Chapter
Umer MalikRelated papers
A Strain Gauge Based System for Measuring Dynamic Loading on a Rotating Shaft
INTERNATIONAL JOURNAL OF MECHANICS, 2011
In a mechanical system, the acting mechanical power is the most important quantity of rotating shaft of machines. There are many methods to measure it such as measuring the torque directly on the rotating shaft and measuring the rotational speed. Also there are many widely used measuring methods and more or less standardized instruments for measuring the rotational speed. A digital hand tachometer was chosen for measuring speed. The torque measurement is more complicate than the speed measurement. It needs a special solution in every occasion. It must be built onto the machine's shaft. This is because the high accuracy, a relatively simple application and the high dynamical behavior, the strain gauge sensor will be chosen for measuring the torque on the rotating shaft. During the design, the shaft was adapted for application of "V shape" strain gauge, to the shaft's end a HBM made slip-ring assembly was connected the rotating shaft with the standing cable and the Spider8 measurement electronics. The HBM CATMAN-Express software was used during the calibration and the tests. The calibration was carried out with 0.5 m long lever and dead weights in 0.5 kg steps up to 4.5 kg.
White Paper DC Motor Calculations Calculating Mechanical Power Requirements
In dc motors, electrical power (Pel) is converted to mechanical power (Pmech). In addition to frictional losses, there are power losses in Joules/sec (Iron losses in coreless dc motors are negligible). Pel = Pmech + Pj loss Physically, power is defined as the rate of doing work. For linear motion, power is the product of force multiplied by the distance per unit time. In the case of rotational motion, the analogous calculation for power is the product of torque multiplied by the rotational distance per unit time. Prot = M x ω Where: Prot = rotational mechanical power M = torque ω = angular velocity The most commonly used unit for angular velocity is rev/min (RPM). In calculating rotational power, it is necessary to convert the velocity to units of rad/sec. This is accomplished by simply multiplying the velocity in RPM by the constant (2 x ∏) /60: ωrad = ωrpm x (2∏)/60
Tracer le trac, Esquisse anthropologique d'une passion
Christine Détrez, Kevin Diter, Sylvie Octobre (ed.) Culture & émotions. La dimension affective des goûts, Paris, Presses de SciencesPo, 2024
Le trac est révélateur d'un rapport possible entre une émotion et la culture artistique. La question est de déterminer comment se forme culturellement une émotion ? L'organisation des rapports entre un orateur et son public engendre une tension cérémonielle. De ce fait, le trac est un signal personnel du pouvoir rhétorique du public. En examinant ce rapport de pouvoir, la méthode d'analyse a reconstruit le circuit symbolique de transformations culturelles d'une passion primaire, la peur. Le monde du théâtre s'approprie l'argot du trac pour en faire une passion spécifique aux comédiens avant de se communiquer à l'ensemble des mondes de l'art sous la forme d'un symptôme d'une peur professionnelle pathologique : la crainte du jugement critique au principe des réputations. Pour les professionnelles de la santé, le symptôme est en quête d'une catégorie nosographique : phobie, obsession ou timidité. C'est la thérapeutique qui forge le jugement clinique à l'égard du trac au point où le symptôme puisse frapper, peu avant la seconde guerre mondiale, toutes les catégories de personnes ne pouvant échapper à l'étiquette de la mise en scène de leur vie quotidienne. Dès lors, le remède est dans le mal. La réaction sociale à la « mise en scène » implique des techniques d'apprivoisement de son public quel que soit le seuil personnel de la tension cérémonielle, de la plus petite inhibition lors d'une situation circonscrite à « l'anxiété sociale » où le degré de « phobie » indique le poids moral intolérable de l'épreuve publique de soi. Cette esquisse anthropologique permet de tracer la genèse et la transformation de l'organisation de la situation d'une personne qu'un public vient troubler. Mais il revient au travail de terrain de décrire les variations sociales et genrées pour conjurer ou non les réactions négatives à cette tension cérémonielle et d'analyser les procédés mis en oeuvre pour réaliser aujourd'hui l'idéal d'aisance publique.
Robert Mugerauer’s Legacy— “‘The gathering together of what already belongs together even while apart”: Knowing Robert Mugerauer”
University of Washington Symposium, 2023
This presentation was prepared for the 2023 Annual Symposium sponsored by the University of Washington’s Interdisciplinary PhD program in Urban Design and Planning; and PhD program in the Built Environment. The 2023 Symposium theme was “Space, Place, and Belonging,” in honor of the late Prof. Robert Mugerauer, who died in 2022. One Symposium aim was to “facilitate conversations particularly in phenomenology and qualitative research, in memory of Mugerauer’s dedication to these topics.” This presentation is part of a panel discussion that included Lynne Manzo, Edward Casey, and Jeff Malpas. The quotation in the presentation title is from Mugerauer's 1988 HEIDEGGER'S LANGUAGE AND THINKING (NY: Humanities Press), p. 216.
Relational moral philosophy needs relational moral psychology
Philosophical Psychology, 2024
Well written, tightly argued, provocative, and original, Metz's book is a mustread contribution. In addition to skillfully and judiciously bringing African moral philosophy into conversation with Western analytic philosophy, Metz has done the field a service by putting social and interpersonal relationships at the heart of his theory-and encouraging others to do the same. Going forward, especially given his explicit desire to accommodate or explain common moral intuitions, it might be that more direct engagement with the empirical literatures in relationship science and experimental moral psychology would further strengthen his theory.
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10–1. Prove that the sum of the normal strains in
perpendicular directions is constant.
ex¿ =
ey¿ =
ex + ey
2
ex + ey
2
+
-
ex - ey
2
ex - ey
2
cos 2u +
cos 2u -
gxy
2
gxy
2
sin 2u
(1)
sin 2u
(2)
Adding Eq. (1) and Eq. (2) yields:
ex¿ + ey¿ = ex + ey = constant
QED
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10–2. The state of strain at the point has components
of Px = 200 110-62, Py = -300 110-62, and gxy = 400(10-62.
Use the strain-transformation equations to determine the
equivalent in-plane strains on an element oriented at an
angle of 30° counterclockwise from the original position.
Sketch the deformed element due to these strains within the
x–y plane.
y
x
In accordance to the established sign convention,
ey = -300(10 - 6)
ex = 200(10 - 6),
ex¿ =
ex + ey
2
= c
+
ex - ey
2
cos 2u +
gxy
2
gxy = 400(10 - 6)
u = 30°
sin 2u
200 - (-300)
200 + (-300)
400
+
cos 60° +
sin 60° d(10 - 6)
2
2
2
= 248 (10 - 6)
gx¿y¿
2
= -a
Ans.
ex - ey
2
b sin 2u +
gxy
2
cos 2u
gx¿y¿ = e - C 200 - ( -300) D sin 60° + 400 cos 60° f(10 - 6)
= -233(10 - 6)
ey¿ =
ex + ey
= c
2
-
Ans.
ex - ey
2
cos 2u -
gxy
2
sin 2u
200 - ( -300)
200 + ( -300)
400
cos 60° sin 60° d(10 - 6)
2
2
2
= -348(10 - 6)
Ans.
The deformed element of this equivalent state of strain is shown in Fig. a
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10–3. A strain gauge is mounted on the 1-in.-diameter
A-36 steel shaft in the manner shown. When the shaft is
rotating with an angular velocity of v = 1760 rev>min, the
reading on the strain gauge is P = 800110-62. Determine
the power output of the motor. Assume the shaft is only
subjected to a torque.
v = (1760 rev>min)a
60⬚
2p rad
1 min
ba
b = 184.307 rad>s
60 sec
1 rev
ex = ey = 0
ex¿ =
ex + ey
2
+
ex - ey
2
800(10 - 6) = 0 + 0 +
cos 2u +
gxy
2
gxy
2
sin 2u
sin 120°
gxy = 1.848(10 - 3) rad
t = G gxy = 11(103)(1.848)(10 - 3) = 20.323 ksi
t =
Tc
;
J
20.323 =
T(0.5)
p
2
(0.5)4
;
T = 3.99 kip # in = 332.5 lb # ft
P = Tv = 0.332.5 (184.307) = 61.3 kips # ft>s = 111 hp
Ans.
740
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*10–4. The state of strain at a point on a wrench
has components Px = 120110-62, Py = -180110-62, gxy =
150110-62. Use the strain-transformation equations to
determine (a) the in-plane principal strains and (b) the
maximum in-plane shear strain and average normal strain.
In each case specify the orientation of the element and show
how the strains deform the element within the x–y plane.
ex = 120(10 - 6)
e1, 2 =
a)
ey = -180(10 - 6)
gxy = 150(10 - 6)
ex + ey
Ex - Ey 2
gxy 2
;
a
b + a
b
2
A
2
2
120 + (-180)
120 - ( -180) 2
150 2
-6
;
a
b + a
b d 10
2
A
2
2
e1 = 138(10 - 6);
e2 = -198(10 - 6)
= c
Ans.
Orientation of e1 and e2
gxy
150
tan 2up =
=
= 0.5
ex - ey
[120 - (-180)]
up = 13.28° and -76.72°
Use Eq. 10.5 to determine the direction of e1 and e2
ex¿ =
ex + ey
+
2
ex - ey
2
cos 2u +
gxy
2
sin 2u
u = up = 13.28°
ex¿ = c
120 + (-180)
120 - (-180)
150
+
cos (26.56°) +
sin 26.56° d 10 - 6
2
2
2
= 138 (10 - 6) = e1
Therefore up1 = 13.3° ;
gmax
b)
in-plane
=
2
in-plane
ex + ey
2
A
ex - ey
2
b + a
gxy
b
Ans.
2
2
2
150 2
120 - (-180) 2
-6
-6
= 2c a
b + a
b d10 = 335 (10 )
A
2
2
gmax
eavg =
a
up2 = -76.7°
= c
120 + (-180)
d 10 - 6 = -30.0(10 - 6)
2
Ans.
Ans.
Orientation of gmax
tan 2us =
-(ex - ey)
gxy
=
-[120 - ( -180)]
= -2.0
150
us = -31.7° and 58.3°
Ans.
gmax
Use Eq. 10–6 to determine the sign of in-plane
gx¿y¿
ex - ey
gxy
= sin 2u +
cos 2u
2
2
2
u = us = -31.7°
gx¿y¿ = 2c -
120 - (-180)
150
sin (-63.4°) +
cos (-63.4°) d10 - 6 = 335(10 - 6)
2
2
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10–5. The state of strain at the point on the arm
has components Px = 250110-62, Py = -450110-62, gxy =
-825110-62. Use the strain-transformation equations to
determine (a) the in-plane principal strains and (b) the
maximum in-plane shear strain and average normal strain.
In each case specify the orientation of the element and show
how the strains deform the element within the x–y plane.
ex = 250(10 - 6)
ey = -450(10 - 6)
y
gxy = -825(10 - 6)
x
a)
ex + ey
e1, 2 =
;
2
= c
A
ex - ey
a
2
2
b + a
gxy
2
b
2
250 - 450
250 - ( -450) 2
-825 2
-6
;
a
b + a
b d(10 )
2
A
2
2
e1 = 441(10 - 6)
Ans.
e2 = -641(10 - 6)
Ans.
Orientation of e1 and e2 :
gxy
tan 2up =
ex - ey
up = -24.84°
-825
250 - ( -450)
=
up = 65.16°
and
Use Eq. 10–5 to determine the direction of e1 and e2:
ex¿ =
ex + ey
+
2
ex - ey
2
cos 2u +
gxy
2
sin 2u
u = up = -24.84°
ex¿ = c
250 - (-450)
250 - 450
-825
+
cos (-49.69°) +
sin (-49.69°) d(10 - 6) = 441(10 - 6)
2
2
2
Therefore, up1 = -24.8°
Ans.
up2 = 65.2°
Ans.
b)
g
max
in-plane
2
g
max
in-plane
eavg =
=
A
= 2c
a
ex - ey
2
gxy
2
b
2
250 - (-450) 2
-825 2
-6
-3
b + a
b d(10 ) = 1.08(10 )
A
2
2
a
ex + ey
2
2
b + a
= a
250 - 450
b(10 - 6) = -100(10 - 6)
2
Ans.
Ans.
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10–6. The state of strain at the point has components of
Px = -100110-62, Py = 400110-62, and gxy = -300110-62.
Use the strain-transformation equations to determine the
equivalent in-plane strains on an element oriented at an
angle of 60° counterclockwise from the original position.
Sketch the deformed element due to these strains within
the x–y plane.
y
x
In accordance to the established sign convention,
ey = 400(10 - 6)
ex = -100(10 - 6)
ex¿ =
ex + ey
2
= c
+
ex - ey
2
gxy
cos 2u +
2
gxy = -300(10 - 6)
u = 60°
sin 2u
-100 - 400
-300
-100 + 400
+
cos 120° +
sin 120° d(10 - 6)
2
2
2
= 145(10 - 6)
gx¿y¿
2
= -a
Ans.
ex - ey
2
b sin 2u +
gxy
2
cos 2u
gx¿y¿ = c -( -100 - 400) sin 120° + (-300) cos 120° d(10 - 6)
= 583(10 - 6)
ey¿ =
ex + ey
= c
2
-
Ans.
ex - ey
2
cos 2u -
gxy
2
sin 2u
-100 - 400
-300
-100 + 400
cos 120° sin 120° d(10 - 6)
2
2
2
= 155 (10 - 6)
Ans.
The deformed element of this equivalent state of strain is shown in Fig. a
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10–7. The state of strain at the point has components of
Px = 100110-62, Py = 300110-62, and gxy = -150110-62.
Use the strain-transformation equations to determine the
equivalent in-plane strains on an element oriented u = 30°
clockwise. Sketch the deformed element due to these
strains within the x–y plane.
y
x
In accordance to the established sign convention,
ex = 100(10 - 6)
ex¿ =
ex + ey
2
= c
+
ey = 300(10 - 6)
ex - ey
2
cos 2u +
gxy = -150(10 - 6)
gxy
2
u = -30°
sin 2u
100 - 300
-150
100 + 300
+
cos (-60°) +
sin ( -60°) d (10 - 6)
2
2
2
= 215(10 - 6)
gx¿y¿
2
= -a
Ans.
ex - ey
2
b sin 2u +
gxy
2
cos 2u
gx¿y¿ = c -(100 - 300) sin ( -60°) + ( -150) cos ( -60°) d(10 - 6)
= -248 (10 - 6)
ey¿ =
ex + ey
= c
2
-
Ans.
ex - ey
2
cos 2u -
gxy
2
sin 2u
100 - 300
-150
100 + 300
cos (-60°) sin (-60°) d (10 - 6)
2
2
2
= 185(10 - 6)
Ans.
The deformed element of this equivalent state of strain is shown in Fig. a
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*10–8. The state of strain at the point on the bracket
has components Px = -200110-62, Py = -650110-62, gxy ⫽
-175110-62. Use the strain-transformation equations to
determine the equivalent in-plane strains on an element
oriented at an angle of u = 20° counterclockwise from the
original position. Sketch the deformed element due to these
strains within the x–y plane.
ey = -650(10 - 6)
ex = -200(10 - 6)
ex¿ =
ex + ey
2
= c
+
ex - ey
2
cos 2u +
gxy
2
y
x
gxy = -175(10 - 6)
u = 20°
sin 2u
(-200) - (-650)
(-175)
-200 + (-650)
+
cos (40°) +
sin (40°) d(10 - 6)
2
2
2
= -309(10 - 6)
ey¿ =
ex + ey
2
= c
-
Ans.
ex - ey
2
cos 2u -
gxy
2
sin 2u
-200 - ( -650)
(-175)
-200 + (-650)
cos (40°) sin (40°) d(10 - 6)
2
2
2
= -541(10 - 6)
gx¿y¿
2
= -
ex - ey
2
Ans.
sin 2u +
gxy
2
cos 2u
gx¿y¿ = [-(-200 - (-650)) sin (40°) + (-175) cos (40°)](10 - 6)
= -423(10 - 6)
Ans.
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10–9. The state of strain at the point has components of
Px = 180110-62, Py = -120110-62, and gxy = -100110-62.
Use the strain-transformation equations to determine (a)
the in-plane principal strains and (b) the maximum in-plane
shear strain and average normal strain. In each case specify
the orientation of the element and show how the strains
deform the element within the x–y plane.
y
x
a)
In
accordance
to
the
established
sign
convention,
ex = 180(10 - 6),
ey = -120(10 - 6) and gxy = -100(10 - 6).
ex + ey
e1, 2 =
= b
;
2
a
A
ex - ey
2
2
b + a
gxy
2
b
2
180 + (-120)
180 - ( -120) 2
-100 2
-6
;
c
d + a
b r (10 )
2
A
2
2
= A 30 ; 158.11 B (10 - 6)
e2 = -128(10 - 6)
e1 = 188(10 - 6)
tan 2uP =
gxy
ex - ey
Ans.
-100(10 - 6)
C 180 - (-120) D (10 - 6)
=
uP = -9.217°
and
= -0.3333
80.78°
Substitute u = -9.217°,
ex + ey
ex¿ =
2
= c
+
ex - ey
2
cos 2u +
gxy
2
sin 2u
180 + (-120)
180 - (-120)
-100
+
cos (-18.43°) +
sin (-18.43) d(10 - 6)
2
2
2
= 188(10 - 6) = e1
Thus,
(uP)1 = -9.22°
(uP)2 = 80.8°
Ans.
The deformed element is shown in Fig (a).
gmax
ex - ey 2
gxy 2
in-plane
=
b)
a
b + a
b
2
A
2
2
gmax
in-plane
tan 2us = - a
= b2
180 - (-120) 2
-100 2
-6
-6
d + a
b r (10 ) = 316 A 10 B
A
2
2
ex - ey
gxy
c
b = -c
C 180 - (-120) D (10 - 6)
us = 35.78° = 35.8° and
-100(10 - 6)
Ans.
s = 3
-54.22° = -54.2°
Ans.
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10–9.
Continued
gmax
The algebraic sign for in-plane
when u = 35.78°.
gx¿y¿
ex - ey
gxy
= -a
b sin 2u +
cos 2u
2
2
2
gx¿y¿ = e - C 180 - ( -120) D sin 71.56° + (-100) cos 71.56° f(10 - 6)
eavg
= -316(10 - 6)
ex + ey
180 + (-120)
= c
d(10 - 6) = 30(10 - 6)
=
2
2
Ans.
The deformed element for the state of maximum In-plane shear strain is shown is
shown in Fig. b
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10–10. The state of strain at the point on the bracket
has components Px = 400110-62, Py = -250110-62, gxy ⫽
310110-62. Use the strain-transformation equations to
determine the equivalent in-plane strains on an element
oriented at an angle of u = 30° clockwise from the original
position. Sketch the deformed element due to these strains
within the x–y plane.
ex = 400(10 - 6)
ex¿ =
ex + ey
2
= c
+
ey = -250(10 - 6)
ex - ey
2
cos 2u +
gxy
2
gxy = 310(10 - 6)
y
x
u = -30°
sin 2u
400 - (-250)
400 + (-250)
310
+
cos (-60°) + a
b sin (-60°) d(10 - 6)
2
2
2
= 103(10 - 6)
ey¿ =
ex + ey
2
= c
-
Ans.
ex - ey
2
cos 2u -
gxy
2
sin 2u
400 - (-250)
400 + (-250)
310
cos (60°) sin (-60°) d(10 - 6)
2
2
2
= 46.7(10 - 6)
gx¿y¿
2
= -
ex - ey
2
Ans.
sin 2u +
gxy
2
cos 2u
gx¿y¿ = [-(400 - (-250)) sin (-60°) + 310 cos ( -60°)](10 - 6) = 718(10 - 6)
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10–11. The state of strain at the point has components of
Px = -100110-62, Py = -200110-62, and gxy = 100110-62.
Use the strain-transformation equations to determine (a)
the in-plane principal strains and (b) the maximum in-plane
shear strain and average normal strain. In each case specify
the orientation of the element and show how the strains
deform the element within the x–y plane.
In accordance to the established
ey = -200(10 - 6) and gxy = 100(10 - 6).
ex + ey
e1, 2 =
;
2
= b
A
a
ex - ey
2
2
b + a
gxy
2
b
sign
y
x
convention,
ex = -100(10 - 6),
2
-100 + (-200)
100 2
-100 - (-200) 2
-6
;
c
d + a
b r (10 )
2
A
2
2
A -150 ; 70.71 B (10 - 6)
=
e1 = -79.3(10 - 6)
tan 2uP =
gxy
e2 = -221(10 - 6)
100(10 - 6)
C -100 - (-200) D (10 - 6)
=
ex - ey
uP = 22.5°
Ans.
= 1
-67.5°
and
Substitute u = 22.5,
ex + ey
ex¿ =
+
ex - ey
cos 2u +
gxy
sin 2u
2
2
2
-100 + (-200)
-100 - (-200)
100
= c
+
cos 45° +
sin 45° d(10 - 6)
2
2
2
= -79.3(10 - 6) = e1
Thus,
(uP)1 = 22.5°
(uP)2 = -67.5°
Ans.
The deformed element of the state of principal strain is shown in Fig. a
gmax
ex - ey 2
gxy 2
in-plane
=
a
b + a
b
2
A
2
2
gmax
in-plane
= b2
tan 2us = - a
-100 - (-200) 2
100 2
-6
-6
d + a
b r (10 ) = 141(10 )
A
2
2
c
ex - ey
gxy
b = -c
us = -22.5°
The algebraic sign for
gx¿y¿
2
= -a
ex - ey
2
C -100 - (-200) D (10 - 6)
100(10 - 6)
and
gmax
in-plane
b sin 2u +
Ans.
s = -1
67.5°
Ans.
when u = -22.5°.
gxy
2
cos 2u
gx¿y¿ = - C -100 - (-200) D sin ( -45°) + 100 cos (-45°)
eavg
= 141(10 - 6)
ex + ey
-100 + ( -200)
= c
d(10 - 6) = -150(10 - 6)
=
2
2
Ans.
The deformed element for the state of maximum In-plane shear strain is shown in
Fig. b.
749
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10–11. Continued
*10–12. The state of plane strain on an element is given by
Px = 500110-62, Py = 300110-62, and gxy = -200110-62.
Determine the equivalent state of strain on an element at
the same point oriented 45° clockwise with respect to the
original element.
y
Pydy
dy gxy
2
Strain Transformation Equations:
ex = 500 A 10 - 6 B
ey = 300 A 10 - 6 B
gxy = -200 A 10 - 6 B
u = -45°
We obtain
ex¿ =
ex + ey
2
= c
+
ex - ey
2
cos 2u +
gxy
2
sin 2u
500 - 300
-200
500 + 300
+
cos (-90°) + a
b sin (-90°) d A 10 - 6 B
2
2
2
= 500 A 10 - 6 B
gx¿y¿
2
= -a
Ans.
ex - ey
2
b sin 2u +
gxy
2
cos 2u
gx¿y¿ = [-(500 - 300) sin ( -90°) + (-200) cos ( -90°)] A 10 - 6 B
= 200 A 10 - 6 B
ey¿ =
ex + ey
= c
2
-
Ans.
ex - ey
2
cos 2u -
gxy
2
sin 2u
500 + 300
500 - 300
-200
cos (-90°) - a
b sin (-90°) d A 10 - 6 B
2
2
2
= 300 A 10 - 6 B
Ans.
The deformed element for this state of strain is shown in Fig. a.
750
x
gxy
2
dx
Pxdx
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10–13. The state of plane strain on an element is
Px = -300110-62, Py = 0, and gxy = 150110-62. Determine
the equivalent state of strain which represents (a) the
principal strains, and (b) the maximum in-plane shear strain
and the associated average normal strain. Specify the
orientation of the corresponding elements for these states
of strain with respect to the original element.
y
gxy
dy 2
x
In-Plane Principal Strains: ex = -300 A 10 - 6 B , ey = 0, and gxy = 150 A 10 - 6 B . We
obtain
ex + ey
e1, 2 =
2
= C
;
C
¢
ex - ey
2
≤ + ¢
2
gxy
2
≤
2
-300 + 0
-300 - 0 2
150 2
;
¢
≤ + ¢
≤ S A 10 - 6 B
2
C
2
2
= ( -150 ; 167.71) A 10 - 6 B
e1 = 17.7 A 10 - 6 B
e2 = -318 A 10 - 6 B
Ans.
Orientation of Principal Strain:
tan 2up =
gxy
ex - ey
=
150 A 10 - 6 B
(-300 - 0) A 10 - 6 B
= -0.5
uP = -13.28° and 76.72°
Substituting u = -13.28° into Eq. 9-1,
ex¿ =
ex + ey
= c
+
2
ex - ey
2
cos 2u +
gxy
2
sin 2u
-300 + 0
-300 - 0
150
+
cos (-26.57°) +
sin (-26.57°) d A 10 - 6 B
2
2
2
= -318 A 10 - 6 B = e2
Thus,
A uP B 1 = 76.7° and A uP B 2 = -13.3°
Ans.
The deformed element of this state of strain is shown in Fig. a.
Maximum In-Plane Shear Strain:
gmax
ex - ey 2
gxy 2
in-plane
=
¢
≤ + ¢ ≤
2
C
2
2
gmax
in-plane
= B2
-300 - 0 2
150 2
-6
-6
b + a
b R A 10 B = 335 A 10 B
A
2
2
a
Ans.
Orientation of the Maximum In-Plane Shear Strain:
tan 2us = - ¢
ex - ey
gxy
≤ = -C
(-300 - 0) A 10 - 6 B
150 A 10 - 6 B
S = 2
us = 31.7° and 122°
Ans.
751
gxy
2
dx
Pxdx
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10–13. Continued
The algebraic sign for
gx¿y¿
2
= -¢
ex - ey
2
gmax
in-plane
≤ sin 2u +
when u = us = 31.7° can be obtained using
gxy
2
cos 2u
gx¿y¿ = [-(-300 - 0) sin 63.43° + 150 cos 63.43°] A 10 - 6 B
= 335 A 10 - 6 B
Average Normal Strain:
eavg =
ex + ey
2
= a
-300 + 0
b A 10 - 6 B = -150 A 10 - 6 B
2
Ans.
The deformed element for this state of strain is shown in Fig. b.
752
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10–14. The state of strain at the point on a boom of an
hydraulic engine crane has components of Px = 250110-62,
Py = 300110-62, and gxy = -180110-62. Use the straintransformation equations to determine (a) the in-plane
principal strains and (b) the maximum in-plane shear strain
and average normal strain. In each case, specify the
orientation of the element and show how the strains deform
the element within the x–y plane.
y
a)
In-Plane Principal Strain: Applying Eq. 10–9,
ex + ey
e1, 2 =
;
2
= B
a
A
ex - ey
2
2
b + a
gxy
2
b
2
250 - 300 2
-180 2
250 + 300
-6
;
a
b + a
b R A 10 B
2
A
2
2
= 275 ; 93.41
e1 = 368 A 10 - 6 B
e2 = 182 A 10 - 6 B
Ans.
Orientation of Principal Strain: Applying Eq. 10–8,
gxy
tan 2uP =
ex - ey
=
-180(10 - 6)
(250 - 300)(10 - 6)
uP = 37.24°
and
= 3.600
-52.76°
Use Eq. 10–5 to determine which principal strain deforms the element in the x¿
direction with u = 37.24°.
ex¿ =
ex + ey
= c
2
+
ex - ey
2
cos 2u +
gxy
2
sin 2u
250 + 300
250 - 300
-180
+
cos 74.48° +
sin 74.48° d A 10 - 6 B
2
2
2
= 182 A 10 - 6 B = e2
Hence,
uP1 = -52.8°
and
uP2 = 37.2°
Ans.
b)
Maximum In-Plane Shear Strain: Applying Eq. 10–11,
g max
ex - ey 2
gxy 2
in-plane
=
a
b + a
b
2
A
2
2
g
max
in-plane
= 2B
250 - 300 2
-180 2
-6
b + a
b R A 10 B
A
2
2
a
= 187 A 10 - 6 B
Ans.
753
x
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10–14. Continued
Orientation of the Maximum In-Plane Shear Strain: Applying Eq. 10–10,
tan 2us = -
ex - ey
gxy
us = -7.76°
and
The proper sign of
gx¿y¿
2
= -
= -
ex - ey
2
g
max
in-plane
250 - 300
= -0.2778
-180
82.2°
Ans.
can be determined by substituting u = -7.76° into Eq. 10–6.
sin 2u +
gxy
2
cos 2u
gx¿y¿ = {-[250 - 300] sin (-15.52°) + (-180) cos (-15.52°)} A 10 - 6 B
= -187 A 10 - 6 B
Normal Strain and Shear strain: In accordance with the sign convention,
ex = 250 A 10 - 6 B
ey = 300 A 10 - 6 B
gxy = -180 A 10 - 6 B
Average Normal Strain: Applying Eq. 10–12,
eavg =
ex + ey
2
= c
250 + 300
d A 10 - 6 B = 275 A 10 - 6 B
2
Ans.
754
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*10–16. The state of strain at a point on a support
has components of Px = 350110-62, Py = 400110-62,
gxy = -675110-62. Use the strain-transformation equations
to determine (a) the in-plane principal strains and (b) the
maximum in-plane shear strain and average normal strain.
In each case specify the orientation of the element and show
how the strains deform the element within the x–y plane.
a)
e1, 2 =
=
ex + ey
;
2
B
a
ex -ey
2
2
b + a
gxy
2
b
2
350 - 400 2
-675 2
350 + 400
;
a
b + a
b
2
A
2
2
e1 = 713(10 - 6)
Ans.
e2 = 36.6(10 - 6)
Ans.
tan 2uP =
gxy
ex - ey
=
-675
(350 - 400)
uP = 42.9°
Ans.
b)
(gx¿y¿)max
2
(gx¿y¿)max
2
=
=
A
a
ex - ey
2
2
b + a
gxy
2
b
2
350 - 400 2
-675 2
b + a
b
A
2
2
a
(gx¿y¿)max = 677(10 - 6)
eavg =
ex + ey
tan 2us =
2
=
350 + 400
= 375(10 - 6)
2
-(ex - ey)
gxy
Ans.
=
Ans.
350 - 400
675
us = -2.12°
Ans.
755
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•10–17.
Solve part (a) of Prob. 10–4 using Mohr’s circle.
ex = 120(10 - 6)
ey = -180(10 - 6)
gxy = 150(10 - 6)
A (120, 75)(10 - 6) C (-30, 0)(10 - 6)
R = C 2[120 - (-30)]2 + (75)2 D (10 - 6)
= 167.71 (10 - 6)
e1 = (-30 + 167.71)(10 - 6) = 138(10 - 6)
Ans.
e2 = (-30 - 167.71)(10 - 6) = -198(10 - 6)
Ans.
75
tan 2uP = a
b , uP = 13.3°
30 + 120
Ans.
756
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10–18.
Solve part (b) of Prob. 10–4 using Mohr’s circle.
ex = 120(10 - 6)
ey = -180(10 - 6)
gxy = 150(10 - 6)
A (120, 75)(10 - 6) C (-30, 0)(10 - 6)
R = C 2[120 - (-30)]2 + (75)2 D (10 - 6)
= 167.71 (10 - 6)
gxy
max
2 in-plane
gxy
= R = 167.7(10 - 6)
max
in-plane
= 335(10 - 6)
Ans.
eavg = -30 (10 - 6)
tan 2us =
120 + 30
75
Ans.
us = -31.7°
Ans.
757
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Solve Prob. 10–8 using Mohr’s circle.
10–19.
ex = -200(10 - 6)
ey = -650(10 - 6)
gxy = -175(10 - 6)
gxy
2
= -87.5(10 - 6)
u = 20°, 2u = 40°
A(-200, -87.5)(10 - 6)
C(-425, 0)(10 - 6)
R = [2(-200 - (-425))2 + 87.52 ](10 - 6) = 241.41(10 - 6)
tan a =
87.5
;
-200 - (-425)
a = 21.25°
f = 40 + 21.25 = 61.25°
ex¿ = (-425 + 241.41 cos 61.25°)(10 - 6) = -309(10 - 6)
Ans.
ey¿ = ( -425 - 241.41 cos 61.25°)(10 - 6) = -541(10 - 6)
Ans.
-gx¿y¿
2
= 241.41(10 - 6) sin 61.25°
gx¿y¿ = -423(10 - 6)
Ans.
758
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*10–20.
Solve Prob. 10–10 using Mohr’s circle.
ex = 400(10 - 6)
A(400, 155)(10 - 6)
ey = -250(10 - 6)
gxy = 310(10 - 6)
gxy
2
= 155(10 - 6)
C(75, 0)(10 - 6)
R = [2(400 - 75)2 + 1552 ](10 - 6) = 360.1(10 - 6)
tan a =
155
;
400 - 75
a = 25.50°
f = 60 + 25.50 = 85.5°
ex¿ = (75 + 360.1 cos 85.5°)(10 - 6) = 103(10 - 6)
Ans.
ey¿ = (75 - 360.1 cos 85.5°)(10 - 6) = 46.7(10 - 6)
Ans.
gx¿y¿
2
= (360.1 sin 85.5°)(10 - 6)
gx¿y¿ = 718(10 - 6)
Ans.
759
u = 30°
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•10–21.
Solve Prob. 10–14 using Mohr’s circle.
Construction of the Circle: In accordance with the sign convention, ex = 250 A 10 - 6 B ,
gxy
ey = 300 A 10 - 6 B , and
= -90 A 10 - 6 B . Hence,
2
eavg =
ex + ey
2
= a
250 + 300
b A 10 - 6 B = 275 A 10 - 6 B
2
Ans.
The coordinates for reference points A and C are
A(250, -90) A 10 - 6 B
C(275, 0) A 10 - 6 B
The radius of the circle is
R = a 2(275 - 250)2 + 902 b A 10 - 6 B = 93.408
In-Plane Principal Strain: The coordinates of points B and D represent e1 and e2,
respectively.
e1 = (275 + 93.408) A 10 - 6 B = 368 A 10 - 6 B
Ans.
e2 = (275 - 93.408) A 10 - 6 B = 182 A 10 - 6 B
Ans.
Orientation of Principal Strain: From the circle,
tan 2uP2 =
90
= 3.600
275 - 250
2uP2 = 74.48°
2uP1 = 180° - 2uP2
uP1 =
180° - 74.78°
= 52.8° (Clockwise)
2
Ans.
Maximum In-Plane Shear Strain: Represented by the coordinates of point E on
the circle.
g max
in-plane
2
g
= -R = -93.408 A 10 - 6 B
max
in-plane
= -187 A 10 - 6 B
Ans.
Orientation of the Maximum In-Plane Shear Strain: From the circle,
tan 2us =
275 - 250
= 0.2778
90
us = 7.76° (Clockwise)
Ans.
760
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10–22. The strain at point A on the bracket has
components Px = 300110-62, Py = 550110-62, gxy =
-650110-62. Determine (a) the principal strains at A in the
x– y plane, (b) the maximum shear strain in the x–y plane,
and (c) the absolute maximum shear strain.
ex = 300(10 - 6)
ey = 550(10 - 6)
A(300, -325)10 - 6
gxy = -650(10 - 6)
y
gxy
2
= -325(10 - 6)
A
C(425, 0)10 - 6
R = C 2(425 - 300)2 + (-325)2 D 10 - 6 = 348.2(10 - 6)
a)
e1 = (425 + 348.2)(10 - 6) = 773(10 - 6)
Ans.
e2 = (425 - 348.2)(10 - 6) = 76.8(10 - 6)
Ans.
b)
g
max
in-plane
= 2R = 2(348.2)(10 - 6) = 696(10 - 6)
Ans.
773(10 - 6)
;
2
Ans.
c)
gabs
max
=
2
gabs
max
= 773(10 - 6)
10–23. The strain at point A on the leg of the angle has
components Px = -140110-62, Py = 180110-62, gxy =
-125110-62. Determine (a) the principal strains at A in the
x– y plane, (b) the maximum shear strain in the x–y plane,
and (c) the absolute maximum shear strain.
ex = -140(10 - 6)
A(-140, -62.5)10 - 6
ey = 180(10 - 6)
gxy = -125(10 - 6)
A
gxy
2
= -62.5(10 - 6)
C(20, 0)10 - 6
A 2(20 - (-140))2 + (-62.5)2 B 10 - 6 = 171.77(10 - 6)
R =
a)
e1 = (20 + 171.77)(10 - 6) = 192(10 - 6)
Ans.
e2 = (20 - 171.77)(10 - 6) = -152(10 - 6)
Ans.
(b, c)
gabs
max
=
g
max
in-plane
= 2R = 2(171.77)(10 - 6) = 344(10 - 6)
Ans.
761
x
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*10–24. The strain at point A on the pressure-vessel wall
has components Px = 480110-62, Py = 720110-62, gxy =
650110-62. Determine (a) the principal strains at A, in the
x– y plane, (b) the maximum shear strain in the x–y plane,
and (c) the absolute maximum shear strain.
ex = 480(10 - 6)
ey = 720(10 - 6)
A(480, 325)10 - 6
C(600, 0)10 - 6
gxy = 650(10 - 6)
y
A
gxy
2
= 325(10 - 6)
R = (2(600 - 480)2 + 3252 )10 - 6 = 346.44(10 - 6)
a)
e1 = (600 + 346.44)10 - 6 = 946(10 - 6)
Ans.
e2 = (600 - 346.44)10 - 6 = 254(10 - 6)
Ans.
b)
g
max
in-plane
= 2R = 2(346.44)10 - 6 = 693(10 - 6)
Ans.
946(10 - 6)
;
2
Ans.
c)
gabs
max
2
=
gabs
max
= 946(10 - 6)
762
x
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The 60° strain rosette is mounted on the bracket.
The following readings are obtained for each gauge:
Pa = -100110-62, Pb = 250110-62, and Pc = 150110-62.
Determine (a) the principal strains and (b) the maximum inplane shear strain and associated average normal strain. In
each case show the deformed element due to these strains.
•10–25.
b
c
60⬚
60⬚
This is a 60° strain rosette Thus,
ex = ea = -100(10 - 6)
1
A 2eb + 2ec - ea B
3
ey =
1
C 2(250) + 2(150) - (-100) D (10 - 6)
3
=
= 300(10 - 6)
gxy =
2
23
(eb - ec) =
2
23
(250 - 150)(10 - 6) = 115.47(10 - 6)
In accordance to the established sign convention, ex = -100(10 - 6), ey = 300(10 - 6)
gxy
and
= 57.74(10 - 6).
2
Thus,
eavg =
ex + ey
2
= a
-100 + 300
b(10 - 6) = 100(10 - 6)
2
Ans.
Then, the coordinates of reference point A and Center C of the circle are
A( -100, 57.74)(10 - 6)
C(100, 0)(10 - 6)
Thus, the radius of the circle is
R = CA = a 2(-100 - 100)2 + 208.16 b(10 - 6) = 208.17(10 - 6)
Using these result, the circle is shown in Fig. a.
The coordinates of points B and D represent e1 and e2 respectively.
e1 = (100 + 208.17)(10 - 6) = 308(10 - 6)
Ans.
e2 = (100 - 208.17)(10 - 6) = -108(10 - 6)
Ans.
Referring to the geometry of the circle,
tan 2(uP)2 =
57.74(10 - 6)
(100 + 100)(10 - 6)
= 0.2887
A uP B 2 = 8.05° (Clockwise)
Ans.
The deformed element for the state of principal strain is shown in Fig. b.
763
a
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10–25. Continued
gmax
The coordinates for point E represent eavg and
in-plane
2
. Thus,
gmax
in-plane
2
= R = 208.17(10 - 6)
gmax
in-plane
= 416(10 - 6)
Ans.
Referring to the geometry of the circle,
tan 2us =
100 + 100
57.74
us = 36.9° (Counter Clockwise)
Ans.
The deformed element for the state of maximum In-plane shear strain is shown in
Fig. c.
764
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10–26. The 60° strain rosette is mounted on a beam.
The following readings are obtained for each gauge:
Pa = 200110-62, Pb = - 450110-62, and Pc = 250110-62.
Determine (a) the in-plane principal strains and (b) the
maximum in-plane shear strain and average normal strain.
In each case show the deformed element due to these strains.
b
a
30⬚ 30⬚
c
With ua = 60°, ub = 120° and uc = 180°,
ea = ex cos2 ua + ey sin2 ua + gxy sin ua cos ua
200(10 - 6) = ex cos2 60° + ey sin2 60° + gxy sin 60° cos 60°
gxy = 200(10 - 6)
0.25ex + 0.75ey + 0.4330
(1)
eb = ex cos2 ub + ey sin2 ub + gxy sin ub cos ub
-450(10 - 6) = ex cos2 120° + ey sin2 120° + gxy sin 120° cos 120°
gxy = -450(10 - 6)
0.25ex + 0.75ey - 0.4330
(2)
ec = ex cos2 uc + ey sin2 uc + gxy sin uc cos uc
250(10 - 6) = ex cos2 180° + ey sin2 180° + gxy sin 180° cos 180°
ex = 250(10 - 6)
Substitute this result into Eqs. (1) and (2) and solve them,
ey = -250 (10 - 6)
gxy = 750.56 (10 - 6)
In accordance to the established sign convention, ex = 250(10 - 6), ey = -250(10 - 6),
gxy
and
= 375.28(10 - 6), Thus,
2
eavg =
ex + ey
2
= c
250 + (-250)
d(10 - 6) = 0
2
Ans.
Then, the coordinates of the reference point A and center C of the circle are
A(250, 375.28)(10 - 6)
C(0, 0)
Thus, the radius of the circle is
R = CA =
A 2(250 - 0)2 + 375.282 B (10 - 6) = 450.92(10 - 6)
Using these results, the circle is shown in Fig. a.
The coordinates for points B and D represent e1 and e2, respectively. Thus,
e1 = 451(10 - 6)
e2 = -451(10 - 6)
Ans.
Referring to the geometry of the circle,
tan 2(uP)1 =
375.28
= 1.5011
250
(uP)1 = 28.2° (Counter Clockwise)
Ans.
The deformed element for the state of principal strains is shown in Fig. b.
765
60⬚
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10–26. Continued
gmax
in-plane
The coordinates of point E represent eavg and
. Thus,
2
gmax
in-plane
gmax
= R = 450.92(10 - 6)
= 902(10 - 6)
in-plane
2
Ans.
Referring to the geometry of the circle,
tan 2us =
250
= 0.6662
375.28
us = 16.8° (Clockwise)
Ans.
766
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10–27. The 45° strain rosette is mounted on a steel shaft.
The following readings are obtained from each gauge:
Pa = 300110-62, Pb = -250110-62, and Pc = -450110-62.
Determine (a) the in-plane principal strains and (b) the
maximum in-plane shear strain and average normal strain.
In each case show the deformed element due to these strains.
b
c
45⬚
With ua = 45°, ub = 90° and uc = 135°,
ea = ex cos2 ua + ey sin2 ua + gxy sin ua cos ua
300(10 - 6) = ex cos2 45° + ey sin2 45° + gxy sin 45° cos 45°
ex + ey + gxy = 600(10 - 6)
(1)
eb = ex cos2 ub + ey sin2 ub + gxy sin ub cos ub
-250(10 - 6) = ex cos2 90° + ey sin2 90° + gxy sin 90° cos 90°
ey = -250(10 - 6)
ec = ex cos2 uc + ey sin2 uc + gxy sin uc cos uc
-450(10 - 6) = ex cos2 135° + ey sin2 135° + gxy sin 135° cos 135°
ex + ey - gxy = -900(10 - 6)
(2)
Substitute the result of ey into Eq. (1) and (2) and solve them
ex = 100(10 - 6)
gxy = 750(10 - 6)
In accordance to the established sign convention, ex = 100(10 - 6), ey = -250(10 - 6)
gxy
and
= 375(10 - 6). Thus,
2
eavg =
ex + ey
2
= c
100 + (-250)
d(10 - 6) = -75(10 - 6)
2
Ans.
Then, the coordinates of the reference point A and the center C of the circle are
A(100, 375)(10 - 6)
C(-75, 0)(10 - 6)
Thus, the radius of the circle is
R = CA = a 2 C 100 - (-75) D 2 + 3752 b (10 - 6) = 413.82(10 - 6)
Using these results, the circle is shown in Fig. a.
The Coordinates of points B and D represent e1 and e2, respectively. Thus,
e1 =
e2 =
A -75 + 413.82 B (10 - 6) = 339(10 - 6)
Ans.
A -75 - 413.82 B (10 - 6) = -489(10 - 6)
Ans.
Referring to the geometry of the circle
tan 2(uP)1 =
375
= 2.1429
100 + 75
(uP)1 = 32.5° (Counter Clockwise)
Ans.
767
45⬚
a
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10–27. Continued
The deformed element for the state of principal strains is shown in Fig. b.
gmax
The coordinates of point E represent eavg and
gmax
in-plane
2
= R = 413.82(106)
in-plane
gmax
2
in-plane
. Thus
= 828(10 - 6)
Ans.
Referring to the geometry of the circle
tan 2us =
-100 + 75
= 0.4667
375
us = 12.5° (Clockwise)
Ans.
768
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*10–28. The 45° strain rosette is mounted on the link of
the backhoe. The following readings are obtained from
each gauge: Pa = 650110-62, Pb = -300110-62, Pc = 480110-62.
Determine (a) the in-plane principal strains and (b) the
maximum in-plane shear strain and associated average
normal strain.
a
45⬚
b
ea = 650(10 - 6);
ua = 180°;
eb = -300(10 - 6);
ub = 225°
c
uc = 270°
Applying Eq. 10–16, e = ex cos2 u + ey sin2 u + gxy sin u cos u
650(10 - 6) = ex cos2 (180°) + ey sin2 (180°) + gxy sin (180°) cos (180°)
ex = 650 (10 - 6)
480 (10 - 6) = ex cos2 (270°) + ey sin2 (270°) + gxy sin (270°) cos (270°)
ey = 480 (10 - 6)
-300 (10 - 6) = 650 (10 - 6) cos2 (225°) + 480 (10 - 6) sin2 (225°) + gxy sin (225°) cos (225°)
gxy = -1730 (10 - 6)
Therefore, ex = 650 (10 - 6)
gxy
2
ey = 480 (10 - 6)
gxy = -1730 (10 - 6)
= -865 (10 - 6)
Mohr’s circle:
A(650, -865) 10 - 6
C(565, 0) 10 - 6
R = CA = C 2(650 - 565)2 + 8652 D 10 - 6 = 869.17 (10 - 6)
(a)
(b)
e1 = [565 + 869.17]10 - 6 = 1434 (10 - 6)
Ans.
e2 = [565 - 869.17]10 - 6 = -304 (10 - 6)
Ans.
gmax
in-plane
45⬚
ec = 480(10 - 6)
= 2 R = 2(869.17) (10 - 6) = 1738 (10 - 6)
Ans.
eavg = 565(10 - 6)
Ans.
769
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10–30. For the case of plane stress, show that Hooke’s law
can be written as
sx =
E
E
1Px + nPy2, sy =
1Py + nPx2
11 - n22
11 - n22
Generalized Hooke’s Law: For plane stress, sz = 0. Applying Eq. 10–18,
ex =
1
A sx - v sy B
E
vEex = A sx - v sy B v
vEex = v sx - v2 sy
ey =
[1]
1
(s - v sx)
E y
E ey = -v sx + sy
[2]
Adding Eq [1] and Eq.[2] yields.
vE ex - E ey = sy - v2 sy
sy =
E
A vex + ey B
1 - v2
(Q.E.D.)
Substituting sy into Eq. [2]
E ey = -vsx +
sx =
=
=
E
A v ex + ey B
1 - v2
E A v ex + ey B
v (1 - v2)
-
Eey
v
E v ex + E ey - E ey + Eey v2
v(1 - v2)
E
(ex + v ey)
1 - v2
(Q.E.D.)
770
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10–31. Use Hooke’s law, Eq. 10–18, to develop the straintransformation equations, Eqs. 10–5 and 10–6, from the
stress-transformation equations, Eqs. 9–1 and 9–2.
Stress transformation equations:
sx + sy
sx¿ =
2
tx¿y¿ =
sy¿ =
+
sx - sy
2
2
cos 2u + txy sin 2u
(1)
sin 2u + txy cos 2u
2
sx + sy
sx - sy
-
sx - sy
2
(2)
cos 2u - txy sin 2u
(3)
Hooke’s Law:
ex =
v sy
sx
E
E
(4)
ey =
sy
-v sx
+
E
E
(5)
txy = G gxy
G =
(6)
E
2 (1 + v)
(7)
From Eqs. (4) and (5)
ex + ey =
ex - ey =
(1 - v)(sx + sy)
(8)
E
(1 + v)(sx - sy)
(9)
E
From Eqs. (6) and (7)
txy =
E
g
2 (1 + v) xy
(10)
From Eq. (4)
ex¿ =
v sy¿
sx¿
E
E
(11)
Substitute Eqs. (1) and (3) into Eq. (11)
ex¿ =
(1 - v)(sx - sy)
2E
+
(1 + v)(sx - sy)
2E
cos 2u +
(1 + v)txy sin 2u
E
(12)
By using Eqs. (8), (9) and (10) and substitute into Eq. (12),
ex¿ =
ex + ey
2
+
ex - ey
2
cos 2u +
gxy
2
sin 2u
QED
771
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10–31. Continued
From Eq. (6).
gx¿y¿ = G gx¿y¿ =
E
g
2 (1 + v) x¿y¿
(13)
Substitute Eqs. (13), (6) and (9) into Eq. (2),
E (ex - ey)
E
E
gx¿y¿ = sin 2u +
g cos 2u
2 (1 + v)
2 (1 + v)
2 (1 + v) xy
gx¿y¿
2
= -
(ex - ey)
2
sin 2u +
gxy
2
cos 2u
QED
*10–32. A bar of copper alloy is loaded in a tension
machine and it is determined that Px = 940110-62 and
sx = 14 ksi, sy = 0, sz = 0. Determine the modulus of
elasticity, Ecu, and the dilatation, ecu, of the copper.
ncu = 0.35.
ex =
1
[s - v(sy + sz)]
E x
940(10 - 6) =
ecu =
1
[14(103) - 0.35(0 + 0)]
Ecu
Ecu = 14.9(103) ksi
Ans.
1 - 2(0.35)
1 - 2v
(14 + 0 + 0) = 0.282(10 - 3)
(sx + sy + sz) =
E
14.9(103)
Ans.
The principal strains at a point on the aluminum
fuselage of a jet aircraft are P1 = 780110-62 and P2 =
400110-62. Determine the associated principal stresses at
the point in the same plane. Eal = 1011032 ksi, nal = 0.33.
Hint: See Prob. 10–30.
•10–33.
Plane stress, s3 = 0
See Prob 10-30,
s1 =
=
s2 =
=
E
(e1 + ve2)
1 - v2
10(103)
1 - 0.332
(780(10 - 6) + 0.33(400)(10 - 6)) = 10.2 ksi
Ans.
E
(e2 + ve1)
1 - v2
10(103)
1 - 0.332
(400(10 - 6) + 0.33(780)(10 - 6)) = 7.38 ksi
Ans.
772
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10–34. The rod is made of aluminum 2014-T6. If it is
subjected to the tensile load of 700 N and has a diameter of
20 mm, determine the absolute maximum shear strain in the
rod at a point on its surface.
700 N
Normal Stress: For uniaxial loading, sy = sz = 0.
sx =
P
=
A
p
4
700
= 2.228 MPa
(0.022)
Normal Strain: Applying the generalized Hooke’s Law.
ex =
=
1
C s - v A sy + sz B D
E x
1
C 2.228 A 106 B - 0 D
73.1(109)
= 30.48 A 10 - 6 B
ey =
=
1
C s - v(sx + sz) D
E y
1
C 0 - 0.35 A 2.228 A 106 B + 0 B D
73.1(109)
= -10.67 A 10 - 6 B
ez =
=
1
C s - v A sx + sy B D
E z
1
C 0 - 0.35 A 2.228 A 106 B + 0 B D
73.1(109)
= -10.67 A 10 - 6 B
Therefore.
emax = 30.48 A 10 - 6 B
emin = -10.67 A 10 - 6 B
Absolute Maximum Shear Strain:
gabs
max
= emax - emin
= [30.48 - (-10.67)] A 10 - 6 B = 41.1 A 10 - 6 B
Ans.
773
700 N
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10–35. The rod is made of aluminum 2014-T6. If it is
subjected to the tensile load of 700 N and has a diameter of
20 mm, determine the principal strains at a point on the
surface of the rod.
700 N
Normal Stress: For uniaxial loading, sy = sz = 0.
sx =
P
=
A
p
4
700
= 2.228 MPa
(0.022)
Normal Strains: Applying the generalized Hooke’s Law.
ex =
=
1
C s - v A sy + sz B D
E x
1
C 2.228 A 106 B - 0 D
73.1(109)
= 30.48 A 10 - 6 B
ey =
=
1
C s - v(sx + sz) D
E y
1
C 0 - 0.35 A 2.228 A 106 B + 0 B D
73.1(109)
= -10.67 A 10 - 6 B
ez =
=
1
C s - v A sx + sy B D
E z
1
C 0 - 0.35 A 2.228 A 106 B + 0 B D
73.1(109)
= -10.67 A 10 - 6 B
Principal Strains: From the results obtained above,
emax = 30.5 A 10 - 6 B
eint = emin = -10.7 A 10 - 6 B
Ans.
774
700 N
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*10–36. The steel shaft has a radius of 15 mm. Determine
the torque T in the shaft if the two strain gauges, attached to
the surface of the shaft, report strains of Px¿ = -80110-62
and Py¿ = 80110-62. Also, compute the strains acting in the x
and y directions. Est = 200 GPa, nst = 0.3.
ex¿ = -80(10 - 6)
y
T
ex = ey = 0
Ans.
ex¿ = ex cos2 u + ey sin2 u + gxy sin u cos u
u = 45°
-80(10 - 6) = 0 + 0 + gxy sin 45° cos 45°
gxy = -160(10 - 6)
Ans.
Also, u = 135°
80(10 - 6) = 0 + 0 + g sin 135° cos 135°
gxy = -160(10 - 6)
200(109)
E
=
= 76.923(109)
2(1 + V)
2(1 + 0.3)
t = Gg = 76.923(109)(160)(10 - 6) = 12.308(106) Pa
12.308(106) A
p
B (0.015)4
2
= 65.2 N # m
0.015
Ans.
10–37. Determine the bulk modulus for each of the
following materials: (a) rubber, Er = 0.4 ksi, nr = 0.48, and
(b) glass, Eg = 811032 ksi, ng = 0.24.
a) For rubber:
Kr =
Er
0.4
=
= 3.33 ksi
3 (1 - 2 vr)
3[1 - 2(0.48)]
Ans.
b) For glass:
Kg =
Eg
3 (1 - 2 vg)
=
x
T
Pure shear
tJ
T =
=
c
x¿
45⬚
ey¿ = 80(10 - 6)
G =
y¿
8(103)
= 5.13 (103) ksi
3[1 - 2(0.24)]
Ans.
775
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10–38. The principal stresses at a point are shown in the
figure. If the material is A-36 steel, determine the
principal strains.
12 ksi
e1 =
1
1
e 12 - 0.32 C 8 + (-20) D f = 546 (10-6)
C s1 - v(s2 + s3) D =
E
29.0(103)
e2 =
1
1
e 8 - 0.32 C 12 + (-20) D f = 364 (10-6)
C s - v(s1 + s3) D =
E 2
29.0(103)
e3 =
20 ksi
8 ksi
1
1
C s3 - v(s1 + s2) D =
C -20 - 0.32(12 + 8) D = -910 (10-6)
E
29.0(103)
emax = 546 (10 - 6)
eint = 346 (10 - 6)
emin = -910 (10 - 6)
Ans.
10–39. The spherical pressure vessel has an inner
diameter of 2 m and a thickness of 10 mm. A strain gauge
having a length of 20 mm is attached to it, and it is observed
to increase in length by 0.012 mm when the vessel
is pressurized. Determine the pressure causing this
deformation, and find the maximum in-plane shear stress,
and the absolute maximum shear stress at a point on the
outer surface of the vessel. The material is steel, for which
Est = 200 GPa and nst = 0.3.
20 mm
1000
r
=
= 100 7 10, the thin wall analysis is valid to
t
10
determine the normal stress in the wall of the spherical vessel. This is a plane stress
Normal Stresses: Since
problem where smin = 0 since there is no load acting on the outer surface of the wall.
smax = slat =
p(1000)
pr
=
= 50.0p
2t
2(10)
[1]
Normal Strains: Applying the generalized Hooke’s Law with
emax = elat =
0.012
= 0.600 A 10 - 3 B mm>mm
20
emax =
1
C s - V (slat + smin) D
E max
0.600 A 10 - 3 B =
1
[50.0p - 0.3 (50.0p + 0)]
200(104)
p = 3.4286 MPa = 3.43 MPa
Ans.
From Eq.[1] smax = slat = 50.0(3.4286) = 171.43 MPa
Maximum In-Plane Shear (Sphere’s Surface): Mohr’s circle is simply a dot. As the
result, the state of stress is the same consisting of two normal stresses with zero
shear stress regardless of the orientation of the element.
t
max
in-plane
= 0
Ans.
smax - smin
171.43 - 0
=
= 85.7MPa
2
2
Ans.
Absolute Maximum Shear Stress:
tabs
max
=
776
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*10–40. The strain in the x direction at point A on the
steel beam is measured and found to be Px = -100110-62.
Determine the applied load P. What is the shear strain gxy
at point A? Est = 2911032 ksi, nst = 0.3.
P
y
3 in.
A
3 ft
1
1
(6)(9)3 (5.5)(83) = 129.833 in4
12
12
Ix =
QA = (4.25)(0.5)(6) + (2.75)(0.5)(2.5) = 16.1875 in3
s = Eex = 29(103)(100)(10 - 6) = 2.90 ksi
My
,
I
s =
2.90 =
1.5P(12)(1.5)
129.833
P = 13.945 = 13.9 kip
tA =
VQ
0.5(13.945)(16.1875)
=
= 1.739 ksi
It
129.833(0.5)
G =
29(103)
E
=
= 11.154(103) ksi
2(1 + v)
2(1 + 0.3)
gxy =
txy
G
=
Ans.
1.739
= 0.156(10 - 3) rad
11.154(103)
Ans.
777
x
4 ft
7 ft
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The cross section of the rectangular beam is
subjected to the bending moment M. Determine an
expression for the increase in length of lines AB and CD.
The material has a modulus of elasticity E and Poisson’s
ratio is n.
•10–41.
C
D
B
h
For line AB,
sz = ey = -
A
M
12My
My
My
= = 1
3
I
b h3
12 b h
v sz
=
E
¢LAB =
=
L0
b
12 v My
E b h3
h
h
2
ey dy =
2
12 v M
y dy
3
E b h L0
3vM
2Ebh
Ans.
For line CD,
sz = ex = -
M h2
Mc
6M
= - 2
= - 1
3
I
bh
b
h
12
v sz
E
=
6vM
E b h2
¢LCD = ex LCD =
=
6vM
(b)
E b h2
6vM
E h2
Ans.
10–42. The principal stresses at a point are shown in
the figure. If the material is aluminum for which
Eal = 1011032 ksi and nal = 0.33, determine the principal
strains.
26 ksi
ex =
1
1
(10 - 0.33(-15 - 26)) = 2.35(10 - 3)
(s - v(sy + sz)) =
E x
10(103)
ey =
1
1
(-15 - 0.33)(10 - 26)) = -0.972(10 - 3)Ans.
(s - v(sx + sz)) =
E y
10(103)
ez =
Ans.
1
1
(-26 - 0.33(10 - 15)) = -2.44(10 - 3) Ans.
(s - v(sx + sy)) =
E z
10(103)
778
15 ksi
10 ksi
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10–43. A single strain gauge, placed on the outer surface
and at an angle of 30° to the axis of the pipe, gives a reading
at point A of Pa = -200(10-6). Determine the horizontal
force P if the pipe has an outer diameter of 2 in. and an
inner diameter of 1 in. The pipe is made of A-36 steel.
1.5 ft
Using the method of section and consider the equilibrium of the FBD of the pipe’s
upper segment, Fig. a,
©Fz = 0;
Vz - p = 0
Vz = p
©Mx = 0;
Tx - p(1.5) = 0 Tx = 1.5p
©My = 0;
My - p(2.5) = 0 My = 2.5p
30⬚
A
The normal strees is due to bending only. For point A, z = 0. Thus
sx =
My z
Iy
= 0
The shear stress is the combination of torsional shear stress and transverse shear
stress. Here, J = p2 (14 - 0.54) = 0.46875 p in4. Thus, for point A
tt =
1.5p(12)(1)
38.4 p
Txc
=
=
p
J
0.46875p
Referring to Fig. b,
(QA)z = y1œ A1œ - y2œ A2œ =
4 (1) p 2
4(0.5) p
c (1 ) d c (0.52) d
3p 2
3p 2
= 0.5833 in3
Iy =
p
4
(14 - 0.54) = 0.234375 p in4
Combine these two shear stress components,
t = tt + tv =
P
2.5 ft
38.4P
2.4889P
40.8889P
+
=
p
p
p
Since no normal stress acting on point A, it is subjected to pure shear which can be
represented by the element shown in Fig. c.
For pure shear, ex = ez = 0,
ea = ex cos3 ua + ez sin2 ua + gxz sin ua cos ua
-200(10 - 6) = 0 + 0 + gxz sin 150° cos 150°
gxz = 461.88(10 - 6)
Applying the Hooke’s Law for shear,
txz = G gxz
40.8889P
= 11.0(103) C 461.88(10 - 6) D
p
P = 0.3904 kip = 390 lb
Ans.
779
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*10–44. A single strain gauge, placed in the vertical plane
on the outer surface and at an angle of 30° to the axis of the
pipe, gives a reading at point A of Pa = -200(10-6).
Determine the principal strains in the pipe at point A. The
pipe has an outer diameter of 2 in. and an inner diameter of
1 in. and is made of A-36 steel.
1.5 ft
P
2.5 ft
Using the method of sections and consider the equilibrium of the FBD of the pipe’s
upper segment, Fig. a,
©Fz = 0;
Vz - P = 0
Vz = P
©Mx = 0;
Tx - P(1.5) = 0 Tx = 1.5P
©My = 0;
My - P(2.5) = 0 My = 2.5P
By observation, no normal stress acting on point A. Thus, this is a case of pure shear.
For the case of pure shear,
ex = ez = ey = 0
ea = ex cos2 ua + ez sin2 ua + gxz sin ua cos ua
-200(10 - 6) = 0 + 0 + gxz sin 150° cos 150°
gxz = 461.88(10 - 6)
e1, 2 =
ex + ez
= B
2
+
A
a
ex - ez
2
2
b + a
gxz
2
b
2
0 - 0 2
461.88 2
0 + 0
-6
;
a
b + a
b R (10 )
2
A
2
2
e1 = 231(10 - 6)
e2 = -231(10 - 6)
Ans.
780
30⬚
A
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10–45. The cylindrical pressure vessel is fabricated using
hemispherical end caps in order to reduce the bending stress
that would occur if flat ends were used. The bending stresses
at the seam where the caps are attached can be eliminated
by proper choice of the thickness th and tc of the caps and
cylinder, respectively. This requires the radial expansion to
be the same for both the hemispheres and cylinder. Show
that this ratio is tc>th = 12 - n2>11 - n2.Assume that the
vessel is made of the same material and both the cylinder
and hemispheres have the same inner radius. If the cylinder
is to have a thickness of 0.5 in., what is the required thickness
of the hemispheres? Take n = 0.3.
tc
th
r
For cylindrical vessel:
pr
2 tc
s1 =
pr
;
tc
e1 =
1
[s - v (s2 + s3)]
E 1
=
s2 =
s3 = 0
vpr
pr
1
1 pr
a
b =
a1 - v b
E tc
2 tc
E tc
2
d r = e1 r =
p r2
1
a1 - v b
E tc
2
(1)
For hemispherical end caps:
s1 = s2 =
e1 =
=
pr
2 th
1
[s - v (s2 + s3)] ;
E 1
s3 = 0
vpr
pr
1 pr
a
b =
(1 - v)
E 2 th
2 th
2 E th
d r = e1 r =
p r2
(1 - v)
2 E th
(2)
Equate Eqs. (1) and (2):
p r2
p r2
1
a1 - vb =
(1 - v)
E tc
2
2 E th
2 (1 - 21 v)
tc
2 - v
=
=
th
1 - v
1 - v
th =
QED
(1 - v) tc
(1 - 0.3) (0.5)
=
= 0.206 in.
2 - v
2 - 0.3
Ans.
781
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10–46. The principal strains in a plane, measured
experimentally at a point on the aluminum fuselage of a jet
aircraft, are P1 = 630(10-6) and P2 = 350(10-6). If this is
a case of plane stress, determine the associated principal
stresses at the point in the same plane. Eal = 10(103) ksi
and nal = 0.33.
Normal Stresses: For plane stress, s3 = 0.
Normal Strains: Applying the generalized Hooke’s Law.
e1 =
1
C s1 - v (s2 + s3) D
E
630 A 10 - 6 B =
1
[s1 - 0.33(s2 + 0)]
10(103)
6.30 = s1 - 0.33s2
e2 =
[1]
1
C s - v (s1 + s3) D
E 2
350 A 10 - 6 B =
1
C s2 - 0.33(s1 + 0) D
10(103)
3.50 = s2 - 0.33s1
[2]
Solving Eqs.[1] and [2] yields:
s1 = 8.37 ksi
s2 = 6.26 ksi
Ans.
10–47. The principal stresses at a point are shown in
the figure. If the material is aluminum for which
Eal = 1011032 ksi and nal = 0.33, determine the principal
strains.
3 ksi
e1 =
1
1
e 8 - 0.33 C 3 + (-4) D f = 833 (10 - 6)
C s - v(s2 + s3) D =
E 1
10(103)
e2 =
1
1
e 3 - 0.33 C 8 + (-4) D f = 168 (10 - 6)
C s - v(s1 + s3) D =
E 2
10(103)
e3 =
1
1
C s3 - v(s1 + s2) D =
C -4 - 0.33(8 + 3) D = -763 (10 - 6)
E
10(103)
Using these results,
e1 = 833(10 - 6)
e2 = 168(10 - 6)
e3 = -763(10 - 6)
782
8 ksi
4 ksi
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*10–48. The 6061-T6 aluminum alloy plate fits snugly into
the rigid constraint. Determine the normal stresses sx and
sy developed in the plate if the temperature is increased by
¢T = 50°C. To solve, add the thermal strain a¢T to the
equations for Hooke’s Law.
y
400 mm
300 mm
x
Generalized Hooke’s Law: Since the sides of the aluminum plate are confined in the
rigid constraint along the x and y directions, ex = ey = 0. However, the plate is
allowed to have free expansion along the z direction. Thus, sz = 0. With the
additional thermal strain term, we have
ex =
0 =
1
cs - v A sy + sz B d + a¢T
E x
1
68.9 A 109 B
csx - 0.35 A sy + 0 B d + 24a 10 - 6 b(50)
sx - 0.35sy = -82.68 A 106 B
ey =
0 =
(1)
1
C s - v A sx + sz B D + a¢T
E y
1
68.9a 10 b
9
C sy - 0.35(sx + 0) D + 24 A 10 - 6 B (50)
sy - 0.35sx = -82.68 A 106 B
(2)
Solving Eqs. (1) and (2),
sx = sy = -127.2 MPa = 127.2 MPa (C)
Ans.
Since sx = sy and sy 6 sY, the above results are valid.
783
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Initially, gaps between the A-36 steel plate and
the rigid constraint are as shown. Determine the normal
stresses sx and sy developed in the plate if the temperature
is increased by ¢T = 100°F. To solve, add the thermal
strain a¢T to the equations for Hooke’s Law.
•10–49.
y
0.0015 in.
6 in.
8 in.
0.0025 in.
x
Generalized Hooke’s Law: Since there are gaps between the sides of the plate and the rigid
constraint, the plate is allowed to expand before it comes in contact with the constraint.
dy
dx
0.0025
0.0015
Thus, ex =
=
= 0.3125 A 10 - 3 B and
ey =
=
= 0.25 A 10 - 3 B .
Lx
8
Ly
6
However, the plate is allowed to have free expansion along the z direction. Thus, sz = 0.
With the additional thermal strain term, we have
ex =
1
csx - v A sy + sz B d + a¢T
E
0.3125 a 10 - 3 b =
1
29.0 a103 b
C sx - 0.32 A sy + 0 B D + 6.60 A 10 - 6 B (100)
sx - 0.32sy = -10.0775
ey =
(1)
1
C s - v A sx + sz B D + a¢T
E y
0.25 A 10 - 3 B =
1
29.0 A 103 B
C sy - 0.32(sx + 0) D + 6.60 A 10 - 6 B (100)
sy - 0.32sx = -11.89
(2)
Solving Eqs. (1) and (2),
sx = -15.5 ksi = 15.5 ksi (C)
Ans.
sy = -16.8 ksi = 16.8 ksi (C)
Ans.
Since sx 6 sY and sy 6 sY, the above results are valid.
784
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10–50. Two strain gauges a and b are attached to a plate
made from a material having a modulus of elasticity of
E = 70 GPa and Poisson’s ratio n = 0.35. If the gauges give
a reading of Pa = 450110-62 and Pb = 100110-62, determine
the intensities of the uniform distributed load wx and wy
acting on the plate. The thickness of the plate is 25 mm.
wy
b
y
45⬚
a
Normal Strain: Since no shear force acts on the plane along the x and y axes, gxy = 0.
With ua = 0 and ub = 45°, we have
2
2
ea = ex cos ua + ey sin ua + gxy sin ua cos ua
450 A 10 - 6 B = ex cos2 0° + ey sin2 0°+0
ex = 450 A 10 - 6 B
eb = ex cos2 ub + ey sin2 ub + gxy sin ub cos ub
100 A 10 - 6 B = 450 A 10 - 6 B cos2 45° + ey sin2 45° + 0
ey = -250 A 10 - 6 B
Generalized Hooke’s Law: This is a case of plane stress. Thus, sz = 0.
ex =
1
C s - v A sy + sz B D
E x
450 A 10 - 6 B =
1
70 A 109 B
C sy - 0.35 A sy + 0 B D
sx - 0.35sy = 31.5 A 106 B
ey =
(1)
1
C s - v A sx + sz B D
E y
-250 A 10-6 B =
1
70 A 109 B
C sy - 0.35 A sy + 0 B D
sy - 0.35sx = -17.5 A 106 B
(2)
Solving Eqs. (1) and (2),
sy = -7.379 A 106 B N>m2
sx = 28.917 A 106 B N>m2
Then,
wy = syt = -7.379 A 106 B (0.025) = -184 N>m
Ans.
wx = sxt = 28.917 A 106 B (0.025) = 723 N>m
Ans.
785
z
x
wx
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10–51. Two strain gauges a and b are attached to the
surface of the plate which is subjected to the uniform
distributed load wx = 700 kN>m and wy = -175 kN>m.
If the gauges give a reading of Pa = 450110-62 and
Pb = 100110-62, determine the modulus of elasticity E,
shear modulus G, and Poisson’s ratio n for the material.
wy
b
y
45⬚
Normal Stress and Strain: The normal stresses along the x, y, and z axes are
sx =
700 A 103 B
0.025
sy = -
a
= 28 A 10 B N>m
6
175 A 103 B
0.025
2
= -7 A 106 B N>m2
z
sz = 0 (plane stress)
Since no shear force acts on the plane along the x and y axes, gxy = 0. With ua = 0°
and ub = 45°, we have
ea = ex cos2 ua + ey sin2 ua + gxy sin ua cos ua
450 A 10 - 6 B = ex cos2 0° + ey sin2 0° + 0
ex = 450 A 10 - 6 B
eb = ex cos2 ub + ey sin2 ub + gxy sin ub cos ub
100 A 10 - 6 B = 450 A 10 - 6 B cos2 45°+ ey sin2 45° + 0
ey = -250 A 10 - 6 B
Generalized Hooke’s Law:
ex =
1
C s - v A sy + sz B D
E x
450 A 10 - 6 B =
1
B 28 A 106 B - v C -7 A 106 B + 0 D R
E
450 A 10 - 6 B E - 7 A 106 B v = 28 A 106 B
ey =
(1)
1
[s - v(sx + sz)]
E y
-250 A 10 - 6 B =
1
b -7 A 106 B - v C 28 A 106 B + 0 D r
E
250 A 10 - 6 B E - 28 A 106 B v = 7 A 106 B
(2)
Solving Eqs. (1) and (2),
E = 67.74 A 109 B N>m2 = 67.7 GPa
Ans.
v = 0.3548 = 0.355
Ans.
Using the above results,
G =
67.74 A 109 B
E
=
2(1 + v)
2(1 + 0.3548)
= 25.0 A 109 B N>m2 = 25.0 GPa
Ans.
786
x
wx
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*10–52. The block is fitted between the fixed supports. If the
glued joint can resist a maximum shear stress of tallow = 2 ksi,
determine the temperature rise that will cause the joint to fail.
Take E = 10 (103) ksi, n = 0.2, and Hint: Use Eq. 10–18 with
an additional strain term of a¢T (Eq. 4–4).
40⬚
Normal Strain: Since the aluminum is confined along the y direction by the rigid
frame, then ey = 0 and sx = sz = 0. Applying the generalized Hooke’s Law with
the additional thermal strain,
ey =
0 =
1
C s - v(sx + sz) D + a¢T
E y
1
C sy - 0.2(0 + 0) D + 6.0 A 10 - 6 B (¢T)
10.0(103)
sy = -0.06¢T
Construction of the Circle: In accordance with the sign convention. sx = 0,
sy = -0.06¢T and txy = 0. Hence.
savg =
sx + sy
2
=
0 + ( -0.06¢T)
= -0.03¢T
2
The coordinates for reference points A and C are A (0, 0) and C(-0.03¢T, 0).
The radius of the circle is R = 2(0 - 0.03¢T)2 + 0 = 0.03¢T
Stress on The inclined plane: The shear stress components tx¿y¿, are represented by
the coordinates of point P on the circle.
tx¿y¿ = 0.03¢T sin 80° = 0.02954¢T
Allowable Shear Stress:
tallow = tx¿y¿
2 = 0.02954¢T
¢T = 67.7 °F
Ans.
787
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The smooth rigid-body cavity is filled with liquid
6061-T6 aluminum. When cooled it is 0.012 in. from the top
of the cavity. If the top of the cavity is covered and the
temperature is increased by 200°F, determine the stress
components sx , sy , and sz in the aluminum. Hint: Use
Eqs. 10–18 with an additional strain term of a¢T (Eq. 4–4).
•10–53.
z
0.012 in.
4 in.
4 in.
6 in.
y
Normal Strains: Since the aluminum is confined at its sides by a rigid container and
0.012
allowed to expand in the z direction, ex = ey = 0; whereas ez =
= 0.002.
6
Applying the generalized Hooke’s Law with the additional thermal strain,
ex =
0 =
1
C s - v(sy + sz) D + a¢T
E x
1
C sx - 0.35 A sy + sz B D + 13.1 A 10 - 6 B (200)
10.0(103)
0 = sx - 0.35sy - 0.35sz + 26.2
ey =
0 =
[1]
1
C s - v(sx + sz) + a¢T
E y
1
C sy - 0.35(sx + sz) D + 13.1 A 10 - 6 B (200)
10.0(103)
0 = sy - 0.35sx - 0.35sz + 26.2
ez =
0.002 =
[2]
1
C s - v A sx + sy B D + a¢T
E z
1
C sz - 0.35 A sx + sy B D + 13.1 A 10 - 6 B (200)
10.0(103)
0 = sz - 0.35sx - 0.35sy + 6.20
[3]
Solving Eqs.[1], [2] and [3] yields:
sx = sy = -70.0 ksi
sz = -55.2 ksi
Ans.
788
x
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10–54. The smooth rigid-body cavity is filled with liquid
6061-T6 aluminum. When cooled it is 0.012 in. from the top
of the cavity. If the top of the cavity is not covered and the
temperature is increased by 200°F, determine the strain
components Px , Py , and Pz in the aluminum. Hint: Use
Eqs. 10–18 with an additional strain term of a¢T (Eq. 4–4).
z
0.012 in.
4 in.
4 in.
6 in.
y
Normal Strains: Since the aluminum is confined at its sides by a rigid container,
then
ex = ey = 0
Ans.
and since it is not restrained in z direction, sz = 0. Applying the generalized
Hooke’s Law with the additional thermal strain,
ex =
0 =
1
C sx - v A sy + sz B D + a¢T
E
1
C sx - 0.35 A sy + 0 B D + 13.1 A 10 - 6 B (200)
10.0(103)
0 = sx - 0.35sy + 26.2
ey =
0 =
[1]
1
C s - v(sx + sz) D + a¢T
E y
1
C sy - 0.35(sx + 0) D + 13.1 A 10 - 6 B (200)
10.0(103)
0 = sy - 0.35sx + 26.2
[2]
Solving Eqs. [1] and [2] yields:
sx = sy = -40.31 ksi
ez =
=
1
C s - v A sx + sy B D + a¢T
E z
1
{0 - 0.35[-40.31 + (-40.31)]} + 13.1 A 10 - 6 B (200)
10.0(103)
= 5.44 A 10 - 3 B
Ans.
789
x
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10–55. A thin-walled spherical pressure vessel having an
inner radius r and thickness t is subjected to an internal
pressure p. Show that the increase in the volume within
the vessel is ¢V = 12ppr4>Et211 - n2. Use a small-strain
analysis.
pr
2t
s1 = s2 =
s3 = 0
e1 = e2 =
1
(s - vs2)
E 1
e1 = e2 =
pr
(1 - v)
2t E
e3 =
1
(-v(s1 + s2))
E
e3 = V =
v pr
tE
4pr3
3
V + ¢V =
4p
4pr3
¢r 3
(r + ¢r)3 =
(1 +
)
r
3
3
where ¢V V V, ¢r V r
V + ¢V -
eVol =
¢r
4p r3
a1 + 3
b
r
3
¢r
¢V
= 3a b
V
r
Since e1 = e2 =
eVol = 3e1 =
2p(r + ¢r) - 2p r
¢r
=
r
2p r
3pr
(1 - v)
2t E
¢V = VeVol =
2pp r4
(1 - v)
Et
QED
790
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*10–56. A thin-walled cylindrical pressure vessel has an
inner radius r, thickness t, and length L. If it is subjected
to an internal pressure p, show that the increase in
its inner radius is dr = rP1 = pr211 - 21 n2>Et and the
increase in its length is ¢L = pLr112 - n2>Et. Using these
results, show that the change in internal volume becomes
dV = pr211 + P12211 + P22L - pr2L. Since P1 and P2 are
small quantities, show further that the change in volume
per unit volume, called volumetric strain, can be written as
dV>V = pr12.5 - 2n2>Et.
Normal stress:
pr
;
t
s1 =
s2 =
pr
2t
Normal strain: Applying Hooke’s law
e1 =
=
1
[s - v (s2 + s3)],
E 1
vpr
pr
1
1 pr
a
b =
a1 - vb
E
t
2t
Et
2
d r = et r =
e2 =
=
s3 = 0
p r2
1
a1 - v b
Et
2
1
[s - v (s1 + s3)],
E 2
QED
s3 = 0
vpr
pr 1
1 pr
a
b =
a - vb
E 2t
t
Et 2
¢L = e2 L =
pLr 1
a - vb
Et
2
V¿ = p(r + e1 r)2 (L + e2L) ;
QED
V = p r2 L
dV = V¿ - V = pr2 (1 + e1)2 (1 + e2)L - pr2 L
QED
(1 + e1)2 = 1 + 2 e1 neglect e21 term
(1 + e1)2 (1 + e2) = (1 + 2 e1)(1 + e2) = 1 + e2 + 2 e1 neglect e1 e2 term
dV
= 1 + e2 + 2 e1 - 1 = e2 + 2 e1
V
=
2pr
pr 1
1
a - vb +
a1 - v b
Et 2
Et
2
=
pr
(2.5 - 2 v)
Et
QED
791
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10–57. The rubber block is confined in the U-shape
smooth rigid block. If the rubber has a modulus of elasticity
E and Poisson’s ratio n, determine the effective modulus of
elasticity of the rubber under the confined condition.
P
Generalized Hooke’s Law: Under this confined condition, ex = 0 and sy = 0. We
have
ex =
0 =
1
C sx - v A sy + sz B D
E
1
(s - vsz)
E x
sx = vsz
(1)
ez =
1
C s - v A sx + sy B D
E z
ez =
1
[s - v(sx + 0)]
E z
ez =
1
(s - vsx)
E z
(2)
Substituting Eq. (1) into Eq. (2),
ez =
sz
E
A 1 - v2 B
The effective modulus of elasticity of the rubber block under the confined condition
can be determined by considering the rubber block as unconfined but rather
undergoing the same normal strain of ez when it is subjected to the same normal
stress sz, Thus,
sz = Eeff ez
Eeff =
sz
ez
=
sz
sz
E
A 1 - v2 B
=
E
1 - v2
Ans.
792
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Page 793
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10–58. A soft material is placed within the confines of a
rigid cylinder which rests on a rigid support. Assuming that
Px = 0 and Py = 0, determine the factor by which the
modulus of elasticity will be increased when a load is
applied if n = 0.3 for the material.
z
P
x
Normal Strain: Since the material is confined in a rigid cylinder. ex = ey = 0.
Applying the generalized Hooke’s Law,
ex =
1
C sz - v(sy + sx) D
E
0 = sx - v(sy + sz)
ey =
[1]
1
C sy - v(sx + sz) D
E
0 = sy - v(sx + sz)
[2]
Solving Eqs.[1] and [2] yields:
sx = sy =
v
s
1 - v z
Thus,
ez =
=
=
1
C s - v(sx + sy) D
E z
v
v
1
csz - v a
sz +
s bd
E
1 - v
1 - v z
sz
E
c1 -
2v2
d
1 - v
=
sz 1 - v - 2v2
c
d
E
1 - v
=
sz (1 + v)(1 - 2v
c
d
E
1 - v
Thus, when the material is not being confined and undergoes the same normal strain
of ez, then the requtred modulus of elasticity is
E¿ =
The increased factor is
sz
ez
=
k =
1 - v
E
(1 - 2v)(1 + v)
E¿
1 - v
=
E
(1 - 2v)(1 + v)
=
1 - 0.3
[1 - 2(0.3)](1 + 0.3)
= 1.35
Ans.
793
y
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10–59. A material is subjected to plane stress. Express
the distortion-energy theory of failure in terms of sx , sy ,
and txy .
Maximum distortion energy theory:
(s21 - s1 s2 + s22) = s2Y
s1,2 =
sx + sy
2
Let a =
;
sx + sy
2
s1 = a + b;
A
a
(1)
sx - sy
2
and b =
A
a
2
2
b + txy
sx - sy
2
2
2
b + txy
s2 = a - b
s21 = a2 + b2 + 2 a b;
s22 = a2 + b2 - 2 a b
s1 s2 = a2 - b2
From Eq. (1)
(a2 + b2 + 2 a b - a2 + b2 + a2 + b2 - 2 a b) = s2y
(a2 + 3 b2) = s2Y
(sx + sy)2
4
+ 3
(sx - sy)2
4
+ 3 t2xy = s2Y
s2x + s2y - sxsy + 3 t2xy = s2Y
Ans.
*10–60. A material is subjected to plane stress. Express
the maximum-shear-stress theory of failure in terms of sx ,
sy , and txy . Assume that the principal stresses are of
different algebraic signs.
Maximum shear stress theory:
|s1 - s2| = sY
s1,2 =
sx + sy
2
` s1 - s2 ` = 2
(1)
;
A
a
A
a
sx - sy
2
sx - sy
2
2
2
b + txy
2
2
b + txy
From Eq. (1)
4 ca
sx - sy
2
2
b + t2xy d = s2Y
2
(sx - sy) + 4 t2xy = s2Y
Ans.
794
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An aluminum alloy 6061-T6 is to be used for
a solid drive shaft such that it transmits 40 hp at 2400
rev>min. Using a factor of safety of 2 with respect to
yielding, determine the smallest-diameter shaft that can be
selected based on the maximum-shear-stress theory.
•10–61.
v = a2400
T =
2p rad 1 min
rev
ba
ba
b = 80 p rad>s
min
rev
60s
40 (550) (12)
P
3300 #
=
=
lb in.
p
v
80 p
Tc
J
Applying t =
t =
A 3300
p B c
p
2
=
c4
6600
p3 c3
The principal stresses:
s1 = t =
6600
;
p2 c3
s2 = -t =
6600
p2 c3
Maximum shear stress theory: Both principal stresses have opposite sign, hence,
` s1 - s2 ` =
2a
sY
;
F.S.
37 (103)
6600
b = `
`
2 3
2
pc
c = 0.4166 in.
d = 0.833 in.
Ans.
10–62. Solve Prob. 10–61 using the maximum-distortionenergy theory.
v = a2400
T =
2p rad 1 min
rev
ba
ba
b = 80 p rad>s
min
rev
60s
40 (550) (12)
P
3300
lb.in.
=
=
p
v
80 p
Applying t =
t =
A 3300
p B c
p
2
c4
=
Tc
J
6600
p2 c3
The principal stresses:
s1 = t =
6600
;
p2 c3
s2 = - t = -
6600
p2 c3
The maximum distortion-energy theory:
s21 - s1 s2 + s22 = a
3B
sY 2
b
F.S.
37(103) 2
6600 2
=
a
b
R
2
p2 c3
c = 0.3971 in.
d = 0.794 in.
Ans.
795
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10–63. An aluminum alloy is to be used for a drive shaft
such that it transmits 25 hp at 1500 rev>min. Using a factor
of safety of 2.5 with respect to yielding, determine the
smallest-diameter shaft that can be selected based on the
maximum-distortion-energy theory. sY = 3.5 ksi.
1500(2p)
= 50p
60
T =
P
v
T =
25(550)(12)
3300
=
p
50p
t =
Tc
,
J
t =
3300
p c
p 4
2c
s1 =
v =
J =
=
p 4
c
2
6600
p2c3
6600
p2c3
s2 =
s21 - s1 s2 + s22 = a
3a
-6600
p2c3
sY 2
b
F.S.
3.5(103) 2
6600 2
b
=
a
b
2.5
p2c3
c = 0.9388 in.
d = 1.88 in.
Ans.
*10–64. A bar with a square cross-sectional area is made
of a material having a yield stress of sY = 120 ksi. If the bar
is subjected to a bending moment of 75 kip # in., determine
the required size of the bar according to the maximumdistortion-energy theory. Use a factor of safety of 1.5 with
respect to yielding.
Normal and Shear Stress: Applying the flexure formula,
s =
75 A a2 B
450
Mc
= 1 4 = 3
I
a
12 a
In-Plane Principal Stress: Since no shear stress acts on the element
s1 = sx =
450
a3
s2 = sy = 0
Maximum Distortion Energy Theory:
s21 - s1 s2 + s22 = s2allow
a
120 2
450 2
b - 0 + 0 = a
b
3
1.5
a
a = 1.78 in.
Ans.
796
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Solve Prob. 10–64 using the maximum-shearstress theory.
•10–65.
Normal and Shear Stress: Applying the flexure formula,
s =
75 A a2 B
450
Mc
= 1 4 = 3
I
a
a
12
In-Plane Principal Stress: Since no shear stress acts on the element.
s1 = sx =
450
a3
s2 = sx = 0
Maximum Shear Stress Theory:
|s2| = 0 6 sallow =
120
= 80.0 ksi
1.5
(O.K!)
|s1| = sallow
120
450
=
1.5
a3
a = 1.78 in.
Ans.
10–66. Derive an expression for an equivalent torque Te
that, if applied alone to a solid bar with a circular cross
section, would cause the same energy of distortion as
the combination of an applied bending moment M and
torque T.
t =
Te c
J
Principal stress:
s1 = tx ¿
ud =
s2 = -t
1 + v 2
(s1 - s1 s2 + s22)
3E
(ud)1 =
1 + v
1 + v 3 T2x c2
b
( 3 t2) =
a
3E
3E
J2
Bending moment and torsion:
s =
Mc
;
I
t =
Tc
J
Principal stress:
s1, 2 =
s1 =
s + 0
s - 0 2
2
;
a
b + t
2
A
2
s
s2
+
+ t2 ;
2
A4
s2 =
s
s2
+ t2
2
A4
797
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10–66. Continued
Let a =
s
2
b =
s2
+ t2
A4
s21 = a2 + b2 + 2 a b
s1 s2 = a2 - b2
s22 = a2 + b2 - 2 a b
s21 - s1 s2 + s22 = 3 b2 + a2
1 + v 2
(s1 - s1 s2 + s22)
3E
ud =
(ud)2 =
=
1 + v
1 + v 3 s2
s2
(3 b2 + a2) =
a
+ 3t2 +
b
3E
3E
4
4
c2(1 + v) M2
3 T2
1 + v 2
b
(s + 3 t2) =
a 2 +
3E
3E
I
J2
(ud)1 = (ud)2
c3(1 + v) 3 Tx 2
c2(1 + v) M2
3 T2
=
+
b
a
3E
3E
J2
I2
J2
For circular shaft
J
=
I
p
3
p
4
c4
c4
=2
Te =
J2 M2
+ T2
A I2 3
Te =
4 2
M + T2
A3
Ans.
10–67. Derive an expression for an equivalent bending
moment Me that, if applied alone to a solid bar with a
circular cross section, would cause the same energy of
distortion as the combination of an applied bending
moment M and torque T.
Principal stresses:
s1 =
Me c
;
I
ud =
1 + v 2
(s1 - s1 s2 + s22)
3E
(ud)1 =
s2 = 0
1 + v M2e c2
a 2 b
3E
I
(1)
798
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10–67. Continued
Principal stress:
s - 0 2
s + 0
3
;
a
b + t
2
A
2
s1, 2 =
s
s2
+
+ t2;
2
A4
s1 =
s2 =
s
s2
+ t2
2
A4
Distortion Energy:
s
s2
+ t2
,b =
A4
2
Let a =
s21 = a2 + b2 + 2 a b
s1 s2 = a2 - b2
s22 = a2 + b2 - 2 a b
s22 - s1 s2 + s22 = 3 b2 + a2
Apply s =
(ud)2 =
=
Mc
;
I
t =
Tc
J
1 + v
1 + v s2
3s2
(3 b2 + a2) =
a
+
+ 3 t2 b
3E
3E
4
4
1 + v 2
3 T2 c2
1 + v M2 c2
b
(s + 3 t2) =
a 2 +
3E
3E
I
J2
(2)
Equating Eq. (1) and (2) yields:
(1 + v) Me c2
1 + v M2 c2
3T2 c2
b
a 2 b =
a 2 +
3E
3E
I
I
J2
M2e
2
I
=
M1
3 T2
+
2
I
J2
M2e = M1 + 3 T2 a
I 2
b
J
For circular shaft
I
=
J
p
4
p
2
c4
c4
=
1
2
1 2
Hence, M2e = M2 + 3 T2 a b
2
Me =
A
M2 +
3 2
T
4
Ans.
799
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Page 800
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*10–68. The short concrete cylinder having a diameter of
50 mm is subjected to a torque of 500 N # m and an axial
compressive force of 2 kN. Determine if it fails according to
the maximum-normal-stress theory. The ultimate stress of
the concrete is sult = 28 MPa.
A =
p
(0.05)2 = 1.9635(10 - 3) m2
4
J =
p
(0.025)4 = 0.61359(10 - 4) m4
2
2 kN
500 N⭈m
500 N⭈m
2 kN
3
s =
2(10 )
P
= 1.019 MPa
=
A
1.9635(10 - 3)
t =
500(0.025)
Tc
= 20.372 MPa
=
J
0.61359(10 - 6)
sx = 0
sy = -1.019 MPa
sx + sy
s1, 2 =
s1,2 =
2
;
A
a
sx - sy
2
txy = 20.372 MPa
2
2
b + txy
0 - 1.018
0 - (-1.019) 2
2
;
a
b + 20.372
2
A
2
s1 = 19.87 MPa
s2 = -20.89 MPa
Failure criteria:
|s1| 6 salt = 28 MPa
OK
|s2| 6 salt = 28 MPa
OK
No.
Ans.
Cast iron when tested in tension and compression
has an ultimate strength of 1sult2t = 280 MPa and
1sult2c = 420 MPa, respectively. Also, when subjected to
pure torsion it can sustain an ultimate shear stress of
tult = 168 MPa. Plot the Mohr’s circles for each case and
establish the failure envelope. If a part made of this
material is subjected to the state of plane stress shown,
determine if it fails according to Mohr’s failure criterion.
120 MPa
•10–69.
100 MPa
220 MPa
s1 = 50 + 197.23 = 247 MPa
s2 = 50 - 197.23 = -147 MPa
The principal stress coordinate is located at point A which is outside the shaded
region. Therefore the material fails according to Mohr’s failure criterion.
Yes.
Ans.
800
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10–69. Continued
10–70. Derive an expression for an equivalent bending
moment Me that, if applied alone to a solid bar with a
circular cross section, would cause the same maximum
shear stress as the combination of an applied moment M
and torque T. Assume that the principal stresses are of
opposite algebraic signs.
Bending and Torsion:
4M
Mc
Mc
;
= p 4 =
I
c
p c3
4
s =
t =
2T
Tc
Tc
= p 4 =
J
c
p
c3
2
The principal stresses:
s1, 2 =
=
tabs
max
sx + sy
2
;
A
a
sx - sy
2
2
2
b + txy =
4M
pc3
+ 0
2
¢pc
4M
;
3
Q
- 0
2
≤ + a
2
2T
3
pc
b
2
2
2M
;
2M2 + T2
p c3
p c3
= s1 - s2 = 2c
2
2M2 + T2 d
p c3
(1)
Pure bending:
s1 =
tabs
max
4 Me
Me c
Mc
;
= p 4 =
I
c
p c3
4
= s1 - s2 =
s2 = 0
4 Me
(2)
p c3
Equating Eq. (1) and (2) yields:
4 Me
4
2M2 + T2 =
p c3
p c3
Me = 2M2 + T2
Ans.
801
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10–71. The components of plane stress at a critical point
on an A-36 steel shell are shown. Determine if failure
(yielding) has occurred on the basis of the maximum-shearstress theory.
60 MPa
40 MPa
In accordance to the established sign convention, sx = 70 MPa, sy = -60 MPa and
txy = 40 MPa.
s1, 2 =
=
sx + sy
2
;
A
a
sx - sy
2
70 MPa
2
2
b + txy
70 + (-60)
70 - (-60) 2
2
;
c
d + 40
2
A
2
= 5 ; 25825
s2 = -71.32 MPa
s1 = 81.32 MPa
In this case, s1 and s2 have opposite sign. Thus,
|s1 - s2| = |81.32 - (-71.32)| = 152.64 MPa 6 sy = 250 MPa
Based on this result, the steel shell does not yield according to the maximum shear
stress theory.
*10–72. The components of plane stress at a critical point
on an A-36 steel shell are shown. Determine if failure
(yielding) has occurred on the basis of the maximumdistortion-energy theory.
60 MPa
40 MPa
In accordance to the established sign convention, sx = 70 MPa, sy = -60 MPa and
txy = 40 MPa.
s1, 2 =
=
sx + sy
2
;
A
a
sx - sy
2
2
2
b + txy
70 + ( -60)
70 - (-60) 2
2
;
c
d + 40
2
A
2
= 5 ; 25825
s1 = 81.32 MPa
s2 = -71.32 MPa
s1 2 - s1 s2 + s2 2 = 81.322 - 81.32(-71.32) + (-71.32)2 = 17,500 6 sy 2 = 62500
Based on this result, the steel shell does not yield according to the maximum
distortion energy theory.
802
70 MPa
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If the 2-in. diameter shaft is made from brittle
material having an ultimate strength of sult = 50 ksi for
both tension and compression, determine if the shaft fails
according to the maximum-normal-stress theory. Use a
factor of safety of 1.5 against rupture.
•10–73.
30 kip
4 kip · ft
Normal Stress and Shear Stresses. The cross-sectional area and polar moment of
inertia of the shaft’s cross-section are
A = p A 12 B = pin2
J =
p 4
p
A 1 B = in4
2
2
The normal stress is caused by axial stress.
s =
N
30
= -9.549 ksi
= p
A
The shear stress is contributed by torsional shear stress.
t =
4(12)(1)
Tc
=
= 30.56 ksi
p
J
2
The state of stress at the points on the surface of the shaft is represented on the
element shown in Fig. a.
In-Plane Principal Stress. sx = -9.549 ksi, sy = 0 and txy = -30.56 ksi. We have
s1, 2 =
=
sx + sy
2
;
A
a
sx - sy
2
2
2
b + txy
-9.549 - 0 2
-9.549 + 0
2
;
a
b + (-30.56)
2
A
2
= (-4.775 ; 30.929) ksi
s1 = 26.15 ksi
s2 = -35.70 ksi
Maximum Normal-Stress Theory.
sallow =
sult
50
=
= 33.33 ksi
F.S.
1.5
|s1| = 26.15 ksi 6 sallow = 33.33 ksi
(O.K.)
|s2| = 35.70 ksi 7 sallow = 33.33 ksi
(N.G.)
Based on these results, the material fails according to the maximum normal-stress
theory.
803
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10–74. If the 2-in. diameter shaft is made from cast
iron having tensile and compressive ultimate strengths
of 1sult2t = 50 ksi and 1sult2c = 75 ksi, respectively,
determine if the shaft fails in accordance with Mohr’s
failure criterion.
Normal Stress and Shear Stresses. The cross-sectional area and polar moment of
inertia of the shaft’s cross-section are
A = p A 12 B = p in2
J =
p 4
p
A 1 B = in4
2
2
The normal stress is contributed by axial stress.
s =
N
30
= = -9.549 ksi
p
A
The shear stress is contributed by torsional shear stress.
t =
4(12)(1)
Tc
=
= 30.56 ksi
p
J
2
The state of stress at the points on the surface of the shaft is represented on the
element shown in Fig. a.
In-Plane Principal Stress. sx = -9.549 ksi, sy = 0, and txy = -30.56 ksi. We have
s1, 2 =
=
sx + sy
2
;
A
a
sx - sy
2
2
2
b + txy
-9.549 - 0 2
-9.549 + 0
2
;
a
b + (-30.56)
2
A
2
= (-4.775 ; 30.929) ksi
s1 = 26.15 ksi
s2 = -35.70 ksi
Mohr’s Failure Criteria. As shown in Fig. b, the coordinates of point A, which
represent the principal stresses, are located inside the shaded region. Therefore, the
material does not fail according to Mohr’s failure criteria.
804
30 kip
4 kip · ft
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10–75. If the A-36 steel pipe has outer and inner
diameters of 30 mm and 20 mm, respectively, determine the
factor of safety against yielding of the material at point A
according to the maximum-shear-stress theory.
900 N
150 mm
A
100 mm
200 mm
Internal Loadings. Considering the equilibrium of the free - body diagram of the
post’s right cut segment Fig. a,
©Fy = 0; Vy + 900 - 900 = 0
Vy = 0
T = -360 N # m
©Mx = 0; T + 900(0.4) = 0
©Mz = 0; Mz + 900(0.15) - 900(0.25) = 0 Mz = 90 N # m
Section Properties. The moment of inertia about the z axis and the polar moment of
inertia of the pipe’s cross section are
Iz =
p
A 0.0154 - 0.014 B = 10.15625p A 10 - 9 B m4
4
J =
p
A 0.0154 - 0.014 B = 20.3125p A 10 - 9 B m4
2
Normal Stress and Shear Stress. The normal stress is contributed by bending stress.
Thus,
sY = -
MyA
90(0.015)
= = -42.31MPa
Iz
10.15625p A 10 - 9 B
The shear stress is contributed by torsional shear stress.
t =
360(0.015)
Tc
=
= 84.62 MPa
J
20.3125p A 10 - 9 B
The state of stress at point A is represented by the two - dimensional element shown
in Fig. b.
In - Plane Principal Stress. sx = -42.31 MPa, sz = 0 and txz = 84.62 MPa. We have
s1, 2 =
=
sx + sz
2
;
A
a
sx - sz
2
2
b + txz
2
-42.31 + 0
-42.31 - 0 2
2
;
a
b + 84.62
2
A
2
= (-21.16 ; 87.23) MPa
s1 = 66.07 MPa
s2 = -108.38 MPa
805
200 mm
900 N
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10–75. Continued
Maximum Shear Stress Theory. s1 and s2 have opposite signs. This requires
|s1 - s2| = sallow
66.07 - (-108.38) = sallow
sallow = 174.45 MPa
The factor of safety is
F.S. =
sY
250
= 1.43
=
sallow
174.45
Ans.
806
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*10–76. If the A-36 steel pipe has an outer and inner
diameter of 30 mm and 20 mm, respectively, determine the
factor of safety against yielding of the material at point A
according to the maximum-distortion-energy theory.
900 N
150 mm
A
100 mm
200 mm
Internal Loadings: Considering the equilibrium of the free - body diagram of the
pipe’s right cut segment Fig. a,
©Fy = 0; Vy + 900 - 900 = 0
Vy = 0
T = -360 N # m
©Mx = 0; T + 900(0.4) = 0
©Mz = 0; Mz + 900(0.15) - 900(0.25) = 0 Mz = 90 N # m
Section Properties. The moment of inertia about the z axis and the polar moment of
inertia of the pipe’s cross section are
Iz =
p
A 0.0154 - 0.014 B = 10.15625p A 10 - 9 B m4
4
J =
p
A 0.0154 - 0.014 B = 20.3125p A 10 - 9 B m4
2
Normal Stress and Shear Stress. The normal stress is caused by bending stress. Thus,
sY = -
MyA
90(0.015)
= = -42.31MPa
Iz
10.15625p A 10 - 9 B
The shear stress is caused by torsional stress.
t =
360(0.015)
Tc
=
= 84.62 MPa
J
20.3125p A 10 - 9 B
The state of stress at point A is represented by the two -dimensional element shown
in Fig. b.
In - Plane Principal Stress. sx = -42.31 MPa, sz = 0 and txz = 84.62 MPa. We have
s1, 2 =
=
sx + sz
2
;
A
a
sx - sz
2
2
b + txz
2
-42.31 - 0 2
-42.31 + 0
2
;
a
b + 84.62
2
A
2
= (-21.16 ; 87.23) MPa
s1 = 66.07 MPa
s2 = -108.38 MPa
807
200 mm
900 N
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10–76. Continued
Maximum Distortion Energy Theory.
s1 2 - s1s2 + s2 2 = sallow 2
66.072 - 66.07(-108.38) + (-108.38)2 = sallow 2
sallow = 152.55 MPa
Thus, the factor of safety is
F.S. =
sY
250
= 1.64
=
sallow
152.55
Ans.
808
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The element is subjected to the stresses shown. If
sY = 36 ksi, determine the factor of safety for the loading
based on the maximum-shear-stress theory.
•10–77.
sx = 4 ksi
s1, 2 =
=
sy = -12 ksi
sx + sy
2
;
A
a
sx - sy
2
txy = -8 ksi
4 ksi
2
2
b + txy
8 ksi
4 - (-12) 2
4 - 12
2
;
a
b + (-8)
2
A
2
s1 = 7.314 ksi
s2 = -15.314 ksi
tabsmax =
7.314 - (-15.314)
s1 - s2
=
= 11.314 ksi
2
2
tallow =
sY
36
=
= 18 ksi
2
2
F.S. =
12 ksi
tallow
18
=
= 1.59
abs
tmax
11.314
Ans.
10–78. Solve Prob. 10–77 using the maximum-distortionenergy theory.
sx = 4 ksi
s1, 2 =
=
sy = -12 ksi
sx + sy
2
;
A
a
sx - sy
txy = -8 ksi
4 ksi
2
2
b + txy
8 ksi
4 - (-12) 2
4 - 12
2
;
a
b + (-8)
2
A
2
s1 = 7.314 ksi
s2 = -15.314 ksi
s1 2 - s1 s2 + s2 2 = a
F.S. =
2
12 ksi
sY 2
b
F.S.
362
= 1.80
A (7.314)2 - (7.314)(-15.314) + (-15.314)2
Ans.
809
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10–79. The yield stress for heat-treated beryllium copper
is sY = 130 ksi. If this material is subjected to plane stress
and elastic failure occurs when one principal stress is 145 ksi,
what is the smallest magnitude of the other principal stress?
Use the maximum-distortion-energy theory.
Maximum Distortion Energy Theory : With s1 = 145 ksi,
s21 - s1 s2 + s22 = s2Y
1452 - 145s2 + s22 = 1302
s22 - 145s2 + 4125 = 0
s2 =
-(-145) ; 2( -145)2 - 4(1)(4125)
2(1)
= 72.5 ; 33.634
Choose the smaller root, s2 = 38.9 ksi
Ans.
*10–80. The plate is made of hard copper, which yields at
sY = 105 ksi. Using the maximum-shear-stress theory,
determine the tensile stress sx that can be applied to the
plate if a tensile stress sy = 0.5sx is also applied.
s1 = sx
sy ⫽ 0.5sx
sx
1
s2 = sx
2
|s1| = sY
sx = 105 ksi
Ans.
Solve Prob. 10–80 using the maximum-distortionenergy theory.
•10–81.
sy ⫽ 0.5sx
s1 = sx
s2 =
sx
2
sx
s21 - s1 s2 + s22 = s2Y
s2x -
s2x
s2x
+
= (105)2
2
4
sx = 121 ksi
Ans.
810
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10–82. The state of stress acting at a critical point on the
seat frame of an automobile during a crash is shown in the
figure. Determine the smallest yield stress for a steel that
can be selected for the member, based on the maximumshear-stress theory.
Normal and Shear Stress: In accordance with the sign convention.
sx = 80 ksi
sy = 0
25 ksi
txy = 25 ksi
80 ksi
In - Plane Principal Stress: Applying Eq. 9-5.
s1,2 =
=
sx + sy
2
;
A
a
sx - sy
2
2
2
b + txy
80 - 0 2
80 + 0
2
;
a
b + 25
2
A
2
= 40 ; 47.170
s1 = 87.170 ksi
s2 = -7.170 ksi
Maximum Shear Stress Theory: s1 and s2 have opposite signs so
|s1 - s2| = sY
|87.170 - (-7.170)| = sY
sY = 94.3 ksi
Ans.
10–83. Solve Prob. 10–82 using the maximum-distortionenergy theory.
Normal and Shear Stress: In accordance with the sign convention.
sx = 80 ksi
sy = 0
txy = 25 ksi
In - Plane Principal Stress: Applying Eq. 9-5.
s1,2 =
=
sx + sy
2
;
A
a
25 ksi
2
sx - s
2
b + txy
2
80 ksi
80 - 0 2
80 + 0
2
;
a
b + 25
2
A
2
= 40 ; 47.170
s1 = 87.170 ksi
s2 = -7.170 ksi
Maximum Distortion Energy Theory:
s21 - s1s2 + s22 = s2Y
87.1702 - 87.170(-7.170) + (-7.170)2 = s2Y
sY = 91.0 ksi
Ans.
811
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*10–84. A bar with a circular cross-sectional area is made
of SAE 1045 carbon steel having a yield stress of
sY = 150 ksi. If the bar is subjected to a torque of
30 kip # in. and a bending moment of 56 kip # in., determine
the required diameter of the bar according to the
maximum-distortion-energy theory. Use a factor of safety
of 2 with respect to yielding.
Normal and Shear Stresses: Applying the flexure and torsion formulas.
56 A d2 B
Mc
1792
=
=
p d 4
I
pd3
A B
s =
4
t =
Tc
=
J
2
30 A d2 B
A B
d 4
2
p
2
=
480
pd3
The critical state of stress is shown in Fig. (a) or (b), where
sx =
1792
pd3
sy = 0
txy =
480
pd3
In - Plane Principal Stresses : Applying Eq. 9-5,
s1,2 =
=
=
s1 =
sx + sy
2
1792
3
pd
;
A
+ 0
2
;
D
a
¢
sx - sy
2
1792
3
pd
- 0
2
2
2
b + txy
≤ + a
2
480 2
b
pd3
1016.47
896
;
pd3
pd3
1912.47
pd3
s2 = -
120.47
pd3
Maximum Distortion Energy Theory :
s21 - s1s2 + s22 = s2allow
a
1912.47
120.47
120.47 2
150 2
1912.47 2
b - a
bab + ab = a
b
3
3
3
3
2
pd
pd
pd
pd
d = 2.30 in.
Ans.
812
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The state of stress acting at a critical point on a
machine element is shown in the figure. Determine the
smallest yield stress for a steel that might be selected for the
part, based on the maximum-shear-stress theory.
•10–85.
10 ksi
The Principal stresses:
s1,2 =
=
sx + sy
2
;
A
4 ksi
a
sx - sy
2
2
2
b + txy
8 ksi
8 - (-10) 2
8 - 10
2
;
a
b + 4
2
A
2
s2 = -10.8489 ksi
s1 = 8.8489 ksi
Maximum shear stress theory: Both principal stresses have opposite sign. hence,
8.8489 - (-10.8489) = sY
|s1 - s2| = sY
sY = 19.7 ksi
Ans.
10–86. The principal stresses acting at a point on a thinwalled cylindrical pressure vessel are s1 = pr>t, s2 = pr>2t,
and s3 = 0. If the yield stress is sY, determine the maximum
value of p based on (a) the maximum-shear-stress theory and
(b) the maximum-distortion-energy theory.
a) Maximum Shear Stress Theory: s1 and s2 have the same signs, then
|s2| = sg
|s1| = sg
2
2
pr
2 = sg
2t
pr
2 = sg
t
p =
2t
s
r g
p =
t
s (Controls!)
r g
Ans.
b) Maximum Distortion Energy Theory :
s21 - s1s2 + s22 = s2g
a
pr pr
pr 2
pr 2
b - a b a b + a b = s2g
t
t
2t
2t
p =
2t
23r
Ans.
sg
813
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10–87. If a solid shaft having a diameter d is subjected to
a torque T and moment M, show that by the maximumshear-stress theory the maximum allowable shear stress is
tallow = 116>pd322M2 + T2. Assume the principal stresses
to be of opposite algebraic signs.
T
T
M
M
Section properties :
I =
p d 4
pd4
a b =
;
4 2
64
J =
p d 4
pd4
a b =
2 2
32
Thus,
M(d2 )
32 M
Mc
=
=
p d4
I
pd3
s =
64
T (d2 )
Tc
16 T
t =
=
=
p d4
J
pd3
32
The principal stresses :
s1,2 =
=
sx + sy
2
;
A
a
sx - sy
2
2
2
b + txy
16 M
16 M
16 M 2
16 T 2
16
;
;
2M2 + T2
a
b + a
b =
3
3
A pd
pd
p d3
pd3
p d3
Assume s1 and s2 have opposite sign, hence,
tallow
2 C 163 2M2 + T2 D
s1 - s2
16
pd
=
2M2 + T2
=
=
2
2
pd3
QED
*10–88. If a solid shaft having a diameter d is subjected to a
torque T and moment M, show that by the maximum-normalstress theory the maximum allowable principal stress is
sallow = 116>pd321M + 2M2 + T22.
T
M
M
Section properties :
I =
p d4
;
64
p d4
32
J =
Stress components :
s =
M (d2 )
Mc
32 M
;
= p 4 =
I
p d3
d
64
t =
T(d2 )
Tc
16 T
= p 4 =
J
p d3
d
32
The principal stresses :
s1,2 =
=
sx + sy
2
;
A
a
sx - sy
2
2
2
b + txy =
32 M
3
pd
2
¢ pd
32 M
+ 0
3
;
D
- 0
2
≤ + a
2
16 T 2
b
p d3
16
16 M
;
2M2 + T2
p d3
p d3
Maximum normal stress theory. Assume s1 7 s2
sallow = s1 =
=
16
16 M
+
2M2 + T2
p d3
p d3
16
[M + 2M2 + T2]
p d3
QED
814
T
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The shaft consists of a solid segment AB and a
hollow segment BC, which are rigidly joined by the
coupling at B. If the shaft is made from A-36 steel,
determine the maximum torque T that can be applied
according to the maximum-shear-stress theory. Use a factor
of safety of 1.5 against yielding.
•10–89.
A
B
T
C
Shear Stress: This is a case of pure shear, and the shear stress is contributed by
p
torsion. For the hollow segment, Jh =
A 0.054 - 0.044 B = 1.845p A 10 - 6 B m4. Thus,
2
(tmax)h =
T(0.05)
Tch
=
= 8626.28T
Jh
1.845p A 10 - 6 B
For the solid segment, Js =
(tmax)s =
p
A 0.044 B = 1.28p A 10 - 6 B m4. Thus,
2
T(0.04)
Tcs
= 9947.18T
=
Js
1.28p A 10 - 6 B
By comparision, the points on the surface of the solid segment are critical and their
state of stress is represented on the element shown in Fig. a.
In - Plane Principal Stress. sx = sy = 0 and txy = 9947.18T. We have
s1,2 =
=
sx + sy
2
;
C
¢
sx - sy
2
≤ + t2xy
2
0 - 0 2
0 + 0
;
¢
≤ + (9947.18T)2
2
C
2
s1 = 9947.18T
s2 = -9947.18T
Maximum Shear Stress Theory.
sallow =
80 mm
sY
250
=
= 166.67 MPa
F.S.
1.5
Since s1 and s2 have opposite sings,
|s1 - s2| = sallow
9947.18T - (-9947.18T) = 166.67 A 106 B
T = 8377.58 N # m = 8.38 kN # m
Ans.
815
80 mm
100 mm
T
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10–90. The shaft consists of a solid segment AB and a
hollow segment BC, which are rigidly joined by the
coupling at B. If the shaft is made from A-36 steel,
determine the maximum torque T that can be applied
according to the maximum-distortion-energy theory. Use a
factor of safety of 1.5 against yielding.
A
B
T
C
Shear Stress. This is a case of pure shear, and the shear stress is contributed by
p
torsion. For the hollow segment, Jh =
A 0.054 - 0.044 B = 1.845p A 10 - 6 B m4. Thus,
2
(tmax)h =
T(0.05)
Tch
=
= 8626.28T
Jh
1.845p A 10 - 6 B
For the solid segment, Js =
(tmax)s =
p
A 0.044 B = 1.28p A 10 - 6 B m4. Thus,
2
T(0.04)
Tcs
=
= 9947.18T
Js
1.28p A 10 - 6 B
By comparision, the points on the surface of the solid segment are critical and their
state of stress is represented on the element shown in Fig. a.
In - Plane Principal Stress. sx = sy = 0 and txy = 9947.18T. We have
s1,2 =
=
sx + sy
2
;
C
¢
sx - sy
2
≤ + t2xy
2
0 + 0
0 - 0 2
;
¢
≤ + (9947.18T)2
2
C
2
s1 = 9947.18T
s2 = -9947.18T
Maximum Distortion Energy Theory.
sallow =
80 mm
sY
250
=
= 166.67 MPa
F.S.
1.5
Then,
s1 2 - s1s2 + s2 2 = sallow 2
(9947.18T)2 - (9947.18T)( -9947.18T) + (-9947.18T)2 = C 166.67 A 106 B D 2
T = 9673.60 N # m = 9.67 kN # m
Ans.
816
80 mm
100 mm
T
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10–91. The internal loadings at a critical section along the
steel drive shaft of a ship are calculated to be a torque of
2300 lb # ft, a bending moment of 1500 lb # ft, and an axial
thrust of 2500 lb. If the yield points for tension and shear are
sY = 100 ksi and tY = 50 ksi, respectively, determine the
required diameter of the shaft using the maximum-shearstress theory.
2300 lb⭈ft
2500 lb
p
I = c4
4
A = p c2
sA =
p
J = c4
2
1500(12)(c)
2500
72 000
P
Mc
2500
b = -a
+
+
b
+
= -a
pc4
A
I
p c2
p c2
p c3
4
tA =
2300(12)(c)
55 200
Tc
=
=
p c4
J
p c3
2
s1,2 =
sx + sy
= -a
2
;
A
a
sx - sy
2
2
2
b + txy
2500c + 72 000 2
55200 2
2500 c + 72 000
b ;
a
b + a
b
3
3
A
2p c
2p c
p c3
(1)
Assume s1 and s2 have opposite signs:
|s1 - s2| = sg
55 200 2
2500c + 72 000 2
3
b + a
b = 100(10 )
3
A
2p c
p c3
2
a
(2500c + 72000)2 + 1104002 = 10 000(106)p2 c6
6.25c2 + 360c + 17372.16 - 10 000p2 c6 = 0
By trial and error:
c = 0.750 57 in.
Substitute c into Eq. (1):
s1 = 22 193 psi
s2 = -77 807 psi
s1 and s2 are of opposite signs
OK
Therefore,
d = 1.50 in.
Ans.
817
1500 lb⭈ft
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*10–92. The gas tank has an inner diameter of 1.50 m and
a wall thickness of 25 mm. If it is made from A-36 steel and
the tank is pressured to 5 MPa, determine the factor of
safety against yielding using (a) the maximum-shear-stress
theory, and (b) the maximum-distortion-energy theory.
(a) Normal Stress. Since
0.75
r
=
= 30 7 10, thin - wall analysis can be used.We have
t
0.025
s1 = sh =
pr
5(0.75)
=
= 150 MPa
t
0.025
s2 = slong =
pr
5(0.75)
=
= 75 MPa
2t
2(0.025)
Maximum Shear Stress Theory. s1 and s2 have the sign. Thus,
|s1| = sallow
sallow = 150 MPa
The factor of safety is
F.S. =
sY
250
=
= 1.67
sallow
150
Ans.
(b) Maximum Distortion Energy Theory.
s1 2 - s1s2 + s2 2 = sallow 2
1502 - 150(75) + 752 = sallow 2
sallow = 129.90 MPa
The factor of safety is
F.S. =
sY
250
= 1.92
=
sallow
129.90
Ans.
818
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Page 819
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The gas tank is made from A-36 steel and
has an inner diameter of 1.50 m. If the tank is designed
to withstand a pressure of 5 MPa, determine the required
minimum wall thickness to the nearest millimeter using
(a) the maximum-shear-stress theory, and (b) maximumdistortion-energy theory. Apply a factor of safety of 1.5
against yielding.
•10–93.
(a) Normal Stress. Assuming that thin - wall analysis is valid, we have
s1 = sh =
5 A 106 B (0.75)
3.75 A 106 B
pr
=
=
t
t
t
s2 = slong =
5 A 106 B (0.75)
1.875 A 106 B
pr
=
=
2t
2t
t
Maximum Shear Stress Theory.
sallow =
250 A 106 B
sY
=
= 166.67 A 106 B Pa
FS.
1.5
s1 and s2 have the same sign. Thus,
|s1| = sallow
3.75 A 106 B
= 166.67 A 106 B
t
t = 0.0225 m = 22.5 mm
Since
Ans.
0.75
r
=
= 33.3 7 10, thin - wall analysis is valid.
t
0.0225
(b) Maximum Distortion Energy Theory.
sallow =
250 A 106 B
sY
=
= 166.67 A 106 B Pa
F.S.
1.5
Thus,
s1 2 - s1s2 + s2 2 = sallow 2
C
3.75 A 106 B
t
3.2476 A 106 B
t
2
S - C
3.75 A 106 B
t
SC
1.875 A 106 B
t
S + C
1.875 A 106 B
t
2
S = c166.67 A 106 B d
= 166.67 A 106 B
t = 0.01949 m = 19.5 mm
Since
2
Ans.
0.75
r
=
= 38.5 7 10, thin - wall analysis is valid.
t
0.01949
819
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Page 820
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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.
10–94. A thin-walled spherical pressure vessel has an
inner radius r, thickness t, and is subjected to an internal
pressure p. If the material constants are E and n, determine
the strain in the circumferential direction in terms of the
stated parameters.
s1 = s2 =
pr
2t
e1 = e2 = e =
e =
1
(s - vs)
E
pr
1 - v pr
1 - v
s =
a b =
(1 - v)
E
E
2t
2Et
Ans.
10–95. The strain at point A on the shell has components
Px = 250(10 - 6), Py = 400(10 - 6), gxy = 275(10 - 6), Pz = 0.
Determine (a) the principal strains at A, (b) the maximum
shear strain in the x–y plane, and (c) the absolute maximum
shear strain.
ex = 250(10 - 6)
A(250, 137.5)10 - 6
ey = 400(10 - 6)
gxy = 275(10 - 6)
y
A
gxy
2
= 137.5(10 - 6)
C(325, 0)10 - 6
R = a 2(325 - 250)2 + (137.5)2 b10 - 6 = 156.62(10 - 6)
a)
e1 = (325 + 156.62)10 - 6 = 482(10 - 6)
Ans.
e2 = (325 - 156.62)10 - 6 = 168(10 - 6)
Ans.
b)
g
max
in-plane
= 2R = 2(156.62)(10 - 6) = 313(10 - 6)
Ans.
c)
gabs
max
2
gabs
max
=
482(10 - 6)
2
= 482(10 - 6)
Ans.
820
x
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Page 821
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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.
*10–96. The principal plane stresses acting at a point are
shown in the figure. If the material is machine steel having a
yield stress of sY = 500 MPa, determine the factor of
safety with respect to yielding if the maximum-shear-stress
theory is considered.
100 MPa
150 MPa
Have, the in plane principal stresses are
s1 = sy = 100 MPa
s2 = sx = -150 MPa
Since s1 and s2 have same sign,
F.S =
sy
=
|s1 - s2|
500
= 2
|100 - (-150)|
Ans.
The components of plane stress at a critical point
on a thin steel shell are shown. Determine if failure
(yielding) has occurred on the basis of the maximumdistortion-energy theory. The yield stress for the steel is
sY = 650 MPa.
•10–97.
340 MPa
65 MPa
55 MPa
sx = -55 MPa
s1, 2 =
=
sx + sy
2
sy = 340 MPa
;
A
a
sx - sy
2
txy = 65 MPa
2
2
b + txy
-55 - 340 2
-55 + 340
2
;
a
b + 65
2
A
2
s1 = 350.42 MPa
s2 = -65.42 MPa
(s1 2 - s1s2 + s2 ) = [350.422 - 350.42(-65.42) + (-65.42)2]
= 150 000 6 s2Y = 422 500
OK
No.
Ans.
821
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Page 822
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10–98. The 60° strain rosette is mounted on a beam.
The following readings are obtained for each gauge:
Pa = 600110-62, Pb = -700110-62, and Pc = 350110-62.
Determine (a) the in-plane principal strains and (b) the
maximum in-plane shear strain and average normal strain. In
each case show the deformed element due to these strains.
a
60⬚
60⬚
b
Strain Rosettes (60º): Applying Eq. 10-15 with ex = 600 A 10 - 6 B ,
eb = -700 A 10
-6
c
B , ec = 350 A 10 B , ua = 150°, ub = -150° and uc = -90°,
-6
350 A 10 - 6 B = ex cos2 (-90°) + ey sin2(-90°) + gxy sin (-90°) cos ( -90°)
ey = 350 A 10 - 6 B
600 A 10 - 6 B = ex cos2 150° + 350 A 10 - 6 B sin2 150° + gxy sin 150° cos 150°
512.5 A 10 - 6 B = 0.75 ex - 0.4330 gxy
[1]
-787.5 A 10 - 6 B = 0.75ex + 0.4330 gxy
[2]
-700 A 10 - 6 B = ex cos2 ( -150°) + 350 A 10 - 6 B sin2(-150°) + gxy sin (-150°) cos (-150°)
Solving Eq. [1] and [2] yields ex = -183.33 A 10 - 6 B
gxy = -1501.11 A 10 - 6 B
Construction of she Circle: With ex = -183.33 A 10 - 6 B , ey = 350 A 10 - 6 B , and
gxy
= -750.56 A 10 - 6 B .
2
eavg =
ex + ey
2
= a
-183.33 + 350
b A 10 - 6 B = 83.3 A 10 - 6 B
2
Ans.
The coordinates for reference points A and C are
A( -183.33, -750.56) A 10 - 6 B
C(83.33, 0) A 10 - 6 B
The radius of the circle is
R = a 2(183.33 + 83.33)2 + 750.562 b A 10 - 6 B = 796.52 A 10 - 6 B
a)
In-plane Principal Strain: The coordinates of points B and D represent e1 and e2,
respectively.
e1 = (83.33 + 796.52) A 10 - 6 B = 880 A 10 - 6 B
Ans.
e2 = (83.33 - 796.52) A 10 - 6 B = -713 A 10 - 6 B
Ans.
Orientation of Principal Strain: From the circle,
tan 2uP1 =
750.56
= 2.8145
183.33 + 83.33
2uP2 = 70.44°
2uP1 = 180° - 2uP2
uP =
180° - 70.44°
= 54.8° (Clockwise)
2
Ans.
822
60⬚
10 Solutions 46060
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Page 823
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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.
10–98. Continued
b)
Maximum In - Plane Shear Strain: Represented by the coordinates of point E on
the circle.
g max
in-plane
2
g
max
in-plane
= -R = -796.52 A 10 - 6 B
= -1593 A 10 - 6 B
Ans.
Orientation of Maximum In-Plane Shear Strain: From the circle.
tan 2uP =
183.33 + 83.33
= 0.3553
750.56
uP = 9.78° (Clockwise)
Ans.
10–99. A strain gauge forms an angle of 45° with the axis
of the 50-mm diameter shaft. If it gives a reading of
P = -200110-62 when the torque T is applied to the shaft,
determine the magnitude of T. The shaft is made from
A-36 steel.
T
45⬚
Shear Stress. This is a case of pure shear, and the shear stress developed is
p
contributed by torsional shear stress. Here, J =
A 0.0254 B = 0.1953125p A 10 - 6 B m4.
2
Then
0.128 A 106 B T
T(0.025)
Tc
t =
=
=
p
J
0.1953125p A 10 - 6 B
T
The state of stress at points on the surface of the shaft can be represented by the
element shown in Fig. a.
Shear Strain: For pure shear ex = ey = 0. We obtain,
ea = ex cos2ua + ey sin2ua + gxysin ua cos ua
-200 A 10 - 6 B = 0 + 0 + gxy sin 45° cos 45°
gxy = -400 A 10 - 6 B
Shear Stress and Strain Relation: Applying Hooke’s Law for shear,
txy = Ggxy
-
0.128 A 106 B T
p
= 75 A 109 B C -400 A 10 - 6 B D
T = 736 N # m
Ans.
823
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Page 824
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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.
*10–100. The A-36 steel post is subjected to the forces
shown. If the strain gauges a and b at point A give readings
of Pa = 300110-62 and Pb = 175110-62, determine the
magnitudes of P1 and P2.
P1
4 in.
P2
a
A
c
Internal Loadings: Considering the equilibrium of the free - body diagram of the 1 in.
post’s segment, Fig. a,
P2 - V = 0
V = P2
+ c ©Fy = 0;
N - P1 = 0
N = P1
a + ©MO = 0;
M + P2(2) = 0
M = 2P2
Section Properties: The cross - sectional area and the moment of inertia about the
bending axis of the post’s cross - section are
A = 4(2) = 8 in2
I =
1
(2) A 43 B = 10.667 in4
12
Referring to Fig. b,
A Qy B A = x¿A¿ = 1.5(1)(2) = 3 in3
Normal and Shear Stress: The normal stress is a combination of axial and bending
stress.
sA =
2P2(12)(1)
MxA
P1
N
+
= +
= 2.25P2 - 0.125P1
A
I
8
10.667
The shear stress is caused by transverse shear stress.
tA =
VQA
P2(3)
=
= 0.140625P2
It
10.667(2)
Thus, the state of stress at point A is represented on the element shown in Fig. c.
Normal and Shear Strain: With ua = 90° and ub = 45°, we have
ea = ex cos2ua + ey sin2ua + gxysin ua cos ua
300 A 10 - 6 B = ex cos2 90° + ey sin2 90° + gxysin 90° cos 90°
ey = 300 A 10 - 6 B eb = ex cos2ub + ey sin2 ub + gxysin ub cos ub
175 A 10 - 6 B = ex cos2 45° + 300 A 10 - 6 B sin2 45° + gxy sin 45°cos 45°
ex + gxy = 50 A 10 - 6 B
(1)
824
A
1 in.
b 45⬚
A
+ ©F = 0;
:
x
2 in.
2 ft
c
Section c– c
10 Solutions 46060
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Page 825
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10–100. Continued
Since sy = sz = 0, ex = -vey = -0.32(300) A 10 - 6 B = -96 A 10 - 6 B
Then Eq. (1) gives
gxy = 146 A 10 - 6 B
Stress and Strain Relation: Hooke’s Law for shear gives
tx = Ggxy
0.140625P2 = 11.0 A 103 B C 146 A 10 - 6 B D
P2 = 11.42 kip = 11.4 kip
Ans.
Since sy = sz = 0, Hooke’s Law gives
sy = Eey
2.25(11.42) - 0.125P1 = 29.0 A 103 B C 300 A 10 - 6 B D
P1 = 136 kip
Ans.
825
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Page 826
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10–101. A differential element is subjected to plane strain
that has the following components: Px = 950110-62, Py =
420110-62, gxy = -325110-62. Use the strain-transformation
equations and determine (a) the principal strains and (b) the
maximum in-plane shear strain and the associated average
strain. In each case specify the orientation of the element
and show how the strains deform the element.
e1, 2 =
ex + ey
;
2
= c
A
a
ex - ey
2
2
2
b + gxy
950 - 420 2
-325 2
950 + 420
-6
;
a
b + a
b d(10 )
2
A
2
2
e1 = 996(10 - 6)
Ans.
e2 = 374(10 - 6)
Ans.
Orientation of e1 and e2 :
gxy
tan 2uP =
ex - ey
-325
950 - 420
=
uP = -15.76°, 74.24°
Use Eq. 10.5 to determine the direction of e1 and e2.
ex¿ =
ex + ey
+
2
ex - ey
2
cos 2u +
gxy
2
sin 2u
u = uP = -15.76°
ex¿ = b
( -325)
950 - 420
950 + 420
+
cos (-31.52°) +
sin (-31.52°) r (10 - 6) = 996(10 - 6)
2
2
2
uP1 = -15.8°
Ans.
uP2 = 74.2°
Ans.
b)
gmax
in-plane
2
gmax
in-plane
eavg =
ex - ey
A
a
= 2c
A
=
2
a
ex + ey
2
2
b + a
gxy
2
b
2
950 - 420 2
-325 2
-6
-6
b + a
b d(10 ) = 622(10 )
2
2
Ans.
= a
Ans.
950 + 420
b(10 - 6) = 685(10 - 6)
2
826
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Page 827
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10–101. Continued
Orientation of gmax :
-(ex - ey)
tan 2uP =
gxy
-(950 - 420)
-325
=
uP = 29.2° and uP = 119°
Ans.
Use Eq. 10.6 to determine the sign of
gx¿y¿
2
= -
ex - ey
sin 2u +
2
gxy
2
g
max
in-plane
:
cos 2u
u = uP = 29.2°
gx¿y¿ = 2c
-(950 - 420)
-325
sin (58.4°) +
cos (58.4°) d(10 - 6)
2
2
gxy = -622(10 - 6)
10–102. The state of plane strain on an element is
Px = 400110-62, Py = 200110-62, and gxy = -300110-62.
Determine the equivalent state of strain on an element at
the same point oriented 30° clockwise with respect to the
original element. Sketch the results on the element.
y
Pydy
dy
Stress Transformation Equations:
ex = 400 A 10 - 6 B
ey = 200 A 10 - 6 B
gxy = -300 A 10 - 6 B
u = -30°
ex¿ =
2
= B
+
ex - ey
2
2
2
sin 2u
400 + 200
400 - 200
-300
+
cos (-60°) + a
b sin (-60°) R A 10 - 6 B
2
2
2
= 480 A 10 - 6 B
gx¿y¿
cos 2u +
gxy
= -¢
Ans.
ex - ey
2
≤ sin 2u +
gxy
2
cos 2u
gx¿y¿ = [-(400 - 200) sin ( -60°) + (-300) cos ( -60°)] A 10 - 6 B
= 23.2 A 10 - 6 B
ey¿ =
ex + ey
= B
2
-
Ans.
ex - ey
2
cos 2u -
gxy
2
sin 2u
400 + 200
400 - 200
-300
cos (-60°) - a
b sin (-60°) R A 10 - 6 B
2
2
2
= 120 A 10 - 6 B
Ans.
827
x
gxy
2
dx
We obtain,
ex + ey
gxy
2
Pxdx
10 Solutions 46060
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Page 828
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10–103. The state of plane strain on an element is
Px = 400110-62, Py = 200110-62, and gxy = -300110-62.
Determine the equivalent state of strain, which represents
(a) the principal strains, and (b) the maximum in-plane
shear strain and the associated average normal strain.
Specify the orientation of the corresponding element at the
point with respect to the original element. Sketch the results
on the element.
y
Pydy
dy
Construction of the Circle: ex = 400 A 10 - 6 B , ey = 200 A 10 - 6 B , and
gxy
2
= -150 A 10 - 6 B .
Thus,
eavg =
ex + ey
2
= a
400 + 200
b A 10 - 6 B = 300 A 10 - 6 B
2
Ans.
The coordinates for reference points A and the center C of the circle are
A(400, -150) A 10 - 6 B
C(300, 0) A 10 - 6 B
The radius of the circle is
R = CA = 2(400 - 300)2 + (-150)2 = 180.28 A 10 - 6 B
Using these results, the circle is shown in Fig. a.
In - Plane Principal Stresses: The coordinates of points B and D represent e1 and e2,
respectively. Thus,
e1 = (300 + 180.28) A 10 - 6 B = 480 A 10 - 6 B
Ans.
e2 = (300 - 180.28) A 10 - 6 B = 120 A 10 - 6 B
Ans.
Orientation of Principal Plane: Referring to the geometry of the circle,
tan 2 A up B 1 =
150
= 1.5
400 - 300
A up B 1 = 28.2° (clockwise)
Ans.
The deformed element for the state of principal strains is shown in Fig. b.
Maximum In - Plane Shear Stress: The coordinates of point E represent eavg and
gmax
. Thus
in-plane
gmax
= -R = -180.28 A 10 - 6 B
in-plane
2
gmax
in-plane
= -361 A 10 - 6 B
Ans.
Orientation of the Plane of Maximum In - Plane Shear Strain: Referring to the
geometry of the circle,
tan 2us =
400 - 300
= 0.6667
150
uS = 16.8° (counterclockwise)
Ans.
The deformed element for the state of maximum in - plane shear strain is shown in
Fig. c.
828
gxy
2
x
gxy
2
dx
Pxdx
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Page 829
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10–103. Continued
829
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