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Chapter 16
16-1
(a)
θ
1
=
0°,
θ
2
=
120°,
θ
a
=
90°, sin
θ
a
=
1,
a
=
5in
Eq. (16-2):
M
f
=
0
.
28
p
a
(1
.
5)(6)
120°
sin
θ
(6
−
5 cos
θ
)
d
θ
1
0°
=
17
.
96
p
a
lbf
·
in
Eq. (16-3):
M
N
=
p
a
(1
.
5)(6)(5)
1
120°
sin
2
θ
d
θ
=
56
.
87
p
a
lbf
·
in
0°
c
=
2(5 cos 30
◦
)
=
8
.
66 in
Eq. (16-4):
F
=
56
.
87
p
a
−
17
.
96
p
a
=
4
.
49
p
a
8
.
66
p
a
=
F
/
4
.
49
=
500
/
4
.
49
=
111
.
4 psi for cw rotation
Eq. (16-7): 500
=
56
.
87
p
a
+
17
.
96
p
a
8
.
66
9 psi for ccw rotation
A maximum pressure of 111
p
a
=
57
.
.
4 psioccurs on the RH shoe for cw rotation.
Ans.
(b)
RH shoe
:
Eq. (16-6):
T
R
=
0
.
28(111
.
4)(1
.
5)(6)
2
(cos 0
◦
−
cos 120
◦
)
=
2530 lbf
·
in
Ans.
1
LH shoe
:
Eq. (16-6):
T
L
=
0
.
28(57
.
9)(1
.
5)(6)
2
(cos 0
◦
−
cos 120
◦
)
=
1310 lbf
·
in
Ans.
1
T
total
=
2530
+
1310
=
3840 lbf
·
in
Ans.
(c)
F
x
Force vectors not to scale
F
F
x
30
F
F
y
30
y
F
y
y
R
y
Primary
shoe
R
x
Secondary
shoe
R
x
R
R
x
R
y
x
Chapter 16
397
RH shoe
:
F
x
=
500 sin 30°
=
250 lbf,
F
y
=
500 cos 30°
=
433 lbf
1
120
◦
0
◦
=
2
−
2
π/
3 rad
1
4
sin 2
Eqs. (16-8):
A
=
2
sin
2
θ
0
.
375,
B
=
θ
=
1
.
264
0
Eqs. (16-9):
R
x
=
111
.
4(1
.
5)(6)
[0
.
375
−
0
.
28(1
.
264)]
−
250
=−
229 lbf
1
R
y
=
111
.
4(1
.
5)(6)
[1
.
264
+
0
.
28(0
.
375)]
−
433
=
940 lbf
1
R
=
[(
−
229)
2
+
(940)
2
]
1
/
2
=
967 lbf
Ans.
LH shoe
:
F
x
=
250 lbf,
F
y
=
433 lbf
Eqs. (16-10):
R
x
=
57
.
9(1
.
5)(6)
[0
.
375
+
0
.
28(1
.
264)]
−
250
=
130 lbf
1
R
y
=
57
.
9(1
.
5)(6)
[1
.
264
−
0
.
28(0
.
375)]
−
433
=
171 lbf
1
R
=
[(130)
2
+
(171)
2
]
1
/
2
=
215 lbf
Ans.
16-2
θ
1
=
15°,
θ
2
=
105°,
θ
a
=
90°, sin
θ
a
=
1,
a
=
5in
0
.
28
p
a
(1
.
5)(6)
105°
Eq. (16-2):
M
f
=
sin
θ
(6
−
5 cos
θ
)
d
θ
=
13
.
06
p
a
1
15°
p
a
(1
.
5)(6)(5)
1
105°
Eq. (16-3):
M
N
=
sin
2
θ
d
θ
=
46
.
59
p
a
15°
c
=
2(5 cos 30°)
=
8
.
66 in
Eq. (16-4):
F
=
46
.
59
p
a
−
13
.
06
p
a
=
3
.
872
p
a
8
.
66
RH shoe
:
p
a
=
500
/
3
.
872
=
129
.
1 psi on RH shoe for cw rotation
Ans.
Eq. (16-6):
T
R
=
0
.
28(129
.
1)(1
.
5)(6
2
)(cos 15°
−
cos 105°)
=
2391 lbf
·
in
1
LH shoe
:
500
=
46
.
59
p
a
+
13
.
06
p
a
⇒
p
a
=
72
.
59 psi on LH shoe for ccw rotation
Ans.
8
.
66
T
L
=
0
.
28(72
.
59)(1
.
5)(6
2
)(cos 15°
−
cos 105°)
=
1344 lbf
·
in
1
T
total
=
2391
+
1344
=
3735 lbf
·
in
Ans.
Comparing this result with that of Prob. 16-1, a 2.7% reduction in torque is achieved by
using 25% less braking material.
398
Solutions Manual
• Instructor’s Solution Manual to Accompany Mechanical Engineering Design
16-3
Given:
θ
1
=
0°,
θ
2
=
120°,
θ
a
=
90°, sin
θ
a
=
1,
a
=
R
=
90 mm,
f
=
0
.
30,
F
=
1000 N
=
1kN,
r
=
280
/
2
=
140 mm, counter-clockwise rotation.
LH shoe
:
M
f
=
fp
a
br
sin
r
(1
−
cos
θ
2
)
−
2
sin
2
θ
2
θ
a
=
0
.
30
p
a
(0
.
030)(0
.
140)
0
.
140(1
−
cos 120
◦
)
−
0
.
090
2
sin
2
120°
1
=
0
.
000 222
p
a
N
·
m
M
N
=
p
a
br a
sin
θ
a
θ
2
2
−
1
4
sin 2
θ
2
=
p
a
(0
.
030)(0
.
140)(0
.
090)
120°
2
180
−
4
sin 2(120°)
1
=
4
.
777(10
−
4
)
p
a
N
·
m
c
=
2
r
cos
180
◦
−
θ
2
2
=
2(0
.
090) cos 30
◦
=
0
.
155 88 m
p
a
4
F
=
1
=
.
777(10
−
4
)
−
2
.
22(10
−
4
)
=
1
.
64(10
−
3
)
p
a
0
.
155 88
p
a
=
1
/
1
.
64(10
−
3
)
=
610 kPa
T
L
=
fp
a
br
2
(cos
θ
1
−
cos
θ
2
)
sin
θ
a
=
0
.
30(610)(10
3
)(0
.
030)(0
.
140
2
)
[1
−
(
−
0
.
5)]
1
=
161
.
4N
·
m
Ans.
RH shoe
:
M
f
=
2
.
22(10
−
4
)
p
a
N
·
m
M
N
=
4
.
77(10
−
4
)
p
a
N
·
m
c
=
0
.
155 88 m
p
a
4
F
=
1
=
.
77(10
−
4
)
+
2
.
22(10
−
4
)
=
4
.
49(10
−
3
)
p
a
0
.
155 88
p
a
=
1
=
222
.
8kPa
Ans.
4
.
49(10
−
3
)
T
R
=
(222
.
8
/
610)(161
.
4)
=
59
.
0N
·
m
Ans
.
a
1
Chapter 16
399
16-4
(a)
Given:
θ
1
=
10°,
θ
2
=
75°,
θ
a
=
75°,
p
a
=
10
6
Pa,
f
=
0
.
24,
b
=
0
.
075 m (shoe width), a
=
0
.
150 m, r
=
0
.
200 m, d
=
0
.
050 m, c
=
0
.
165 m
.
Some of the terms needed are evaluated as:
r
θ
2
θ
1
a
1
θ
2
a
θ
2
θ
1
r
−
θ
θ
2
A
=
sin
θ
d
θ
−
sin
θ
cos
θ
d
θ
=
cos
θ
1
−
2
sin
2
θ
θ
1
150
1
75°
10°
=
=
200
−
cos
θ
75°
10°
−
2
sin
2
θ
77
.
5mm
B
=
θ
2
sin
2
θ
d
θ
=
2
−
1
4
sin 2
θ
75
π/
180 rad
10
π/
180 rad
=
0
.
528
θ
1
θ
2
C
=
sin
θ
cos
θ
d
θ
=
0
.
4514
θ
1
Now converting to pascals and meters, we have from Eq. (16-2),
M
f
=
fp
a
br
sin
A
=
0
.
24[(10)
6
](0
.
075)(0
.
200)
(0
.
0775)
=
289 N
·
m
θ
a
sin 75°
From Eq. (16-3),
M
N
=
p
a
br a
sin
B
=
[(10)
6
](0
.
075)(0
.
200)(0
.
150)
(0
.
528)
=
1230 N
·
m
θ
a
sin 75°
Finally, using Eq. (16-4), we have
F
=
M
N
−
M
f
c
=
1230
−
289
=
5
.
70 kN
Ans.
165
(b)
Use Eq. (16-6) for the primary shoe.
T
=
fp
a
br
2
(cos
θ
1
−
cos
θ
2
)
sin
θ
a
=
0
.
24[(10)
6
](0
.
075)(0
.
200)
2
(cos 10°
−
cos 75°)
=
541 N
·
m
sin 75°
For the secondary shoe, we must first find
p
a
.
Substituting
M
N
=
1230
10
6
p
a
and
M
f
=
289
10
6
p
a
into Eq. (16-7),
5
.
70
=
(1230
/
10
6
)
p
a
+
(289
/
10
6
)
p
a
, solving gives
p
a
=
619(10)
3
Pa
165
Then
T
=
0
.
24[0
.
619(10)
6
](0
.
075)(0
.
200)
2
(cos 10°
−
cos 75°)
=
335 N
·
m
sin 75°
so the braking capacity is
T
total
=
2(541)
+
2(335)
=
1750 N
·
m
Ans.
400
Solutions Manual
• Instructor’s Solution Manual to Accompany Mechanical Engineering Design
(c)
Primary shoes
:
R
x
=
p
a
br
sin
θ
a
(
C
−
fB
)
−
F
x
=
(10
6
)(0
.
075)(0
.
200)
[0
.
4514
−
0
.
24(0
.
528)](10)
−
3
−
5
.
70
=−
0
.
658 kN
sin 75°
R
y
=
p
a
br
sin
θ
a
(
B
+
fC
)
−
F
y
=
(10
6
)(0
.
075)(0
.
200)
[0
.
528
+
0
.
24(0
.
4514)](10)
−
3
−
0
=
9
.
88 kN
sin 75°
Secondary shoes
:
R
x
=
p
a
br
sin
θ
a
(
C
+
fB
)
−
F
x
=
[0
.
619(10)
6
](0
.
075)(0
.
200)
[0
.
4514
+
0
.
24(0
.
528)](10)
−
3
−
5
.
70
sin 75°
=−
0
.
143 kN
R
y
=
p
a
br
sin
θ
a
(
B
−
fC
)
−
F
y
=
[0
.
619(10)
6
](0
.
075)(0
.
200)
[0
.
528
−
0
.
24(0
.
4514)](10)
−
3
−
0
sin 75°
=
4
.
03 kN
Note from figure that
+
y
for secondary shoe is opposite to
y
R
+
y
for primary shoe.
R
V
Combining horizontal and vertical components,
x
x
R
H
R
H
=−
0
.
658
−
0
.
143
=−
0
.
801 kN
R
V
=
(0
.
88
−
4
.
03
=
5
.
85 kN
y
R
=
.
801)
2
+
(5
.
85)
2
=
5
.
90 kN
Ans.
16-5
Preliminaries:
θ
1
=
45°
−
tan
−
1
(150
/
200)
=
8
.
13°,
θ
2
=
98
.
13°
θ
a
=
90°,
a
=
[(150)
2
+
(200)
2
]
1
/
2
=
250 mm
Eq. (16-8):
A
=
2
sin
2
θ
98
.
13°
8
=
0
.
480
.
13°
θ
2
θ
=−
cos
θ
98
.
13°
8
Let
C
=
sin
θ
d
=
1
.
1314
.
13°
θ
1
9
1
Plik z chomika:
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MIT LEC
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