4
1 6
9
x - x4 bdx
16
2
1 7
9 5 2 6m
1
d
c a27x3 +
x x b
2EI
112
10
0
666.51 kN2 # m3
EI
E = 200 GPa.
Here,
= 99.2(10 - 6) m4. Then
(Ui)b =
kN # m
666.51 (10002)
200(109) C 99.2(10 - 6) D
I = C 99.2 (106) mm4 D a
= 33.6 J
4
1m
b
1000 mm
Ans.
1172
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14–18. Determine the bending strain energy in the A-36
steel beam due to the distributed load. I = 122 (106) mm4.
15 kN/m
A
B
3m
Referring to the FBD of the entire beam, Fig. a,
+ c ©Fy = 0;
1
(15)(3) = 0
2
Ay -
a + ©MA = 0;
MA -
Ay = 22.5 kN
1
(15)(3)(2) = 0
2
MA = 45
kN # m
Referring to the FBD of the beam’s left cut segment, Fig. b,
a + ©M0 = 0;
M(x) +
1
(5x)(x)(x>3) - 22.5x + 45 = 0
2
M(x) = (22.5x - 0.8333x3 - 45) kN # m
L
(Ui)b =
=
M2dx
1
=
c
2EI
2EI
L0
L0
1
c
2EI L0
3m
(22.5x - 0.8333x3 - 45)2 dx
3m
0.6944x6 - 37.5x4 + 75x3 + 506.25x2
- 2025x + 2025)dx d
=
1
a0.09921x7 - 7.5x5 + 18.75x4 + 168.75x3
2EI
- 1012.5x2 + 2025xb 2
715.98 kN2 # m2
=
EI
For
A
36
steel,
E = 200 GPa.
Here,
3m
0
I = c122(106) mm4 d a
= 122(10 - 6) m4. Thus,
(Ui)b =
715.98 (10002)
200(109) C 122 (10 - 6) D
= 29.3 J
4
1m
b
1000 mm
Ans.
1173
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14–19. Determine the strain energy in the horizontal
curved bar due to torsion. There is a vertical force P acting
at its end. JG is constant.
r
90⬚
P
T = Pr(1 - cos u)
Strain energy:
L
Ui =
T2 ds
L0 2JG
However,
s = ru;
ds = rdu
u
Ui =
T2rdu
r
=
2JG L0
L0 2JG
P2r3
2JG L0
p>2
=
P2r3
2JG L0
p>2
=
P2r3
2JG L0
p>2
=
=
P2r3 3p
a
- 1b
JG
8
p>2
[Pr(1 - cos u)]2du
(1 - cos u)2 du
(1 + cos2 u - 2 cos u)du
(1 +
cos 2u + 1
- 2 cos u) du
2
Ans.
1174
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*14–20. Determine the bending strain energy in the beam
and the axial strain energy in each of the two rods. The
beam is made of 2014-T6 aluminum and has a square cross
section 50 mm by 50 mm. The rods are made of A-36 steel
and have a circular cross section with a 20-mm diameter.
2m
8 kN
Support Reactions: As shown on FBD(a).
8 kN
Internal Moment Function: As shown on FBD(b) and (c).
Axial Strain Energy: Applying Eq. 14–16 gives
1m
N2L
(Ui)a =
2AE
C 8.00(103) D 2 (2)
=
2AE
64.0(106) N2 # m
AE
=
64.0(106)
=
p
4
(0.022) [200(109)]
= 1.02 J
Ans.
Bending Strain Energy: Applying Eq. 14–17 gives
L
(Ui) b =
=
=
=
M2dx
L0 2EI
1
B2
2EI
L0
1m
(8.00x1)2 dx 1 +
85.333 kN2 # m3
EI
L0
2m
8.002 dx2 R
85.333(106)
1
(0.05) (0.053) D
73.1(109) C 12
= 2241.3 N # m = 2.24 kJ
Ans.
1175
2m
1m
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The pipe lies in the horizontal plane. If it is
subjected to a vertical force P at its end, determine the
strain energy due to bending and torsion. Express the
results in terms of the cross-sectional properties I and J, and
the material properties E and G.
•14–21.
z
L
C
x
B
L
—
2
A
P
Ui =
M2 dx
T2 dx
+
L 2E I
L 2JG
L
2
=
L
L PL 2
( 2 ) dx
(P x)2 dx
(P x)2 dx
+
+
2
E
I
2
EI
L0
L0 2 J G
L0
=
L 31
P2 L3
P2L2
P2
a b
+
+
(L)
2EI 2 3
2EI 3
8JG
=
P2 L3
3 P2 L3
+
16 E I
8JG
= P2 L3 c
1
3
+
d
16 E I
8JG
Ans.
1176
y
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14–22. The beam shown is tapered along its width. If a
force P is applied to its end, determine the strain energy in
the beam and compare this result with that of a beam that
has a constant rectangular cross section of width b and
height h.
b
h
P
L
Moment of Inertia: For the beam with the uniform section,
I =
bh3
= I0
12
For the beam with the tapered section,
I =
I0
bh3
1 b
a xb A h3 B =
x =
x
12 L
12L
L
Internal Moment Function: As shown on FBD.
Bending Strain Energy: For the beam with the tapered section, applying Eq. 14–17 gives
L
UI =
M2 dx
L0 2EI
=
L
(-Px)2
1
dx
I0
2E L0
L x
=
P2L
xdx
2EI0 L0
=
3P2 L3
P2L3
=
4EI0
bh3 E
L
Ans.
For the beam with the uniform section,
L
Ui =
M2dx
L0 2EI
L
=
1
(-Px)2 dx
2EI0 L0
=
P3 L3
6EI0
The strain energy in the capered beam is 1.5 times as great as that in the beam
having a uniform cross section.
Ans.
1177
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14–23. Determine the bending strain energy in the
cantilevered beam due to a uniform load w. Solve the
problem two ways. (a) Apply Eq. 14–17. (b) The load w dx
acting on a segment dx of the beam is displaced a distance y,
where y = w1-x4 + 4L3x - 3L42>124EI2, the equation of
the elastic curve. Hence the internal strain energy in the
differential segment dx of the beam is equal to the external
work, i.e., dUi = 121w dx21-y2. Integrate this equation to
obtain the total strain energy in the beam. EI is constant.
w dx
w
dx
Internal Moment Function: As shown on FBD.
Bending Strain Energy: a) Applying Eq. 14–17 gives
L
Ui =
M2dx
L0 2EI
L
=
w 2
1
c - x2 d dx R
B
2EI L0
2
L
=
=
b) Integrating dUi =
dUi =
dUi =
Ui =
=
w2
x4 dx R
B
8EI L0
w2 L5
40EI
Ans.
1
(wdx)( -y)
2
w
1
(wdx) B A -x4 + 4L3x - 3L4 B R
2
24EI
w2
A x4 -4L3x + 3L4 B dx
48EI
w2
48EI L0
L
x
L
A x4 - 4L3x + 3L4 B dx
w2L5
40EI
Ans.
1178
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*14–24. Determine the bending strain energy in the
simply supported beam due to a uniform load w. Solve the
problem two ways. (a) Apply Eq. 14–17. (b) The load w dx
acting on the segment dx of the beam is displaced a distance
y, where y = w1-x4 + 2Lx3 - L3x2>124EI2, the equation
of the elastic curve. Hence the internal strain energy in the
differential segment dx of the beam is equal to the external
work, i.e., dUi = 211w dx21-y2. Integrate this equation to
obtain the total strain energy in the beam. EI is constant.
w dx
w
x
Support Reactions: As shown on FBD(a).
Internal Moment Function: As shown on FBD(b).
Bending Strain Energy: a) Applying Eq. 14–17 gives
L
Ui =
M2dx
L0 2EI
L
=
2
w
1
2
c (Lx - x ) d dx R
B
2EI L0 2
L
=
=
b) Integrating dUi =
dUi =
dUi =
w2
(L2x2 + x4 - 2Lx3) dx R
B
8EI L0
w2L5
240EI
Ans.
1
(wdx) (-y)
2
1
w
(wdx) B (-x4 + 2Lx3 - L3x) R
2
24EI
w2
(x4 - 2Lx3 + L3x) dx
48EI
L
Ui =
=
w2
(x4 - 2Lx3 + L3x) dx
48EI L0
w2L5
240EI
Ans.
1179
dx
L
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Determine the horizontal displacement of joint A.
Each bar is made of A-36 steel and has a cross-sectional
area of 1.5 in2.
•14–25.
2 kip
A
3 ft
D
3 ft
C
B
4 ft
Member Forces: Applying the method of joints to joint at A, we have
+ ©F = 0;
:
x
4
F
- 2 = 0
5 AD
+ c ©Fy = 0;
FAB -
FAD = 2.50 kip (T)
3
(2.50) = 0
5
FAB = 1.50 kip (C)
At joint D
+ ©F = 0;
:
x
4
4
F
- (2.50) = 0
5 DB
5
+ c ©Fy = 0;
3
3
( 2.50) + (2.50) - FDC = 0
5
5
FDB = 2.50 kip (C)
FDC = 3.00 kip (T)
Axial Strain Energy: Applying Eq. 14–16, we have
N2L
Ui = a
2AE
=
1
[2.502 (5) + (-1.50)2 (6) + (-2.50)2 (5) + 3.002(3)]
2AE
=
51.5 kip2 # ft
AE
=
51.5(12)
1.5[29.0(103)]
= 0.014207 in # kip
External Work: The external work done by 2 kip force is
Ue =
1
(2) (¢ A)h = (¢ A)h
2
Conservation of Energy:
Ue = Ui
(¢ A)h = 0.014207
= 0.0142 in.
Ans.
1180
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14–26. Determine the horizontal displacement of joint C.
AE is constant.
C
P
L
L
A
B
L
Member Forces: Applying the method of joints to C, we have
+ c ©Fy = 0;
FBC cos 30° - FAC cos 30° = 0
+ ©F = 0;
:
x
P - 2F sin 30° = 0
Hence,
FBC = P (C)
FBC = FAC = F
F = P
FAC = P (T)
Axial Strain Energy: Applying Eq. 14–16, we have
N2L
Ui = a
2AE
=
1
C P2L + (-P)2 L D
2AE
=
P2L
AE
External Work: The external work done by force P is
Ui =
1
P(¢ c)k
2
Conservation of Energy:
Ue = Ui
P2L
1
P(¢ C)k =
2
AE
(¢ C)k =
2PL
AE
Ans.
1181
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14–27. Determine the vertical displacement of joint C. AE
is constant.
A
L
L
C
L
B
Joint C:
+ ©F = 0
:
x
FCB cos 30° - FCA cos 30° = 0
FCB = FCA
+ c © Fy = 0
FCA sin 30° + FCB sin 30° - P = 0
FCB = FCA = P
Conservation of energy:
Ue = Ui
N2L
1
P¢ C = ©
2
2EA
1
L
2
P¢ C =
[F 2 + FCA
]
2
2EA CB
P¢ C =
¢C =
L
(P2 + P2)
EA
2PL
AE
Ans.
1182
P
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*14–28. Determine the horizontal displacement of joint D.
AE is constant.
D
C
P
Joint B:
L
+ c ©Fy = 0;
FBC = 0.75P
+ ©F = 0;
;
x
FBA = P
0.6 L
B
A
Joint D:
0.8 L
+ T ©Fy = 0;
FDA = 0
+ ©Fx = 0;
:
FDC = P
Joint A:
+ T ©Fy = 0;
3
F
- 0.75P = 0
5 AC
FAC = 1.25P
Conservation of energy:
Ue = Ui
N2L
1
P¢ D = ©
2
2AE
1
1
P¢ D =
[(0.75P)2(0.6L) + (P)2(0.8L) + (02)(0.6L)
2
2AE
+ (P2)(0.8L) + (1.25P)2(L)]
¢D =
3.50PL
AE
Ans.
The cantilevered beam is subjected to a couple
moment M0 applied at its end. Determine the slope of the
beam at B. EI is constant.
•14–29.
M0
A
B
Ui =
L
2
M20L
1
M dx
M20 dx =
=
2EI L0
2EI
L0 2EI
Ue =
1
(M0 uB)
2
L
L
Conservation of energy:
Ue = Ui
M0 2L
1
M0 uB =
2
2EI
uB =
M0L
EI
Ans.
1183
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14–30. Determine the vertical displacement of point C of
the simply supported 6061-T6 aluminum beam. Consider
both shearing and bending strain energy.
100 kip
a
B
A
C
1.5 ft
Support Reactions. Referring to the free-body diagram of the entire beam, Fig. a,
a + ©MB = 0;
100(1.5) - Ay(3) = 0
Ay = 50 kip
+ c ©Fy = 0;
50 - V = 0
a + ©MO = 0;
V = 50 kip
M - 50x = 0
M = 50x
Shearing Strain Energy. For the rectangular beam, the form factor is fs =
6
5
6
A 502 B dx
18 in.
fsV2dx
5
(Ul)v =
= 2
= 0.3041 in # kip
L0 2GA
L0
2 C 3.7 A 103 B D [4(12)]
L
Bending Strain Energy. I =
1
(4) A 123 B = 576 in4. We obtain
12
L
(50x)2 dx
M2dx
= 2
L0 2 C 10.0 A 103 B D (576)
L0 2EI
L
(Ui)b =
= 0.4340 A 10-3 B
L0
= 0.4340 A 10-3 B ¢
18 in.
x2 dx
x3 18in.
≤`
3 0
= 0.84375 in # kip
Thus, the total strain energy stored in the beam is
Ui = (Ui)v + (Ui)b
= 0.3041 + 0.84375
= 1.1478 in # kip
Ans.
External Work. The external work done by the external force (100 kip) is
Ue =
1
1
P¢ = (100)¢ C = 50¢ C
2
2
Conservation of Energy.
Ue = Ui
50¢ C = 1.1478
¢ C = 0.02296 in. = 0.0230 in.
Ans.
1184
1.5 ft
4 in.
12 in.
Internal Loading. Referring to the free-body diagram of the beam’s left cut
segment, Fig. b,
a
Section a – a
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14–31. Determine the slope at the end B of the A-36 steel
beam. I = 8011062 mm4.
6 kN⭈m
A
B
M = -750x
8m
L
2
1
M dx
M uB =
2
L0 2EI
B
( -750x)2dx
1
(6(103)) uB =
2
2EI
L0
uB =
16000
200 (109)(80)(10-6)
= 1 (10-3) rad
Ans.
*14–32. Determine the deflection of the beam at its center
caused by shear. The shear modulus is G.
P
b
Support Reactions: As shown on FBD(a).
h
Shear Functions: As shown on FBD(b).
Shear Strain Energy: Applying 14–19 with fe =
L
2
6
for a rectangular section, we have
5
L
Ui =
feV2dx
L0 2GA
L
2
6 P 2
1
a b a b dx R
=
B2
2bhG
2
L0 5
=
3P2L
20bhG
External Work: The external work done by force P is
Ue =
1
(P) ¢
2
Conservation of Energy:
Ue = Ui
3P2L
1
(P)¢ =
2
20bhG
¢ =
3PL
10bhG
Ans.
1185
L
2
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•14–33. The A-36 steel bars are pin connected at B and C.
If they each have a diameter of 30 mm, determine the slope
at E.
3
2
C
D
A
E
2m
3m
L
300 N⭈m
B
2m
3m
2
Ui =
M dx
1
1
65625
= (2)
(75x1)2dx1 + (2)
(-75x2)2dx2 =
2EI
2EI
2EI
EI
L0
L0
L0
Ue =
1
1
(M¿)u = (300) uE = 150 uE
2
2
Conservation of energy:
Ue = Ui
150 uE =
uE =
65625
EI
473.5
473.5
= 0.0550 rad = 3.15°
=
EI
(200)(109)(p4 )(0.0154)
14–34. The A-36 steel bars are pin connected at B. If
each has a square cross section, determine the vertical
displacement at B.
Ans.
800 lb
2 in.
A
B
C
D
2 in.
Support Reactions: As shown on FBD(a).
8 ft
Moment Functions: As shown on FBD(b) and (c).
Bending Strain Energy: Applying 14–17, we have
L
Ui =
=
=
=
M2dx
L0 2EI
1
B
2EI L0
4ft
( -800x1)2 dx1 +
23.8933(106) lb2 # ft3
EI
23.8933(106)(123)
1
(2)(23) D
29.0(106) C 12
L0
10ft
(-320x2)2 dx2 R
= 1067.78 in # lb
External Work: The external work done by 800 lb force is
Ue =
1
(800)(¢ B) = 400¢ B
2
Conservation of Energy:
Ue = Ui
400¢ B = 1067.78
¢ B = 2.67 in.
Ans.
1186
4 ft
10 ft
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14–35. Determine the displacement of point B on the
A-36 steel beam. I = 8011062 mm4.
20 kN
A
C
B
3m
3
L
5m
5
1
M2dx
=
[(12.5)(103)(x1)]2dx1 +
[(7.5)(103)(x2)]2 dx2 R
Ui =
B
2EI L0
L0
L0 2EI
=
Ue =
1.875(109)
EI
1
1
P¢ = (20)(103)¢ B = 10(103)¢ B
2
2
Conservation of energy:
Ue = Ui
10(103)¢ B =
¢B =
1.875(109)
EI
187500
187500
= 0.0117 m = 11.7 mm
=
EI
200(109)(80)(10 - 6)
Ans.
*14–36. The rod has a circular cross section with a
moment of inertia I. If a vertical force P is applied at A,
determine the vertical displacement at this point. Only
consider the strain energy due to bending. The modulus of
elasticity is E.
r
A
Moment function:
P
a + ©MB = 0;
P[r(1 - cos u)] - M = 0;
M = P r (1 - cos u)
Bending strain energy:
s
Ui =
M2 ds
L0 2 E I
ds = r du
p
u
=
r
M2 r du
=
[P r (1 - cos u) ]2 du
2 E I L0
L0 2 E I
=
P2 r3
(1 + cos2 u - 2 cos u)du
2 E I L0
=
1
cos 2u
P2 r3
a1 + +
- 2 cos u b du
2 E I L0
2
2
=
P2 r3
3
cos 2u
P2 r3 3
3 p P2 r3
a +
- 2 cos ub du =
a pb =
2 E I L0
2
2
2 EI 2
4 EI
p
p
p
Conservation of energy:
Ue = Ui ;
¢A =
1
3 p P2 r3
P ¢A =
2
4 EI
3 p P r3
2 EI
Ans.
1187
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The load P causes the open coils of the spring to
make an angle u with the horizontal when the spring is
stretched. Show that for this position this causes a torque
T = PR cos u and a bending moment M = PR sin u at the
cross section. Use these results to determine the maximum
normal stress in the material.
•14–37.
P
R
d
u
T = P R cos u;
M = P R sin u
Bending:
smax =
Mc
P R sin u d
=
d4
I
)
2 (p4 )(16
tmax =
P R cos u d2
Tc
=
p d4
J
( )
P
2 16
smax =
sx + sy
2
;
C
a
sx - sy
2
2
b + t2xy
=
16 P R cos u 2
16 P R sin u 2
16 P R sin u
;
b
+
a
b
a
C
p d3
pd3
p d3
=
16 P R
[sin u + 1]
p d3
Ans.
14–38. The coiled spring has n coils and is made from a
material having a shear modulus G. Determine the stretch
of the spring when it is subjected to the load P. Assume that
the coils are close to each other so that u L 0° and the
deflection is caused entirely by the torsional stress in the coil.
P
R
u
Bending Strain Energy: Applying 14–22, we have
Ui =
P2R2L
16P2R2L
T2L
=
=
p
2GJ
pd4G
(d4) D
2G C 32
However, L = n(2pR) = 2npR. Then
Ui =
P
32nP2R3
d4G
External Work: The external work done by force P is
Ue =
1
P¢
2
Conservation of Energy:
Ue = Ui
1
32nP2R3
P¢ =
2
d4G
¢ =
64nPR3
d4G
Ans.
1188
d
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14–39. The pipe assembly is fixed at A. Determine
the vertical displacement of end C of the assembly. The
pipe has an inner diameter of 40 mm and outer diameter
of 60 mm and is made of A-36 steel. Neglect the shearing
strain energy.
A
800 mm
600 N
B
400 mm
Internal Loading: Referring to the free-body diagram of the cut segment BC, Fig. a,
©My = 0; My + 600x = 0
My = -600x
Referring to the free-body diagram of the cut segment AB, Fig. b,
©Mx = 0; Mx - 600y = 0
Mx = 600y
©My = 0; 600(0.4) - Ty = 0
Ty = 240 N # m
p
A 0.034 - 0.024 B = 0.325 A 10 - 6 B pm4. We obtain
2
Torsional Strain Energy. J =
L
(Ui)t =
T2dx
=
L0 2GJ
L0
Bending Strain Energy. I =
0.8 m
2 C 75 A 109 B D C 0.325 A 10 - 6 B p D
=
=
=
= 0.3009 J
p
A 0.034 - 0.024 B = 0.1625 A 10 - 6 B pm4. We obtain
4
L
(Ui)b =
2402 dx
1
M2dx
=
B
2EI
2EI
L0
L0
0.4 m
(-600x)2 dx +
L0
0.4 m
0.8 m
1
+ 120 A 103 B y3 2
B 120 A 103 B x3 2
R
2EI
0
0
0.8 m
A 600y)2 dy R
34 560 N2 # m3
EI
34 560
200 A 10 B c0.1625 A 10
9
-6
Bp d
= 0.3385 J
Thus, the strain energy stored in the pipe is
Ui = (Ui)t + (Ui)b
= 0.3009 + 0.3385
= 0.6394 J
External Work. The work done by the external force P = 600 N is
Ue =
1
1
P¢ = (600)¢ C = 300¢ C
2
2
Conservation of Energy.
Ue = Ut
300¢ C = 0.6394
¢ C = 2.1312 A 10 - 3 B = 2.13 mm
Ans.
1189
C
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*14–40. The rod has a circular cross section with a polar
moment of inertia J and moment of inertia I. If a vertical
force P is applied at A, determine the vertical displacement
at this point. Consider the strain energy due to bending and
torsion. The material constants are E and G.
z
y
r
P
T = Pr(1 - cos u);
M = Pr sin u
Torsion strain energy:
x
s
Ui =
u
T2 ds
T2 rdu
=
L0 2GJ
L0 2GJ
p
=
r
[Pr(1 - cos u)]2 du
2GJ L0
=
P2 r3
(1 + cos2 u - 2 cos u)du
2GJ L0
=
cos 2u + 1
P2 r3
a1 +
- 2 cos ubdu
2GJ L0
2
=
3P2r3 p
4GJ
p
p
Bending strain energy:
s
Ui =
M2ds
L0 2EI
u
p
=
M2r du
r
=
[Pr sin u]2 du
2EI
2EI
L0
L0
=
P2 r3
1 - cos 2u
P2 r3 p
a
bdu =
2EI L0
2
4EI
p
Conservation of energy:
Ue = Ui
1
3P2 r3 p
P2 r3 p
P¢ =
+
2
4GJ
4EI
¢ =
1
Pr3 p 3
a
+
b
2
GJ
EI
Ans.
1190
A
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•14–41. Determine the vertical displacement of end B of
the frame. Consider only bending strain energy. The frame
is made using two A-36 steel W460 * 68 wide-flange
sections.
3m
B
Internal Loading. Using the coordinates x1 and x2, the free-body diagrams of the
frame’s segments in Figs. a and b are drawn. For coordinate x1,
-M1 - 20 A 103 B x1 = 0
+ ©MO = 0;
For coordinate x2,
+ ©MO = 0;
M1 = -20 A 103 B x1
M2 - 20 A 103 B (3) = 0
M2 = 60 A 103 B N # m
20 kN
A
Bending Strain Energy.
L
(Ub)i =
M2dx
1
=
B
2EI L0
L0 2EI
400 A 10
1
D£
=
2EI
3
6
=
B
3m
c -20 A 103 B x1 d dx1 +
3m
x1 ≥ 3
3
0
2
+ 3.6 A 109 B x 2
4m
0
L0
4m
c60 A 103 B d dx2 R
2
T
9 A 109 B N2 # m2
EI
For a W460 * 68, I = 297 A 106 B mm4 = 297 A 10 - 6 B m4. Then
(Ub)i =
9 A 109 B
200 A 109 B (297) A 10 - 6 B
= 151.52 J
External Work. The work done by the external force P = 20 kN is
Ue =
4m
1
1
P¢ = c20 A 103 B d ¢ B = 10 A 103 B ¢ B
2
2
Conservation of Energy.
Ue = Ui
10 A 103 B ¢ B = 151.52
¢ B = 0.01515 m = 15.2 mm
Ans.
1191
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14–42. A bar is 4 m long and has a diameter of 30 mm. If it
is to be used to absorb energy in tension from an impact
loading, determine the total amount of elastic energy that it
can absorb if (a) it is made of steel for which
Est = 200 GPa, sY = 800 MPa, and (b) it is made from an
aluminum alloy for which Eal = 70 GPa, sY = 405 MPa.
a) eg =
800(106)
sY
= 4(10 - 3) m>m
=
E
200(109)
ur =
1
1
(s )(e ) = (800)(106)(N>m2)(4)(10 - 3)m>m = 1.6 MJ>m3
2 Y g
2
V =
p
(0.03)2(4) = 0.9(10 - 3)p m2
4
ui = 1.6(106)(0.9)(10 - 3)p = 4.52 kJ
Ans.
b)
eg =
405(106)
sY
= 5.786(10 - 3) m>m
=
E
70(109)
ur =
1
1
(s )(e ) = (405)(106)(N>m2)(5.786)(10 - 3)m>m = 1.172 MJ>m3
2 Y g
2
V =
p
(0.03)2 (4) = 0.9(10 - 3)p m3
4
ui = 1.172(106)(0.9)(10 - 3)p = 3.31 kJ
Ans.
14–43. Determine the diameter of a red brass C83400 bar
that is 8 ft long if it is to be used to absorb 800 ft # lb of
energy in tension from an impact loading. No yielding occurs.
Elastic Strain Energy: The yielding axial force is PY = sgA. Applying Eq. 14–16,
we have
Ui =
(sgA)2L
s2gAL
N2L
=
=
2AE
2AE
2E
Substituting, we have
Ui =
0.8(12) =
s2gAL
2E
11.42 C p4 (d2) D (8)(12)
2[14.6(103)]
d = 5.35 in.
Ans.
1192
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*14–44. A steel cable having a diameter of 0.4 in. wraps
over a drum and is used to lower an elevator having a weight
of 800 lb. The elevator is 150 ft below the drum and is
descending at the constant rate of 2 ft兾s when the drum
suddenly stops. Determine the maximum stress developed in
the cable when this occurs. Est = 2911032 ksi, sY = 50 ksi.
k =
AE
=
L
p
4
(0.42)(29)(103)
150 (12)
150 ft
= 2.0246 kip>in.
Ue = Ui
1
1
mv2 + W ¢ max = k¢ 2max
2
2
1
800
1
c
d[(12) (2)]2 + 800 ¢ max = (2.0246)(103)¢ 2max
2 32.2 (12)
2
596.27 + 800 ¢ max = 1012.29 ¢ 2max
¢ max = 1.2584 in.
Pmax = k¢ max = 2.0246 (1.2584) = 2.5477 kip
smax =
Pmax
2.5477
= 20.3 ksi 6 sg
= p
2
A
4 (0.4)
O.K.
Ans.
The composite aluminum bar is made from two
segments having diameters of 5 mm and 10 mm. Determine
the maximum axial stress developed in the bar if the 5-kg
collar is dropped from a height of h = 100 mm.
Eal = 70 GPa, sY = 410 MPa.
•14–45.
5 mm
200 mm
300 mm
¢ st = ©
WL
=
AE
Pmax = W B 1 +
5(9.81)(0.2)
p
4
(0.0052)(70)(109)
C
1 + 2a
= 5(9.81) B 1 +
smax =
Pmax
=
A
p
4
C
h
bR
¢ st
1 + 2a
+
5(9.81)(0.3)
p
4
(0.012)(70)(109)
0.1
9.8139(10 - 6)
7051
= 359 MPa 6 sy
(0.0052)
h
= 9.8139(10 - 4) m
10 mm
b R = 7051 N
O.K.
1193
Ans.
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14–46. The composite aluminum bar is made from two
segments having diameters of 5 mm and 10 mm. Determine
the maximum height h from which the 5-kg collar should
be dropped so that it produces a maximum axial stress in the
bar of s max = 300 MPa, Eal = 70 GPa, sY = 410 MPa.
5 mm
200 mm
300 mm
h
10 mm
¢ st = ©
WL
=
AE
Pmax = W B 1 +
5(9.81)(0.2)
p
2
9
4 (0.005 )(70)(10 )
C
1 + 2a
+
5(9.81)(0.3)
p
4
(0.012)(70)(109)
= 9.8139(10 - 6) m
h
bR
¢ st
p
h
bR
300(106)a b (0.0052) = 5(9.81) B 1 +
1 + 2a
4
C
9.8139(10 - 6)
120.1 = 1 + 21 + 203791.6 h
h = 0.0696 m = 69.6 mm
Ans.
1194
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14–47. The 5-kg block is traveling with the speed of
v = 4 m>s just before it strikes the 6061-T6 aluminum
stepped cylinder. Determine the maximum normal stress
developed in the cylinder.
C
B
40 mm
Equilibrium. The equivalent spring constant for segments AB and BC are
kAB
kBC
p
A 0.022 B c68.9 A 109 B d
AAB E
4
=
=
= 72.152 A 106 B N>m
LAB
0.3
p
A 0.042 B c68.9 A 109 B d
ABC E
4
=
=
= 288.608 A 106 B N>m
LBC
0.3
Equilibrium requires
FAB = FBC
kAB ¢ AB = kBC ¢ BC
72.152 A 106 B ¢ AB = 288.608 A 106 B ¢ BC
¢ BC =
1
¢
4 AB
(1)
Conservation of Energy.
Ue = Ui
1
1
1
mv2 = kAB ¢ AB 2 + kBC ¢ BC 2
2
2
2
(2)
Substituting Eq. (1) into Eq. (2),
2
1
1
1
1
mv2 = kAB ¢ AB 2 + kBC a ¢ AB b
2
2
2
4
1
1
1
mv2 = kAB ¢ AB 2 +
k ¢ 2
2
2
32 BC AB
1
1
1
(5) A 42 B = c 72.152 A 106 B d ¢ AB 2 +
c288.608 A 106 B d ¢ AB 2
2
2
32
¢ AB = 0.9418 A 10 - 3 B m
Maximum Stress. The force developed in segment AB is FAB = kAB ¢ AB =
72.152 A 106 B c0.9418 A 10 - 3 B d = 67.954 A 103 B N.
Thus,
smax = sAB =
300 mm
300 mm
67.954 A 103 B
FAB
=
= 216.30 MPa = 216 MPa
p
AAB
2
0.02
A
B
4
Since smax 6 sY = 255 MPa, this result is valid.
1195
Ans.
v
A
20 mm
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*14–48. Determine the maximum speed v of the 5-kg
block without causing the 6061-T6 aluminum stepped
cylinder to yield after it is struck by the block.
C
B
40 mm
Equilibrium. The equivalent spring constant for segments AB and BC are
kAB
kBC
p
A 0.022 B C 68.9 A 109 B D
AAB E
4
=
=
= 72.152 A 106 B N>m
LAB
0.3
p
A 0.042 B C 68.9 A 109 B D
ABC E
4
=
=
= 288.608 A 106 B N>m
LBC
0.3
Equilibrium requires
FAB = FBC
kAB ¢ AB = kBC ¢ BC
72.152 A 106 B ¢ AB = 288.608 A 106 B ¢ BC
¢ BC =
1
¢
4 AB
(1)
Conservation of Energy.
Ue = Ui
1
1
1
mv2 = kAB ¢ AB 2 + kBC ¢ BC 2
2
2
2
(2)
Substituting Eq. (1) into Eq. (2),
2
1
1
1
1
mv2 = kAB ¢ AB 2 + kBC a ¢ AB b
2
2
2
4
1
1
1
mv2 = kAB ¢ AB 2 +
k ¢ 2
2
2
32 BC AB
1
1
1
(5)v2 = c72.152 A 106 B d ¢ AB 2 +
c288.608 A 106 B d ¢ AB 2
2
2
32
¢ AB = 0.23545 A 10 - 3 B v
Maximum Stress. The force developed in segment AB is FAB = kAB ¢ AB
= 72.152 A 106 B C 0.23545 A 10 - 3 B v D = 16988.46v.
Thus,
smax = sAB =
255 A 106 B =
300 mm
300 mm
FAB
AAB
16988.46v
p
A 0.022 B
4
v = 4.716 m>s = 4.72 m>s
Ans.
1196
v
A
20 mm
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•14–49. The steel beam AB acts to stop the oncoming
railroad car, which has a mass of 10 Mg and is coasting
towards it at v = 0.5 m>s . Determine the maximum stress
developed in the beam if it is struck at its center by the
car. The beam is simply supported and only horizontal
forces occur at A and B. Assume that the railroad car
and the supporting framework for the beam remains rigid.
Also, compute the maximum deflection of the beam.
Est = 200 GPa,sY = 250 MPa.
200 mm
v ⫽ 0.5 m/s
k =
1m
B
10(103)(9.81)(23)
PL3
= 0.613125(10 - 3) m
=
1
48EI
)(0.2)(0.23)
48(200)(104)(12
10(103)(9.81)
W
= 160(106) N>m
=
¢ st
0.613125(10 - 3)
¢ max =
0.613125(10 - 3)(0.52)
¢ st v2
=
= 3.953(10 - 3) m = 3.95 mm
C g
C
9.81
Ans.
W¿ = k¢ max = 160(106)(3.953)(10 - 3) = 632455.53 N
M¿ =
632455.53(2)
w¿L
=
= 316228 N # m
4
4
smax =
316228(0.1)
M¿c
= 237 MPa 6 sg
= 1
3
I
12 (0.2)(0.2 )
A
1m
From Appendix C:
¢ st =
200 mm
O.K.
Ans.
1197
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14–50. The aluminum bar assembly is made from two
segments having diameters of 40 mm and 20 mm.
Determine the maximum axial stress developed in the bar if
the 10-kg collar is dropped from a height of h = 150 mm.
Take Eal = 70 GPa, sY = 410 MPa.
C
1.2 m
40 mm
B
0.6 m
kAB =
kBC =
AAB E
=
LAB
p (0.012) C 70(109) D
0.6
= 11.667(106) p N>m
A
p (0.022) C 70(109) D
ABC E
=
= 23.333 (106) p N>m
LBC
1.2
Equilibrium requires
FAB = FBC
kAB ¢ AB = kBC ¢ BC
11.667(106) p ¢ AB = 23.333(106) p ¢ BC
¢ BC = 0.5 ¢ AB
(1)
Ue = Ui
mg (h + ¢ AB + ¢ BC) =
1
1
k ¢ 2 + kBC ¢ 2BC
2 AB AB
2
(2)
Substitute Eq. (1) into (2),
mg (h + ¢ AB + 0.5 ¢ AB) =
mg (h + 1.5¢ AB) =
1
1
k ¢ 2 + kBC (0.5¢ AB)2
2 AB AB
2
1
k ¢ 2 + 0.125 kBC ¢ 2AB
2 AB AB
10(9.81)(0.15 + 1.5¢ AB) =
1
C 11.667(106)p D ¢ 2AB + 0.125 C 23.333(106)p D ¢ 2AB
2
27.4889 (106)¢ 2AB - 147.15 ¢ AB - 14.715 = 0
¢ AB = 0.7343(10 - 3) m
The
force
developed
in
segment
AB
C 11.667(106)p D C 0.7343(10 - 3) D = 26.915(103) N. Thus
smax = sAB =
h
20 mm
is
FAB = kAB ¢ AB =
26.915(103)
FAB
= 85.67(106)Pa = 85.7 MPa
=
AAB
p (0.012)
Since smax 6 sy = 410 MPa, this result is valid
1198
Ans.
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14–51. The aluminum bar assembly is made from two
segments having diameters of 40 mm and 20 mm.
Determine the maximum height h from which the 60-kg
collar can be dropped so that it will not cause the bar to
yield. Take Eal = 70 GPa, sY = 410 MPa.
C
1.2 m
40 mm
B
0.6 m
kAB =
kBC =
p(0.012) C 70(109) D
AAB E
=
= 11.667(106) p N>m
LAB
0.6
A
p(0.022) C 70(109) D
ABC E
=
= 23.333(106) p N>m
LBC
1.2
Here, FAB = kAB ¢ AB = C 11.667(106)p D ¢ AB. It is required that smax = sAB = sy.
sy =
FAB
;
AAB
410(106) =
C 11.667(106)p D ¢ AB
p(0.012)
¢ AB = 0.003514 m
Equilibrium requires that
FAB = FBC
kAB ¢ AB = kBC ¢ BC
11.6667(106)p ¢ AB = 23.333(106)p ¢ BC
¢ BC = 0.5 ¢ B = 0.5(0.003514) = 0.001757 m
Ue = Ui
mg(h + ¢ AB + ¢ BC) =
1
1
k ¢ 2 + kBC ¢ 2BC
2 AB AB
2
60(9.81)(h + 0.003514 + 0.001757) =
1
C 11.667(106)p D (0.0035142)
2
+
h
20 mm
The equivalent spring constants for segment AB and BC are
1
C 23.333(106)p D (0.0017572)
2
h = 0.571 m
Ans.
1199
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*14–52. The 50-lb weight is falling at 3 ft>s at the instant it
is 2 ft above the spring and post assembly. Determine the
maximum stress in the post if the spring has a stiffness of
k = 200 kip>in. The post has a diameter of 3 in. and a
modulus of elasticity of E = 6.8011032 ksi. Assume the
material will not yield.
3 ft/s
2 ft
k
Equilibrium: This requires Fsp = FP. Hence
ksp ¢ sp = kP ¢ P
¢ sp = =
and
P
ksp
2 ft
¢P
[1]
Conservation of Energy: The equivalent spring constant for the post is
kp =
AE
=
L
p
4
(32) C 6.80(103) D
2(12)
= 2.003 A 106 B lb>in.
Ue = Ui
1
1
1
my2 + W(h + ¢ max) = kP ¢ 2P + ksp ¢ 2sp
2
2
2
[2]
However, ¢ max = ¢ P + ¢ sp. Then, Eq. [2] becomes
1
1
1
my2 + W A h + ¢ P + ¢ sp B = kP ¢ 2P + ksp ¢ 2sp
2
2
2
[3]
Substituting Eq. [1] into [3] yields
kp
1
1
1 k2P 2
my2 + W ¢ h + ¢ P +
¢ P ≤ = kP¢ 2P + ¢
¢ ≤
2
ksp
2
2 ksp P
2.003(106)
1 50
¢P R
¢
≤ A 32 B (12) + 50 B 24 + ¢ p +
2 32.2
200(103)
=
1 [2.003(106)]2
1
≤ ¢ 2P
C 2.003 A 106 B D ¢ 2P + ¢
2
2
200(103)
11.029 A 106 B ¢ 2P - 550.69¢ P - 1283.85 = 0
Solving for positive root, we have
¢ P = 0.010814 in.
Maximum Stress: The maximum axial force for the post is Pmax = kp ¢ p
= 2.003 A 106 B (0.010814) = 21.658 kip.
smax =
Pmax
21.658
= p 2 = 3.06 ksi
A
4 (3 )
Ans.
1200
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The 50-kg block is dropped from h = 600 mm
onto the bronze C86100 tube. Determine the minimum
length L the tube can have without causing the tube to yield.
•14–53.
A
30 mm
20 mm
Maximum Stress.
A = p A 0.03 - 0.02
2
B = 0.5 A 10 B p
50(9.81)L
WL
= 3.0317 A 10 - 6 B L
=
AE
C 0.5 A 10 - 3 B p D C 103 A 109 B D
¢ st =
sst =
h ⫽ 600 mm
-3
2
Section a – a
a
a
L
B
50(9.81)
W
=
= 0.3123 MPa
A
0.5 A 10 - 3 B p
Using these results,
n = 1 +
C
1 + 2a
Then,
h
0.6
395 821.46
b = 1 +
1 + 2B
R = 1 + 1 +
-6
¢ st
C
C
L
3.0317 A 10 B L
smax = sY = nsst
345 = ¢ 1 +
A
1 +
395 821.46
≤ (0.3123)
L
L = 0.3248 m = 325 mm
Ans.
14–54. The 50-kg block is dropped from h = 600 mm
onto the bronze C86100 tube. If L = 900 mm, determine
the maximum normal stress developed in the tube.
A
30 mm
20 mm
Maximum Stress.
A = p A 0.03 - 0.02
2
¢ st =
sst =
2
h ⫽ 600 mm
B = 0.5 A 10 B p
-3
50(9.81)(0.9)
WL
=
= 2.7285 A 10 - 6 B
AE
C 0.5 A 10 - 3 B p D C 103 A 109 B D
Section a – a
Thus,
C
B
50(9.81)
W
=
= 0.3123 MPa
A
0.5 A 10 - 3 B p
1 + 2a
0.6
h
b = 1 +
1 + 2B
R = 664.18
¢ st
C
2.7285 A 10 - 6 B
smax = nsst = 664.18(0.3123) = 207.40 MPa = 207 MPa
Since smax 6 sY = 345 MPa, this result is valid.
1201
a
L
Using these results,
n = 1 +
a
Ans.
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14–55. The steel chisel has a diameter of 0.5 in. and a
length of 10 in. It is struck by a hammer that weighs 3 lb, and
at the instant of impact it is moving at 12 ft兾s. Determine
the maximum compressive stress in the chisel, assuming
that 80% of the impacting energy goes into the chisel.
Est = 2911032 ksi, sY = 100 ksi.
k =
AE
=
L
p
4
(0.52)(29)(103)
10
= 569.41 kip>in.
10 in.
0.8 Ue = Ui
0.8c
3
1
1
a
b((12)(12))2 + 3¢ max d = (569.41)(103)¢ 2max
2 (32.2)(12)
2
¢ max = 0.015044 in.
P = k¢ max = 569.41(0.015044) = 8.566 kip
smax =
Pmax
8.566
= p
= 43.6 ksi 6 sg
2
A
4 (0.5)
O.K.
Ans.
*14–56. The sack of cement has a weight of 90 lb. If it is
dropped from rest at a height of h = 4 ft onto the center of
the W10 * 39 structural steel A-36 beam, determine the
maximum bending stress developed in the beam due to the
impact. Also, what is the impact factor?
h
12 ft
Impact Factor: From the table listed in Appendix C,
¢ st =
90[24(12)]3
PL3
= 7.3898 A 10 - 3 B in.
=
48EI
48[29.0(106)](209)
n = 1 +
= 1 +
C
1 + 2a
C
1 + 2a
h
b
¢ st
4(12)
7.3898(10 - 3)
b
= 114.98 = 115
Ans.
Maximum Bending Stress: The maximum moment occurs at mid-span where
90(24)(12)
PL
=
= 6480 lb # in.
Mmax =
4
4
sst =
6480(9.92>2)
Mmax c
=
= 153.78 psi
I
209
Thus,
smax = nsst = 114.98(153.78) = 17.7 ksi
Ans.
Since smax 6 sg = 36 ksi, the above analysis is valid.
1202
12 ft
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The sack of cement has a weight of 90 lb.
Determine the maximum height h from which it can be
dropped from rest onto the center of the W10 * 39
structural steel A-36 beam so that the maximum bending
stress due to impact does not exceed 30 ksi.
•14–57.
h
12 ft
Maximum Bending Stress: The maximum moment occurs at mid-span where
90(24)(12)
PL
Mmax =
=
= 6480 lb # in.
4
4
sst =
6480(9.92>2)
Mmax c
=
= 153.78 psi
I
209
However,
smax = nsst
30 A 103 B = n(153.78)
n = 195.08
Impact Factor: From the table listed in Appendix C,
¢ st =
90[24(12)]3
PL3
= 7.3898 A 10 - 3 B in.
=
48EI
48[29.0(106)](209)
n = 1 +
195.08 = 1 +
C
C
1 + 2a
h
b
¢ st
1 + 2a
h
b
7.3898(10 - 3)
h = 139.17 in. = 11.6 ft
Ans.
1203
12 ft
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14–58. The tugboat has a weight of 120 000 lb and is
traveling forward at 2 ft兾s when it strikes the 12-in.-diameter
fender post AB used to protect a bridge pier. If the post is
made from treated white spruce and is assumed fixed at the
river bed, determine the maximum horizontal distance
the top of the post will move due to the impact. Assume
the tugboat is rigid and neglect the effect of the water.
3 ft
A
C
12 ft
B
From Appendix C:
Pmax =
3EI(¢ C)max
(LBC)3
Conservation of energy:
1
1
mv2 = Pmax (¢ C)max
2
2
1
1 3EI(¢ C)2max
b
mv2 = a
2
2
(LBC)3
(¢ C)max =
(¢ C)max =
Pmax =
uC =
mv2L3BC
C 3EI
(120 000>32.2)(2)2(12)3
C (3)(1.40)(106)(144)(p4 )(0.5)4
3[1.40(106)](p4 )(6)4(11.177)
(144)3
= 0.9315 ft = 11.177 in.
= 16.00 kip
16.00(103)(144)2
PmaxL2BC
=
= 0.11644 rad
2EI
2(1.40)(106)(p4 )(6)4
(¢ A)max = (¢ C)max + uC(LCA)
(¢ A)max = 11.177 + 0.11644(36) = 15.4 in.
Ans.
1204
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14–59. The wide-flange beam has a length of 2L, a depth
2c, and a constant EI. Determine the maximum height h
at which a weight W can be dropped on its end without
exceeding a maximum elastic stress s max in the beam.
W
h
A
2c
B
L
L
1
1
(-Px)2 dx
P¢ C = 2 a
b
2
2EI L0
¢C =
2PL3
3EI
¢ st =
2WL3
3EI
n = 1 +
C
1 + 2a
h
b
¢ st
smax = n(sst)max
smax = B 1 +
a
C
1 + 2a
(sst)max =
WLc
I
h
WLc
b R
¢ st
I
2
smax I
2h
- 1b = 1 +
WLc
¢ st
h =
=
2
¢ st
smax I
- 1b - 1 R
Ba
2
WLc
smax I 2
2smaxI
smax L2 smax I
WL3
b - 2R
Ba
R =
B
3EI
WLc
WLc
3Ec
WLc
Ans.
1205
L
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*14–60. The 50-kg block C is dropped from h = 1.5 m
onto the simply supported beam. If the beam is an A-36
steel W250 * 45 wide-flange section, determine the
maximum bending stress developed in the beam.
C
h
Equilibrium. Referring to the free-body diagram of the beam under static
A
condition, Fig. a
a + ©MA = 0;
By(6) - P(4) = 0
By =
2
P
3
4m
Then, the maximum moment in the beam occurs at the position where P is
applied. Thus,
Mmax = By(2) =
2
4
P(2) = P
3
3
Impact Factor. From the table listed in the appendix, the deflection of the beam at
Pba
the point of application of P is ¢ =
A L2 - b2 - a2 B , where P = 50(9.81)
6EIL
= 490.5 N, L = 6 m, a = 4 m, and b = 2 m. From the table listed in the appendix,
the necessary section properties for a W250 * 45 are d = 266 mm = 0.266 m and
Ix = 71.1 A 106 B mm4 = 71.1 A 10 - 6 B m4. Then
¢ st =
490.5(2)(4)
6c 200 A 10 B d c 71.1 A 10
9
-6
B d(6)
A 62 - 22 - 42 B = 0.1226 A 10 - 3 B m
We have,
n = 1 +
Maximum
C
1 + 2¢
Stress.
h
1.5
1 + 2C
S = 157.40
≤ = 1 +
¢ st
Q
0.1226 A 10 - 3 B
The
maximum
= 157.40(490.5) = 77.21 A 10 B N.
3
= 102.94 A 10
smax =
3
force
Then,
on
B N # m. Applying the flexure formula,
beam is Pmax = nP
4
4
= Pmax = C 77.21 A 103 B D
3
3
the
Mmax
102.94 A 103 B (0.266>2)
Mmaxc
=
= 192.56 MPa = 193 MPa
I
71.1 A 10 - 6 B
Since smax 6 sY = 250 MPa, this result is valid.
1206
B
Ans.
2m
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Determine the maximum height h from which the
50-kg block C can be dropped without causing yielding in
the A-36 steel W310 * 39 wide flange section when the
block strikes the beam.
•14–61.
C
h
A
B
4m
Equilibrium. Referring to the free-body diagram of the beam under static
condition, Fig. a
a + ¢MA = 0;
By(6) - P(4) = 0
By =
2
P
3
Then, the maximum moment in the beam occurs at the position where P is
applied. Thus,
Mmax = By(2) =
4
2
P(2) = P
3
3
Maximum Stress. Since P = 50(9.81) = 490.5 N. Then the maximum force on the
4
4
beam is Pmax = nP = 490.5n and Mmax = P = (490.5n) = 654n. From the
3
3
table listed in the appendix, the necessary section properties for a W310 * 39 are
d = 310 mm = 0.31 m and Ix = 84.8 A 106 B mm4 = 84.8 A 10 - 6 B m4. Applying the
flexure formula,
smax =
Mmax c
I
250 A 106 B =
654n(0.31>2)
84.8 A 10 - 6 B
n = 209.13
Impact Factor. From the table listed in the appendix, the deflection of the beam at
Pba
the point of where P is applied is ¢ =
A L2 - b2 - a2 B , where L = 6 m,
6EIL
a = 4 m, and b = 2 m. Then
¢ st =
490.5(2)(4)
6 C 200 A 109 B D C 84.8 A 10 - 6 B D (6)
A 62 - 22 - 42 B = 0.1028 A 10 - 3 B m
We have,
n = 1 +
C
1 + 2¢
209.13 = 1 +
S
h
≤
¢ st
1 + 2C
h = 2.227 m = 2.23 m
h
0.1028 A 10 - 3 B
S
Ans.
Since smax 6 sY = 250 MPa, this result is valid.
1207
2m
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14–62. The diver weighs 150 lb and, while holding himself
rigid, strikes the end of a wooden diving board 1h = 02 with
a downward velocity of 4 ft>s. Determine the maximum
bending stress developed in the board. The board has a
thickness of 1.5 in. and width of 1.5 ft. Ew = 1.811032 ksi,
sY = 8 ksi.
v
h
4 ft
Static Displacement: The static displacement at the end of the diving board can be
determined using the conservation of energy.
L
1
M2 dx
P¢ =
2
L0 2EI
1
1
(150)¢ st =
c
2
2EI L0
¢ st =
=
4 ft
(-375x1)2 dx1 +
70.0(103) lb # ft3
EI
L0
10 ft
(-150x2) dx2 d
70.0(103)(123)
1
(18)(1.53) D
1.8(106) C 12
= 13.274 in.
Conservation of Energy: The equivalent spring constant for the board is
W
150
k =
=
= 11.30 lb>in.,
¢ st
13.274
Ue = Ui
1
1
my2 + W¢ max = k¢ 2max
2
2
c
1 150
1
a
b A 42 B d (12) + 150¢ max = (11.30)¢ 2max
2 32.2
2
Solving for the positive root, we have
¢ max = 29.2538 in.
Maximum Stress: The maximum force on to the beam is Pmax = k¢ max
= 11.30(29.2538) = 330.57 lb. The maximum moment occurs at the middle support
Mmax = 330.57(10)(12) = 39668.90 lb # in.
smax =
39668.90(0.75)
Mmax c
= 5877 psi = 5.88 ksi
= 1
3
I
12 (18)(1.5 )
Ans.
Note: The result will be somewhat inaccurate since the static displacement is so large.
1208
10 ft
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14–63. The diver weighs 150 lb and, while holding himself
rigid, strikes the end of the wooden diving board.
Determine the maximum height h from which he can jump
onto the board so that the maximum bending stress in the
wood does not exceed 6 ksi. The board has a thickness of
1.5 in. and width of 1.5 ft. Ew = 1.811032 ksi.
v
Static Displacement: The static displacement at the end of the diving board can be
determined using the conservation of energy.
h
L
M2 dx
1
P¢ =
2
L0 2EI
1
1
(150)¢ st =
c
2
2EI L0
¢ st =
=
4 ft
4 ft
(-375x1)2 dx1 +
70.0(103) lb # ft3
EI
L0
10 ft
(-150x2) dx2 d
70.0(103)(123)
1
(18)(1.53) D
1.8(106) C 12
= 13.274 in.
Maximum Stress: The maximum force on the beam is Pmax. The maximum moment
occurs at the middle support Mmax = Pmax (10)(12) = 120Pmax.
smax =
6 A 103 B =
Mmax c
I
120Pmax (0.75)
1
12
(18)(1.53)
Pmax = 337.5 lb
Conservation of Energy: The equivalent spring constant for the board is
150
W
=
= 11.30 lb>in.. The maximum displacement at the end of the
k =
¢ st
13.274
Pmax
337.5
board is ¢ max =
=
= 29.687 in.
k
11.30
Ue = Ui
W(h + ¢ max) =
150(h + 29.867) =
1
k¢ 2max
2
1
(11.30) A 29.8672 B
2
h = 3.73 in.
Ans.
Note: The result will be somewhat at inaccurate since the static displacement is so large.
1209
10 ft
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*14–64. The weight of 175 lb is dropped from a height of
4 ft from the top of the A-36 steel beam. Determine the
maximum deflection and maximum stress in the beam if the
supporting springs at A and B each have a stiffness of
k = 500 lb>in. The beam is 3 in. thick and 4 in. wide.
4 ft
A
k
8 ft
8 ft
From Appendix C:
¢ beam =
PL3
48EI
kbeam =
1
)(4)(33)
48(29)(103)(12
48EI
=
= 1.7700 kip>in.
3
L
(16(12))3
From equilibrium (equivalent system):
2Fsp = Fbeam
2ksp ¢ sp = kbeam ¢ beam
¢ sp =
1.7700(103)
¢ beam
2(500)
¢ sp = 1.7700¢ beam
(1)
Conservation of energy:
Ue = Ui
W(h + ¢ sp + ¢ beam) =
1
1
k
¢2
+ 2 a bksp ¢ 2sp
2 beam beam
2
From Eq. (1):
175[(4)(12) + 1.770¢ beam + ¢ beam] =
1
(1.7700)(103)¢ 2beam + 500(1.7700¢ beam)2
2
2451.5¢ 2beam - 484.75¢ beam - 8400 = 0
¢ beam = 1.9526 in.
From Eq. (1):
¢ sp = 3.4561 in.
¢ max = ¢ sp + ¢ beam
= 3.4561 + 1.9526 = 5.41 in.
Ans.
Fbeam = kbeam ¢ beam
= 1.7700(1.9526) = 3.4561 kip
Mmax =
smax =
3.4561(16)(12)
Fbeam L
=
= 165.893 kip # in.
4
4
165.893(1.5)
Mmax c
= 27.6 ksi 6 sg
= 1
3
I
12 (4)(3 )
O.K.
Ans.
1210
3 in.
B
k
4 in.
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The weight of 175 lb, is dropped from a height of
4 ft from the top of the A-36 steel beam. Determine the
load factor n if the supporting springs at A and B each
have a stiffness of k = 300 lb/in. The beam is 3 in. thick
and 4 in. wide.
•14–65.
4 ft
A
k
8 ft
8 ft
From Appendix C:
¢ beam =
PL3
48EI
kbeam =
1
)(4)(33)
48(29)(103)(12
48EI
=
= 1.7700 kip>in.
L3
(16(12))3
From equilibrium (equivalent system):
2Fsp = Fbeam
2ksp ¢ sp = kbeam ¢ beam
¢ sp =
1.7700(103)
¢ beam
2(300)
¢ sp = 2.95¢ beam
(1)
Conservation of energy:
Ue = Ui
W(h + ¢ beam + ¢ sp) =
1
1
k
¢2
+ 2a b ksp ¢ 2sp
2 beam beam
2
From Eq. (1):
175[(4)(12) + ¢ beam + 2.95¢ beam] =
1
(1.7700)(103)¢ 2beam + 300(2.95¢ beam)2
2
3495.75¢ 2beam - 691.25¢ beam - 8400 = 0
¢ beam = 1.6521 in.
Fbeam = kbeam ¢ beam
= 1.7700(1.6521) = 2.924 kip
n =
2.924(103)
= 16.7
175
smax = n(sst)max = na
M =
Ans.
Mc
b
I
175(16)(12)
= 8.40 kip # in.
4
smax = 16.7 a
8.40(1.5)
1
12
(4)(33)
b = 23.4 ksi 6 sg
O.K.
1211
3 in.
B
k
4 in.
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14–66. Block C of mass 50 kg is dropped from height
h = 0.9 m onto the spring of stiffness k = 150 kN>m
mounted on the end B of the 6061-T6 aluminum cantilever
beam. Determine the maximum bending stress developed
in the beam.
C
h
a
k
100 mm
B
Conservation of Energy. From the table listed in the appendix, the
PL
. Thus, the
=
3EI
equivalent spring constant for the beam is kb =
1
(0.1) A 0.23 B = 66.6667 A 10 - 6 B m4,
12
a
3
displacement of end B under static conditions is ¢ st
I =
A
L = 3 m,
3m
3EI
, where
L3
and
E = Eal
= 68.9 GPa. Thus,
3EI
kb =
=
L3
3 c68.9 A 109 B d c66.6667 A 10 - 6 B d
33
= 510.37 A 103 B N>m
Equilibrium requires,
Fsp = P
ksp ¢ sp = kb ¢ b
150 A 103 B ¢ sp = 510.37 A 103 B ¢ b
¢ sp = 3.4025¢ b
(1)
We have,
Ue = Ui
mg A h + ¢ sp + ¢ b B =
1
1
k ¢ 2 + ksp ¢ sp 2
2 b b
2
Substituting Eq. (1) into this equation,
50(9.81)(0.9 + 3.4025¢ b + ¢ b) =
1
1
c510.37 A 103 B d ¢ b 2 + c150 A 103 B d(3.4025¢ b)2
2
2
1123444.90¢ b 2 - 2159.41¢ b - 441.45 = 0
Solving for the positive root,
¢ b = 0.020807 m
Maximum
Stress.
The
maximum
force
Pmax = kb ¢ b = 510.37 A 10 B (0.020807) = 10.619 A 10
3
occurs
at
= 31.858 A 103 B
smax =
3
on
the
beam
is
B N. The maximum moment
Mmax = Pmax L = 10.619 A 103 B (3)
0.2
N # m. Applying the flexure formula with c =
= 0.1 m,
2
fixed
support
A,
where
31.858 A 103 B (0.1)
Mmax c
=
= 47.79 MPa = 47.8 MPa
I
66.6667 A 10 - 6 B
Since smax 6 sY = 255 MPa, this result is valid.
1212
Ans.
200 mm
Section a – a
14 Solutions 46060_Part1
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14–67. Determine the maximum height h from which
200-kg block C can be dropped without causing the 6061-T6
aluminum cantilever beam to yield. The spring mounted on
the end B of the beam has a stiffness of k = 150 kN>m.
C
h
a
k
100 mm
B
A
a
3m
Maximum Stress. From the table listed in the appendix, the displacement of end B
PL3
under static conditions is ¢ st =
. Thus, the equivalent spring constant for the
3EI
3EI
1
beam is kb =
, where I =
(0.1) A 0.23 B = 66.6667 A 10 - 6 B m4, L = 3 m, and
12
L3
E = Eal = 68.9 GPa. Thus,
3EI
=
kb =
L3
3 c68.9 A 109 B d c66.6667 A 10 - 6 B d
33
= 510.37 A 103 B N>m
The maximum force on the beam is Pmax = kb ¢ b = 510.37 A 103 B ¢ b. The maximum
moment occurs at the fixed support A, where Mmax = Pmax L = 510.37 A 103 B ¢ b(3)
= 1.5311 A 106 B ¢ b. Applying the flexure formula with smax = sY = 255 MPa and
0.2
c =
= 0.1 m,
2
smax = sY =
255 A 106 B =
Mmax c
I
1.5311 A 106 B ¢ b(0.1)
66.6667 A 10 - 6 B
¢ b = 0.11103 m
Equilibrium requires,
Fsp = P
ksp ¢ sp = kb ¢ b
150 A 103 B ¢ sp = 510.37 A 103 B (0.11103)
¢ sp = 0.37778 m
Conservation of Energy.
Ue = Ui
mg A h + ¢ sp + ¢ b B =
1
1
kb ¢ b 2 + ksp ¢ sp 2
2
2
200(9.81)(h + 0.37778 + 0.11103) =
1
1
c510.37 A 103 B d(0.11103)2 + c150 A 103 B d(0.37778)2
2
2
h = 6.57 m
Ans.
1213
200 mm
Section a – a
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*14–68. The 2014-T6 aluminum bar AB can slide freely
along the guides mounted on the rigid crash barrier. If the
railcar of mass 10 Mg is traveling with a speed of
v = 1.5 m>s, determine the maximum bending stress
developed in the bar. The springs at A and B have a stiffness
of k = 15 MN>m.
300 mm
k
A
v
2m
2m
a
a
k
B
Equilibrium. Referring to the free-body diagram of the bar for static conditions, Fig. a,
+ ©F = 0;
:
x
2Fsp - P = 0
Fsp =
P
2
(1)
300 mm
400 mm
Referring to the table listed in the appendix, the displacement of the bar at the
PL3
position where P is applied under static conditions is ¢ st =
. Thus, the
48EI
1
48EI
equivalent spring constant for the bar is kb =
, where I =
(0.4) A 0.33 B
12
L3
and
Thus,
= 0.9 A 10 - 3 B m4,
L = 4 m,
E = Eal = 73.1 GPa.
kb =
48 c73.1 A 109 B d c0.9 A 10 - 3 B d
43
= 49.3425 A 106 B N>m
Using Eq. (1)
Fsp =
P
2
ksp ¢ sp =
1
k ¢
2 b b
1 49.3425 A 10
1 kb
¢ ≤ ¢b = C
2 ksp
2
15 A 106 B
6
¢ sp =
B
S ¢ b = 1.64475¢ b
Conservation of Energy.
1
1
1
mv2 = kb ¢ b 2 + 2 c ksp ¢ sp 2 d
2
2
2
Substituting Eq. (2) into this equation,
1
1
mv2 = kb ¢ b 2 + ksp (1.64475¢ b)2
2
2
1
1
mv2 = kb ¢ b 2 + 2.7052ksp ¢ b 2
2
2
1
1
c10 A 103 B d A 1.52 B = c49.3425 A 106 B d ¢ b 2 + 2.7052c15 A 106 B d ¢ b 2
2
2
¢ b = 0.01313 m
1214
(2)
Section a – a
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14–68. Continued
Maximum
Stress.
The
maximum
force
on
the
bar
is
(Pb)max = kb ¢ b = 49.3425 A 106 B (0.01313) = 647.90 A 103 B N. The maximum moment
occurs at the midspan of the bar, where Mmax =
= 647.90 A 103 B N # m. Applying the flexure formula,
smax =
647.90 A 103 B (4)
(Pb)max L
=
4
4
647.90 A 103 B (0.15)
Mmax c
=
= 107.98 MPa = 108 MPa
I
0.9 A 10 - 3 B
Since smax 6 sY = 414 MPa, this result is valid.
1215
Ans.
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8:18 AM
Page 1216
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exist. No portion of this material may be reproduced, in any form or by any means, without permission in writing from the publisher.
•14–69. The 2014-T6 aluminum bar AB can slide freely
along the guides mounted on the rigid crash barrier.
Determine the maximum speed v the 10-Mg railcar without
causing the bar to yield when it is struck by the railcar. The
springs at A and B have a stiffness of k = 15 MN>m.
300 mm
k
A
v
2m
2m
a
a
k
B
Equilibrium. Referring to the free-body diagram of the bar for static conditions, Fig. a,
+ ©F = 0;
:
x
2Fsp - P = 0
Fsp
P
=
2
(1)
300 mm
400 mm
Referring to the table listed in the appendix, the displacement of the bar at the
PL3
position where P is applied under static conditions is ¢ st =
. Thus, the
48EI
1
48EI
equivalent spring constant for the bar is kb =
, where I =
(0.4) A 0.33 B
12
L3
and
Thus,
= 0.9 A 10 - 3 B m4,
L = 4 m,
E = Eal = 73.1 GPa.
kb =
48 c73.1 A 109 B d c0.9 A 10 - 3 B d
43
= 49.3425 A 106 B N>m
Using Eq. (1)
Fsp =
P
2
ksp ¢ sp =
1
k ¢
2 b b
1 49.3425 A 10
1 kb
¢ ≤ ¢b = C
2 ksp
2
15 A 106 B
6
B
S ¢ b = 1.64475¢ b
(2)
Maximum Stress. The maximum force on the bar is
(Pb)max = kb ¢ b
¢ sp =
= 49.3425 A 106 B ¢ b. The maximum moment occurs at the midspan of the bar, where
49.3425 A 106 B ¢ b(4)
(Pb)max L
=
= 49.3425 A 106 B ¢ b. Applying the flexure
Mmax =
4
4
formula with smax = sY = 414 MPa,
smax =
Mmax c
I
414 A 106 B =
49.3425 A 106 B ¢ b (0.15)
0.9 A 10 - 3 B
¢ b = 0.050342 m
1216
Section a – a
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8:18 AM
Page 1217
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exist. No portion of this material may be reproduced, in any form or by any means, without permission in writing from the publisher.
14–69. Continued
Substituting this result into Eq. (2),
¢ sp = 0.0828 m
Conservation of Energy.
1
1
1
mv2 = kb ¢ b 2 + 2 B ksp ¢ sp 2 R
2
2
2
1
1
1
c 10 A 103 B dv2 = c49.3425 A 106 B d A 0.0503422 B + 2 B c15 A 106 B d A 0.08282 B R
2
2
2
v = 5.75 m>s
Ans.
1217
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8:18 AM
Page 1218
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exist. No portion of this material may be reproduced, in any form or by any means, without permission in writing from the publisher.
14–70. The simply supported W10 * 15 structural A-36
steel beam lies in the horizontal plane and acts as a shock
absorber for the 500-lb block which is traveling toward it at
5 ft兾s. Determine the maximum deflection of the beam and
the maximum stress in the beam during the impact. The
spring has a stiffness of k = 1000 lb>in.
For W 10 * 15: I = 68.9 in4
12 ft
v ⫽ 5 ft/s
d = 9.99 in.
k
From Appendix C:
¢ beam =
PL3
48EI
kbeam =
48(29)(103)(68.9)
48EI
=
= 4.015 kip>in.
L3
(24(12))3
12 ft
Equilibrium (equivalent system):
Fsp = Fbeam
ksp ¢ sp = kbeam ¢ beam
¢ sp =
4.015(103)
¢ beam
1000
¢ sp = 4.015¢ beam
(1)
Conservation of energy:
Ue = Ui
1
1
1
mv2 = kbeam ¢ 2beam + ksp ¢ 2sp
2
2
2
From Eq. (1):
500
1
1
1
a
b (5(12))2 = (4.015)(103)¢ 2beam + (1000)(4.015¢ beam)2
2 32.2(12)
2
2
10067.6¢ 2beam = 2329.2
¢ beam = 0.481 in.
Ans.
Fbeam = kbeam ¢ beam
= 4.015(0.481) = 1.931 kip
Mmax = a
smax =
1.931
b (12) (12) = 139.05 kip # in.
2
139.05(9.99
Mmax c
2 )
=
= 10.1 ksi 6 sg
I
68.9
O.K.
Ans.
1218
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exist. No portion of this material may be reproduced, in any form or by any means, without permission in writing from the publisher.
14–71. The car bumper is made of polycarbonatepolybutylene terephthalate. If E = 2.0 GPa, determine the
maximum deflection and maximum stress in the bumper if it
strikes the rigid post when the car is coasting at v = 0.75 m/s.
The car has a mass of 1.80 Mg, and the bumper can
be considered simply supported on two spring supports
connected to the rigid frame of the car. For the bumper
take I = 30011062 mm4, c = 75 mm, sY = 30 MPa and
k = 1.5 MN>m.
0.9 m
k
0.9 m
k
v ⫽ 0.75 m/s
Equilibrium: This requires Fsp =
ksp ¢ sp =
k¢ beam
2
Pbeam
. Then
2
or
¢ sp =
k
¢
2ksp beam
[1]
Conservation of Energy: The equivalent spring constant for the beam can be
determined using the deflection table listed in the Appendix C.
k =
48 C 2(109) D C 300(10 - 6) D
48EI
=
= 4 938 271.6 N>m
L3
1.83
Thus,
Ue = Ui
1
1
1
my2 = k¢ 2beam + 2 a ksp ¢ 2sp b
2
2
2
[2]
Substitute Eq. [1] into [2] yields
1
1
k2
mv2 = k¢ 2beam +
¢2
2
2
4ksp beam
(4 93 8271.6)2 2
1
1
¢ beam
(1800) A 0.752 B = (493 8271.6) ¢ 2beam +
2
2
4[1.5(106)]
¢ beam = 8.8025 A 10 - 3 B m
Maximum Displacement: From Eq. [1] ¢ sp =
4 938 271.6
2[1.5(106)]
C 8.8025 A 10 - 3 B D =
0.014490 m.
¢ max = ¢ sp + ¢ beam
= 0.014490 + 8.8025 A 10 - 3 B
= 0.02329 m = 23.3 mm
Ans.
Maximum Stress: The maximum force on the beam is Pbeam = k¢ beam =
4 938 271.6 C 8.8025 A 10 - 3 B D = 43 469.3 N. The maximum moment
occurs at mid-span. Mmax =
smax =
43 469.3(1.8)
Pbeam L
=
= 19 561.2 N # m.
4
4
19 561.2(0.075)
Mmax c
= 4.89 MPa
=
I
300(10 - 6)
Ans.
Since smax 6 sg = 30 MPa, the above analysis is valid.
1219
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*14–72. Determine the horizontal displacement of joint B
on the two-member frame. Each A-36 steel member has a
cross-sectional area of 2 in2.
800 lb
B
30⬚
60⬚
C
A
Member
n
N
L
nNL
AB
1.1547
800
120
11085.25
BC
–0.5774
0
60
0
5 ft
© = 110851.25
1 # ¢ Bh = ©
¢ Bh =
nNL
AE
110851.25
110851.25
= 0.00191 in.
=
AE
29(106)(2)
Ans.
Determine the horizontal displacement of point B.
Each A-36 steel member has a cross-sectional area of 2 in2.
•14–73.
B
200 lb
Member Real Forces N: As shown on figure(a).
8 ft
Member Virtual Forces n: As shown on figure(b).
nNL
1#¢ = a
AE
1 lb # (¢ B)h =
6 ft
1
[0.8333(166.67)(10)(12)
AE
+( -0.8333)(-166.67)(10)(12)
+0.500(100)(12)(12)]
1 lb # (¢ B)h =
(¢ B)h =
40533.33 lb2 # in
AE
40533.33
2[29.0(106)]
A
C
Virtual-Work Equation:
= 0.699 A 10 - 3 B in. :
Ans.
1220
6 ft
14 Solutions 46060_Part1
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8:18 AM
Page 1221
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14–74. Determine the vertical displacement of point B.
Each A-36 steel member has a cross-sectional area of 2 in2.
B
200 lb
Member Real Forces N: As shown on figure(a).
8 ft
Member Virtual Forces n: As shown on figure(b).
A
C
Virtual-Work Equation:
nNL
1#¢ = a
AE
1 lb # (¢ B)v =
6 ft
6 ft
1
[(-0.625)(166.67)(10)(12)
AE
+(-0.625)(-166.67)(10)(12)
+0.375(100)(12)(12)]
1 lb # (¢ B)v =
(¢ B)v =
5400 lb2 # in
AE
5400
2[29.0(106)]
= 0.0931 A 10 - 3 B in. T
Ans.
14–75. Determine the vertical displacement of joint C on
the truss. Each A-36 steel member has a cross-sectional area
of A = 300 mm2.
Member
n
N
L
3m
C
A
1.50
45.0
3
202.5
AD
0
18.03
213
0
BC
1.50
45.0
3
202.5
BD
0
–20.0
2
0
CD
–1.803
–54.08
213
351.56
DE
–1.803
–72.11
213
468.77
4m
D
E
© = 1225.33
¢ Cv =
nNL
AE
1225.33(103)
300(10 - 6)(200)(109)
3m
B
nNL
AB
1 # ¢ Cv = ©
30 kN
20 kN
= 0.0204 m = 20.4 mm
Ans.
1221
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8:18 AM
Page 1222
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exist. No portion of this material may be reproduced, in any form or by any means, without permission in writing from the publisher.
*14–76. Determine the vertical displacement of joint D on
the truss. Each A-36 steel member has a cross-sectional area
of A = 300 mm2.
30 kN
20 kN
3m
3m
B
C
A
Member
n
N
L
nNL
4m
AB
0
45.0
3
0
AD
0.9014
18.03
213
58.60
BC
0
45.0
3
0
BD
0
–20.0
2
0
CD
0
–54.08
213
0
DE
–0.9014
–72.11
213
234.36
D
E
© = 292.96
1 # ¢ Dv = ©
¢ Dv =
nNL
AE
292.96(103)
300(10 - 6)(200)(109)
= 4.88(10 - 3) m = 4.88 mm
Ans.
Determine the vertical displacement of point B.
Each A-36 steel member has a cross-sectional area of 4.5 in2.
•14–77.
F
E
D
Virtual-Work Equation: Applying Eq. 14–39, we have
Member
n
AB
BC
6 ft
N
L
nNL
0.6667
3.333
96
213.33
0.6667
3.333
96
213.33
A
C
B
CD
0
0
72
0
DE
0
0
96
0
EF
0
0
96
0
AF
0
0
72
0
AE
–0.8333
–4.167
120
416.67
CE
–0.8333
–4.167
120
416.67
BE
1.00
5.00
72
360.00
8 ft
©1620 kip2 # in.
nNL
1#¢ = a
AE
1 kip # (¢ B)v =
(¢ B)v =
8 ft
5 kip
1620 kip2 # in.
AE
1620
= 0.0124 in. T
4.5[29.0(103)]
Ans.
1222
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8:18 AM
Page 1223
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exist. No portion of this material may be reproduced, in any form or by any means, without permission in writing from the publisher.
14–78. Determine the vertical displacement of point E.
Each A-36 steel member has a cross-sectional area of 4.5 in2.
F
E
D
6 ft
Virtual-Work Equation: Applying Eq. 14–39, we have
Member
n
N
L
nNL
AB
0.6667
3.333
96
213.33
BC
0.6667
3.333
96
213.33
CD
0
0
72
0
DE
0
0
96
0
EF
0
0
96
0
AF
0
0
72
0
AE
–0.8333
–4.167
120
416.67
CE
–0.8333
–4.167
120
416.67
BE
0
5.00
72
0
A
C
B
8 ft
8 ft
5 kip
©1260 kip2 # in.
nNL
1#¢ = a
AE
1 kip # (¢ E)v =
(¢ E)v =
1260 kip2 # in.
AE
1260
= 0.00966 in. T
4.5[29.0(103)]
Ans.
14–79. Determine the horizontal displacement of joint B
of the truss. Each A-36 steel member has a cross-sectional
area of 400 mm2.
5 kN
4 kN
2m
C
B
Member
n
N
L
nNL
AB
0
0
1.5
0
AC
–1.25
–5.00
2.5
15.625
AD
1.00
4.00
2.0
8.000
BC
1.00
4.00
2.0
8.000
CD
0.75
–2.00
1.5
–2.25
1.5 m
D
A
© = 29.375
1 # ¢ Bh = ©
¢ Bh =
nNL
AE
29.375(103)
400(10 - 6)(200)(109)
= 0.3672(10 - 3)m = 0.367 mm
Ans.
1223
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*14–80. Determine the vertical displacement of joint C of
the truss. Each A-36 steel member has a cross-sectional area
of 400 mm2.
5 kN
2m
4 kN
C
B
Member
n
N
L
nNL
AB
0
0
1.5
0
AC
0
–5.00
2.5
0
AD
0
4.00
2.0
0
BC
0
4.00
2.0
0
CD
–1.00
–2.00
1.5
3.00
1.5 m
D
A
© = 3.00
1 # ¢ Cv = ©
¢ Cv =
nNL
AE
3.00 (103)
400(10 - 6)(200)(109)
= 37.5(10 - 6)m = 0.0375 mm
Ans.
Determine the vertical displacement of point A.
Each A-36 steel member has a cross-sectional area of
400 mm2.
•14–81.
E
D
Virtual-Work Equation:
Member
n
AB
–0.750
BC
–0.750
AE
1.25
CE
–1.25
BE
0
DE
2m
N
1.50
–22.5 A 103 B
–22.5 A 103 B
37.5 A 10
3
–62.5 A 10
3
60.0 A 10
3
B
B
22.0 A 103 B
B
nNL
1#¢ = a
AE
1 N # (¢ A)v =
(¢ A)v =
L
1.5
1.5
2.5
2.5
2
1.5
nNL
25.3125 A 103 B
C
A
25.3125 A 103 B
117.1875 A 10
3
195.3125 A 10
3
135.00 A 10
3
B
1.5 m
B
B
30 kN
0
B
© 498.125 A 103 B N2 # m
498.125(103) N2 # m
AE
498.125(103)
0.400(10 - 3)[200(109)]
= 6.227 A 10 - 3 B m = 6.23 mm T
Ans.
1224
1.5 m
20 kN
14 Solutions 46060_Part1
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14–82. Determine the vertical displacement of point B.
Each A-36 steel member has a cross-sectional area of
400 mm2.
E
D
2m
C
A
B
1.5 m
Virtual-Work Equation:
Member
AB
n
N
0
BC
0
AE
0
CE
–1.25
BE
1.00
DE
0.750
–22.5 A 103 B
–22.5 A 10
3
–62.5 A 10
3
B
37.5 A 103 B
B
22.0 A 103 B
60.0 A 103 B
nNL
1#¢ = a
AE
1 N # (¢ B)v =
(¢ B)v =
L
30 kN
nNL
1.5
0
1.5
0
2.5
2.5
2
1.5
195.3125 A 10
0
3
B
40.0 A 103 B
67.5 A 103 B
© 302.8125 A 103 B N2 # m
302.8125(103) N2 # m
AE
302.8125(103)
0.400(10 - 3)[200(109)]
= 3.785 A 10 - 3 B m = 3.79 mm T
Ans.
1225
1.5 m
20 kN
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14–83. Determine the vertical displacement of joint C.
Each A-36 steel member has a cross-sectional area of
4.5 in2.
1 # ¢ Cv = ©
¢ Cv =
J
A
nNL
AE
B
12 ft
Ans.
*14–84. Determine the vertical displacement of joint H.
Each A-36 steel member has a cross-sectional area of
4.5 in2.
¢ Hv =
H
G
F
9 ft
21 232
= 0.163 in.
4.5 (29(103))
1 # ¢ Nv = ©
I
C
12 ft
12 ft
12 ft
6 kip
8 kip
6 kip
I
H
G
J
E
D
F
9 ft
A
nNL
AE
12 ft
20 368
= 0.156 in.
4.5 (29(103))
Ans.
1226
C
B
12 ft
6 kip
12 ft
8 kip
E
D
12 ft
6 kip
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Determine the vertical displacement of joint
C. The truss is made from A-36 steel bars having a
cross- sectional area of 150 mm2.
•14–85.
G
2m
H
Member Real Forces N. As indicated in Fig. a.
F
2m
Member Virtual Forces n. As indicated in Fig. b.
18 A 103 B
Virtual Work Equation. Since smax =
Member
AB
n(N)
N(N)
9 A 10
0.375
DE
0.375
BC
0.375
CD
0.375
AH
–0.625
EF
–0.625
BH
0
DF
0
CH
0
CF
0
GH
–0.625
FG
–0.625
CG
1
0.15 A 10 - 3 B
9 A 10
3
3
B
B
9 A 103 B
9 A 103 B
–15 A 103 B
–15 A 103 B
6 A 103 B
6 A 10
3
–3.75 A 10
3
B
–3.75 A 103 B
B
–11.25 A 103 B
–11.25 A 103 B
18 A 103 B
nNL(N
L(m)
2
# m)
5.0625 A 10
1.5
5.0625 A 10
1.5
3
3
B
B
5.0625 A 103 B
1.5
24.4375 A 103 B
2.5
2.5
24.4375 A 103 B
2
0
2
0
2.5
0
2.5
0
17.578125 A 103 B
2.5
17.578125 A 103 B
2.5
72 A 103 B
©174.28125 A 103 B
Then
1#¢ = ©
1N # (¢ C)v
nNL
AE
=
174.28125 A 103 B
0.15 A 10 - 3 B C 200 A 109 B D
(¢ C)v = 5.809 A 10 - 3 B m = 5.81 mm T
Ans.
1227
B
1.5 m
1.5 m
6 kN
5.0625 A 103 B
1.5
4
E
A
= 120 MPa 6 sY = 250 MPa,
C
1.5 m
12 kN
D
1.5 m
6 kN
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14–86. Determine the vertical displacement of joint
G. The truss is made from A-36 steel bars having a
cross-sectional area of 150 mm2.
G
2m
H
Member Real Forces N. As indicated in Fig. a.
F
2m
Member Virtual Forces n. As indicated in Fig. b.
E
A
Virtual
Work
Since
Equation.
18 A 10 B
FCG
= 120 MPa 6 sY = 250 MPa,
=
=
A
0.15 A 10 - 3 B
3
smax
Member
n(N)
AB
0.375
DE
0.375
BC
0.375
CD
0.375
AH
–0.625
EF
–0.625
BH
0
DF
0
CH
0
CF
0
GH
FG
CG
–0.625
–0.625
N(N)
9 A 103 B
9 A 103 B
9 A 103 B
9 A 103 B
–15 A 103 B
–15 A 103 B
6 A 103 B
6 A 103 B
–3.75 A 10
3
–11.25 A 10
3
B
–3.75 A 103 B
–11.25 A 10
18 A 10
0
3
3
B
B
B
5.0625 A 103 B
1.5
5.0625 A 103 B
1.5
5.0625 A 103 B
1.5
5.0625 A 103 B
1.5
24.4375 A 103 B
2.5
2.5
24.4375 A 103 B
2
0
2
0
2.5
0
2.5
17.578125 A 10
2.5
17.578125 A 10
2.5
4
0
3
3
B
B
0
©102.28125 A 103 B
Then
1#¢ = ©
nNL
AE
1N # (¢ G)v =
1.5 m
1.5 m
6 kN
nNL(N 2 # m)
L(m)
B
102.28125 A 103 B
0.15 A 10 - 3 B C 200 A 109 B D
(¢ G)v = 3.409 A 10 - 3 B m = 3.41 mm T
Ans.
1228
C
1.5 m
12 kN
D
1.5 m
6 kN
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14–87. Determine the displacement at point C. EI is
constant.
P
P
A
B
a
1 # ¢C =
mM
dx
L0 EI
a
1
1
a x1 b(Px1)dx1 +
bc
EI L0 2
L0
a>2
1
(a + x2)(Pa)dx2 d
2
23Pa3
24EI
Ans.
*14–88. The beam is made of southern pine for which
Ep = 13 GPa. Determine the displacement at A.
1 # ¢A =
15 kN
4 kN/m
A
L
mM
L0 EI
B
1.5 m
1.5
¢A =
=
a
L
¢C = 2 a
=
a–
2
C
a–
2
C
3m
3
1
c
(x1)(15x1)dx1 +
(0.5x2)(2x22 + 1.5x2)dx2 d
EI L0
L0
43.875(103)
43.875 kN # m3
= 0.0579 m = 57.9 mm
=
1
9
EI
)(0.12)(0.18)3
13(10 )(12
1229
180 mm
Ans.
120 mm
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•14–89. Determine the displacement at C of the A-36
steel beam. I = 7011062 mm4.
2 kN/m
Real Moment Function M(x): As shown on figure(a).
C
B
A
Virtual Moment Functions m(x): As shown on figure(b).
10 m
5m
Virtual Work Equation: For the displacement at point C.
1#¢ =
1 kN # ¢ C =
¢C =
=
L
mM
dx
L0 EI
1
EI L0
10 m
0.500x1 (2.50x1)dx1 +
1
EI L0
5m
x2 A x22 B dx2
572.92 kN # m3
EI
572.92(1000)
200(109)[70(10 - 6)]
= 0.04092 m = 40.9 mm T
Ans.
14–90. Determine the slope at A of the A-36 steel beam.
I = 7011062 mm4.
2 kN/m
C
Real Moment Function M(x): As shown on figure(a).
B
A
Virtual Moment Functions mu (x): As shown on figure(b).
10 m
Virtual Work Equation: For the slope at point A.
1#u =
1 kN # m # uA =
uA =
=
L
muM
dx
L0 EI
1
EI L0
10 m
(1 - 0.100x1)(2.50x1) dx1 +
1
EI L0
5m
0 A 1.00x22 B dx2
41.667 kN # m2
EI
41.667(1000)
200(109)[70(10 - 6)]
= 0.00298 rad
Ans.
1230
5m
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14–91. Determine the slope at B of the A-36 steel beam.
I = 7011062 mm4.
2 kN/m
Real Moment Function M(x): As shown on figure(a).
C
B
A
Virtual Moment Functions mU (x): As shown on figure(b).
10 m
5m
Virtual Work Equation: For the slope at point B.
L
1#u =
1 kN # m # uB =
uB =
=
muM
dx
L0 EI
1
EI L0
10 m
0.100x1(2.50x1) dx1 +
1
EI L0
0 A 1.00x22 B dx2
5m
83.333 kN # m2
EI
83.333(1000)
200(109)[70(10 - 6)]
= 0.00595 rad
Ans.
*14–92. Determine the displacement at B of the 1.5-indiameter A-36 steel shaft.
2 ft
2 ft
A
3 ft
D
1 # ¢B =
B
L
mM
dx
L0 EI
140 lb
2
¢B
1.5 ft
140 lb
C
2
1
=
c
(0.5294x1)(327.06x1)dx1 +
0.5294(2 + x2)(654.12 + 47.06x2)dx2
EI L0
L0
+
=
L0
1.5
(0.4706x3)(592.94x3)dx3 +
L0
3
0.4706(x4 + 1.5)(889.41 - 47.06x4)dx4 d
6437.67(123)
6437.67 lb # ft3
= 1.54 in.
=
EI
29(106) p4 (0.75)4
320 lb 320 lb
Ans.
1231
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Page 1232
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Determine the slope of the 1.5-in-diameter A-36
steel shaft at the bearing support A.
•14–93.
1 # uA =
L
muM
dx
L0 EI
1
(1 - 0.1176x1)(327.06x1)dx1 +
B
EI L0
L0
+
=
2 ft
A
2
uA =
2 ft
L0
3 ft
D
1.5
(0.1176x3)(592.94x3)dx3
5
140 lb
0.1176(x4 + 1.5)(889.41 - 47.06x4)dx4 R
2387.53(122)
2387.53 lb # ft2
=
= 0.0477 rad = 2.73°
EI
29(106) A p4 B (0.754)
1.5 ft
B
140 lb
C
Ans.
320 lb 320 lb
14–94. The beam is made of Douglas fir. Determine the
slope at C.
8 kN
Virtual Work Equation: For the slope at point C.
1#u =
muM
dx
L0 EI
1 kN # m # uC = 0 +
1
EI L0
+
uC =
A
L
B
1.5 m
1.5 m
1.5 m
1.5 m
1
EI L0
(0.3333x2)(4.00x2) dx2
180 mm
1.5 m
(1 - 0.3333x3)(4.00x3)dx3
120 mm
4.50 kN # m3
EI
= -
C
4.50(1000)
1
(0.12)(0.183) D
13.1(10 ) C 12
9
= 5.89 A 10 - 3 B rad
Ans.
1232
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14–95. The beam is made of oak, for which Eo = 11 GPa.
Determine the slope and displacement at A.
200 mm
400 mm
4 kN/m
A
B
3m
Virtual Work Equation: For the displacement at point A,
1#¢ =
1 kN # ¢ A =
+
¢A =
=
L0
L
mM
dx
EI
1
EI L0
1
EI L0
3m
3m
2
x1 a x31 bdx1
9
(x2 + 3) A 2.00x22 + 6.00x2 + 6.00 B dx2
321.3 kN # m3
EI
321.3(103)
1
(0.2)(0.43) D
11(109) C 12
= 0.02738 m = 27.4 mm T
Ans.
For the slope at A.
L
1#u =
1 kN # m # uA =
muM
dx
L0 EI
1
EI L0
+
uA =
=
L0
3m
3m
2
1.00a x31 b dx1
9
1.00 A 2.00x22 + 6.00x2 + 6.00 B dx2
67.5 kN # m2
EI
67.5(1000)
1
(0.2)(0.43) D
11(109) C 12
= 5.75 A 10 - 3 B rad
Ans.
1233
3m
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*14–96. Determine the displacement at point C. EI is
constant.
P
A
C
B
a
1 # ¢C =
L
mM
dx
L0 EI
a
a
¢C =
=
•14–97.
a
1
(x2)(Px2)dx2 d
(x1)(Px1)dx1 +
c
EI L0
L0
2Pa3
3EI
Ans.
Determine the slope at point C. EI is constant.
P
A
C
B
a
1 # uC =
uC =
=
L0
L
L0
a
muMdx
EI
A a1 B Px1 dx1
x
EI
a
+
(1)Px2dx2
EI
L0
Pa2
Pa2
5Pa2
+
=
3EI
2EI
6EI
Ans.
1234
a
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14–98.
1 # uA =
uA
Determine the slope at point A. EI is constant.
P
A
L
muM
dx
L0 EI
C
B
a
a
a
x1
1
Pa2
a1 =
b (Px1)dx1 +
(0)(Px2)dx2 R =
B
a
EI L0
6EI
L0
14–99. Determine the slope at point A of the simply
supported Douglas fir beam.
a
Ans.
3 kN
0.6 kN⭈m
a
A
B
C
Real Moment Function M. As indicated in Fig. a.
1.5 m
a
0.5 m
Virtual Moment Functions m. As indicated in Fig. b.
75 mm
Virtual Work Equation.
1#u =
150 mm
L
mu M
dx
EI
L0
1kN # m # uA =
Section a – a
1
B
EI L0
2m
+
uA =
=
=
1
B
EI L0
2m
(1 - 0.3333x1)(0.8x1 + 0.6)dx1
L0
1m
(0.3333x2)(2.2x2)dx2 R
A -0.2667x1 2 + 0.6x1 + 0.6 B dx1 +
1.9333 kN # m2
EI
L0
1m
0.7333x2 2dx2 R
1.9333 A 103 B
1
13.1 A 109 B c (0.075) A 0.153 B d
2
= 0.00700 rad
Ans.
1235
1m
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14–99. Continued
1236
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*14–100. Determine the displacement at C of the simply
supported Douglas fir beam.
3 kN
0.6 kN⭈m
Real Moment Function M. As indicated in Fig. a.
a
A
B
C
Virtual Moment Functions m. As indicated in Fig. b.
1.5 m
Virtual Work Equation.
1#¢ =
L0
L
1 kN # ¢ C =
¢C =
1.5 m
=
1.5 m
(0.5x1)(0.8x1 + 0.6)dx1 +
L0
1.775kN # m3
EI
L0
1m
Section a – a
(0.5x2)(2.2x2)dx2
0.5 m
(0.5x3 + 0.5)(2.2 - 0.8x3)dx3 R
A 0.4x1 2 + 0.3x1 B dx1 +
+
=
150 mm
1
B
EI L0
1
B
EI L0
L0
0.5 m
L0
1m
1.1x2 2 dx2
A -0.4x3 2 + 0.7x3 + 1.1 B dx3 R
1.775 A 103 B
13.1 A 109 B c
0.5 m
75 mm
mM
dx
EI
+
a
1
(0.075) A 0.153 B d
12
= 6.424 A 10 - 3 B m = 6.42 mm T
Ans.
1237
1m