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Design for Simple Stresses
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SECTION 1 DESIGN FOR SIMPLE STRESSES
2
TENSION, COMPRESSION, SHEAR
DESIGN PROBLEMS
1. The link shown, made of AISI C1045 steel, as rolled, is subjected to a tensile load of 8000 lb. Let bh 5.1= . If the load is repeated but not reversed, determine the dimensions of the section with the design based on (a) ultimate strength, (b) yield strength. (c) If this link, which is 15 in. long., must not elongate more than 0.005 in., what should be the dimensions of the cross section?
Problems 1 3. Solution: For AISI C1045 steel, as rolled (Table AT 7)
ksisu 96= ksisy 59=
psiE 61030=
AF
sd =
where lbF 8000=
bhA = but
bh 5.1= therefore 25.1 bA =
(a) Based on ultimate strength
N = factor of safety = 6 for repeated but not reversed load (Table 1.1)
AF
Ns
s ud ==
25.18000
6000,96
b=
inb 577.0= say in85
.
SECTION 1 DESIGN FOR SIMPLE STRESSES
3
inbh16155.1 ==
(b) Based on yield strength
N = factor of safety = 3 for repeated but not reversed load (Table 1.1)
AF
Ns
s ud ==
25.18000
3000,59
b=
inb 521.0= say in169
.
inbh32275.1 ==
(c) Elongation = AEFL
= where,
in005.0= lbF 8000=
psiE 61030= inL 15=
25.1 bA = then,
AEFL
= ( )( )
( )( )62 10305.1158000005.0
=
b
inb 730.0= say in43
.
inbh8115.1 ==
2. The same as 1 except that the material is malleable iron, ASTM A47-52, grade 35 018.
Solution: For malleable iron, ASTM A47-52, grade 35 018(Table AT 6)
ksisu 55= ksisy 5.36=
psiE 61025=
SECTION 1 DESIGN FOR SIMPLE STRESSES
4
AF
sd =
where lbF 8000=
bhA = but
bh 5.1= therefore 25.1 bA =
(a) Based on ultimate strength
N = factor of safety = 6 for repeated but not reversed load (Table 1.1)
AF
Ns
s ud ==
25.18000
6000,55
b=
inb 763.0= say in87
.
inbh16515.1 ==
(b) Based on yield strength
N = factor of safety = 3 for repeated but not reversed load (Table 1.1)
AF
Ns
s ud ==
25.18000
3500,36
b=
inb 622.0= say in1611
.
inbh32115.1 ==
(c) Elongation = AEFL
= where,
in005.0= lbF 8000=
psiE 61025= inL 15=
25.1 bA = then,
SECTION 1 DESIGN FOR SIMPLE STRESSES
5
AEFL
= ( )( )
( )( )62 10255.1158000005.0
=
b
inb 8.0= say in87
.
inbh16515.1 ==
3. The same as 1 except that the material is gray iron, ASTM 30.
Solution: For ASTM 30 (Table AT 6)
ksisu 30= , no ys psiE 6105.14 =
Note: since there is no ys for brittle materials. Solve only for (a) and (c)
AF
sd =
where lbF 8000=
bhA = but
bh 5.1= therefore 25.1 bA =
(a) Based on ultimate strength
N = factor of safety = 7 ~ 8 say 7.5 (Table 1.1)
AF
Ns
s ud ==
25.18000
5.7000,30
b=
inb 1547.1= say in1631 .
inbh322515.1 ==
(c) Elongation = AEFL
= where,
in005.0= lbF 8000=
psiE 6105.14 =
SECTION 1 DESIGN FOR SIMPLE STRESSES
6
inL 15= 25.1 bA =
then,
AEFL
= ( )( )
( )( )62 105.145.1158000005.0
=
b
inb 050.1= say in1611 .
inbh321915.1 ==
4. A piston rod, made of AISI 3140 steel, OQT 1000 F (Fig. AF 2), is subjected to a repeated, reversed load. The rod is for a 20-in. air compressor, where the maximum pressure is 125 psig. Compute the diameter of the rod using a design factor based on (a) ultimate strength, (b) yield strength.
Solution: From Fig. AF 2 for AISI 3140, OQT 1000 F
ksisu 5.152= ksisy 5.132=
( ) ( ) kipslbforceF 27.39270,39125204
2====
pi
From Table 1.1, page 20 8=uN 4=yN
(a) Based on ultimate strength
u
u
s
FNA =
( )( )5.15227.398
42
=dpi
ind 62.1= say in851
(b) Based on yield strength
y
y
s
FNA =
( )( )5.13227.394
42
=dpi
SECTION 1 DESIGN FOR SIMPLE STRESSES
7
ind 23.1= say in411
5. A hollow, short compression member, of normalized cast steel (ASTM A27-58, 65 ksi), is to support a load of 1500 kips with a factor of safety of 8 based on the ultimate strength. Determine the outside and inside diameters if io DD 2= .
Solution: ksisu 65=
8=uN kipsF 1500=
( ) ( )4
3444
22222 iiiio
DDDDDA pipipi ===
( )( )6515008
43 2
===
u
ui
s
FNDA pi
inDi 85.8= say in878
inDD io 4317
87822 =
==
6. A short compression member with io DD 2= is to support a dead load of 25 tons. The material is to be 4130 steel, WQT 1100 F. Calculate the outside and inside diameters on the basis of (a) yield strength, (b) ultimate strength.
Solution: From Table AT 7 for 4130, WQT 1100 F
ksisu 127= ksisy 114=
From Table 1.1 page 20, for dead load 4~3=uN , say 4
2~5.1=yN , say 2
Area, ( ) ( )4
3444
22222 iiiio
DDDDDA pipipi ===
kipstonsF 5025 ==
(a) Based on yield strength ( )( )
114502
43 2
===
y
yi
s
FNDA pi
SECTION 1 DESIGN FOR SIMPLE STRESSES
8
inDi 61.0= say in85
inDD io 411
8522 =
==
(b) Based on ultimate strength ( )( )
127504
43 2
===
u
ui
s
FNDA pi
inDi 82.0= say in87
inDD io 431
8722 =
==
7. A round, steel tension member, 55 in. long, is subjected to a maximum load of 7000 lb. (a) What should be its diameter if the total elongation is not to exceed 0.030 in? (b) Choose a steel that would be suitable on the basis of yield strength if the load is gradually applied and repeated (not reversed).
Solution:
(a) AEFL
= or E
FLA = where,
lbF 7000= inL 55=
in030.0= psiE
61030=
( )( )( )( )62 1030030.0
5570004
== dA pi
ind 74.0= say in43
(b) For gradually applied and repeated (not reversed) load 3=yN
( )( )( )
psiAFN
sy
y 534,4775.0
4
700032
===
pi
ksisy 48 say C1015 normalized condition ( ksisy 48= )
8. A centrifuge has a small bucket, weighing 0.332 lb. with contents, suspended on a manganese bronze pin (B138-A, hard) at the end of a horizontal arm. If the pin is in double shear under the action of the centrifugal force, determine the diameter
SECTION 1 DESIGN FOR SIMPLE STRESSES
9
needed for 10,000 rpm of the arm. The center of gravity of the bucket is 12 in. from the axis of rotation.
Solution: From Table AT 3, for B138-A, hard
ksisus 48=
rg
WF 2=
where lbW 332.0=
22.32 fpsg = ( )
sec104760
000,10260
2radn === pipi
inr 12=
( ) ( ) kipslbrg
WF 3.11300,11110472.32
332.0 22====
From Table 1.1, page 20 4~3=N , say 4
u
u
s
FNA =
( )( )48
3.1144
2 2 =
dpi for double shear
ind 774.0= say in3225
CHECK PROBLEMS
9. The link shown is made of AISIC1020 annealed steel, with inb43
= and
inh211= . (a) What force will cause breakage? (b) For a design factor of 4 based
on the ultimate strength, what is the maximum allowable load? (c) If 5.2=N based on the yield strength, what is the allowable load?
Problem 9.
SECTION 1 DESIGN FOR SIMPLE STRESSES
10
Solution: For AISI C1020 annealed steel, from Table AT 7
ksisu 57= ksisy 42=
(a) AsF u= 2125.1
211
43 inbhA =
==
( )( ) kipsF 64125.157 == (b)
u
u
NAsF =
4=uN
2125.1211
43 inbhA =
==
( )( ) kipsF 164
125.157==
(c) y
y
NAs
F =
5.2=yN
2125.1211
43 inbhA =
==
( )( ) kipsF 9.182
125.142==
10. A -in.bolt, made of cold-finished B1113, has an effective stress area of 0.334 sq. in. and an effective grip length of 5 in. The bolt is to be loaded by tightening until the tensile stress is 80 % of the yield strength, as determined by measuring the total elongation. What should be the total elongation?
Solution:
EsL
= from Table AT 7 for cold-finished B1113
ksisy 72= then, ( ) ksiss y 6.57728.080.0 ===
ksipsiE 000,301030 6 == ( )( ) in
EsL 0096.0
000,3056.57
===
SECTION 1 DESIGN FOR SIMPLE STRESSES
11
11. A 4-lb. weight is attached by a 3/8-in. bolt to a rotating arm 14-in. from the center of rotation. The axis of the bolts is normal to the plane in which the centrifugal force acts and the bolt is in double shear. At what speed will the bolt shear in two if it is made of AISI B1113, cold finish?
Solution: From Table AT 7, psiksisus 000,6262 ==
( ) 22
2209.083
412 inA =
= pi
Asrg
WF us==2
( ) ( )( )2209.0000,62142.32
4 2=
sec74.88 rad=
74.8860
2==
npi
rpmn 847=
12. How many -in. holes could be punched in one stroke in annealed steel plate of AISI C1040, 3/16-in. thick, by a force of 60 tons?
Solution:
For AISI C1040, from Figure AF 1 ksisu 80=
( ) ksiksiss uus 608075.075.0 === 2
4418.016
3
4
3intdA =
== pipi
kipstonsF 12060 == n = number of holes
( )( ) 5604415.0120
===
usAs
Fn holes
13. What is the length of a bearing for a 4-in. shaft if the load on the bearing is 6400 lb. and the allowable bearing pressure is 200 psi of the projected area?
Solution: WpDL =
where psip 200=
inD 4=
SECTION 1 DESIGN FOR SIMPLE STRESSES
12
lbW 6400= ( )( ) 64004200 =L
inL 8=
BENDING STRESSES
DESIGN PROBLEMS
14. A lever keyed to a shaft is inL 15= long and has a rectangular cross section of th 3= . A 2000-lb load is gradually applied and reversed at the end as shown; the
material is AISI C1020, as rolled. Design for both ultimate and yield strengths. (a) What should be the dimensions of a section at ina 13= ? (b) at inb 4= ? (c) What should be the size where the load is applied?
Problem 14. Solution: For AISI C1020, as rolled, Table AT 7
ksisu 65= ksisy 49=
Design factors for gradually applied and reversed load 8=uN 4=yN
12
3thI = , moment of inertial
but th 3=
36
4hI =
Moment Diagram (Load Upward)
SECTION 1 DESIGN FOR SIMPLE STRESSES
13
Based on ultimate strength
u
u
Ns
s =
(a) I
FacI
Mcs ==
2h
c =
kipslbsF 22000 ==
( )( )
==
36
2132
865
4h
h
s
inh 86.3=
inht 29.1386.3
3===
say
ininh2145.4 ==
inint2115.1 ==
(b) I
FbcI
Mcs ==
2h
c =
kipslbsF 22000 ==
( )( )
==
36
242
865
4h
h
s
inh 61.2=
inht 87.0361.2
3===
say inh 3=
int 1=
(c)
SECTION 1 DESIGN FOR SIMPLE STRESSES
14
41335.4
43
= h
inh 33.2=
41315.1
41
= t
int 78.0= say
inh 625.2= or inh852=
15. A simple beam 54 in. long with a load of 4 kips at the center is made of cast steel, SAE 080. The cross section is rectangular (let bh 3 ). (a) Determine the dimensions for 3=N based on the yield strength. (b) Compute the maximum deflection for these dimensions. (c) What size may be used if the maximum deflection is not to exceed 0.03 in.?
Solution: For cast steel, SAE 080 (Table AT 6)
ksisy 40= psiE 61030=
SECTION 1 DESIGN FOR SIMPLE STRESSES
15
From Table AT 2
Max. ( )( ) inkipsFLM === 544544
4
12
3bhI =
but bh 3=
36
4hI =
(a) I
McNs
sy
y==
2h
c =
( )
=
36
254
340
4h
h
inh 18.4=
inhb 39.1318.4
3===
say inh214= , ininhb
2115.1
35.4
3====
(b) ( )( )( ) ( )( )
inEI
FL 0384.0
125.45.1103048
54400048 36
33
=
==
(c)
=
3648
4
3
hE
FL
( )( ) ( )( )( )46
3
1030483654400003.0h
=
inh 79.4=
inhb 60.1379.4
3===
say ininh41525.5 == , ininhb
43175.1
325.5
3====
SECTION 1 DESIGN FOR SIMPLE STRESSES
16
16. The same as 15, except that the beam is to have a circular cross section.
Solution:
(a) I
McNs
sy
y==
64
4dI pi=
2d
c =
34
32
64
2dM
d
dMs
pipi=
=
( )3
5432340
dpi=
ind 46.3=
say ind213=
(b) EI
FL48
3
=
64
4dI pi=
( )( )( )
( )( )( ) indEFL 0594.0
5.310304854400064
4864
46
3
4
3
=
==
pipi
(c) ( )43
4864
dEFLpi
=
( )( )( )( ) 46
3
1030485440006403.0
dpi=
ind 15.4=
say ind414=
17. A simple beam, 48 in. long, with a static load of 6000 lb. at the center, is made of C1020 structural steel. (a) Basing your calculations on the ultimate strength, determine the dimensions of the rectangular cross section for bh 2= . (b) Determine the dimensions based on yield strength. (c) Determine the dimensions using the principle of limit design.
SECTION 1 DESIGN FOR SIMPLE STRESSES
17
Solution:
From Table AT 7 and Table 1.1 ksisu 65= ksisy 48=
4~3=uN , say 4 2~5.1=yN , say 2
( )( ) kipsinFLM === 724486
4
IMc
s =
2h
c =
12
3bhI =
but 2hb =
24
4hI =
3412
24
2hM
h
hMs =
=
(a) Based on ultimate strength
312
hM
Ns
su
u==
( )37212
465
h=
inh 76.3=
SECTION 1 DESIGN FOR SIMPLE STRESSES
18
inhb 88.1276.3
2===
say ininh43375.3 == , ininhb
871875.1
275.3
2====
(b) Based on yield strength
312
hM
Ns
sy
y==
( )37212
248
h=
inh 30.3=
inhb 65.1230.3
2===
say ininh2135.3 == , ininhb
43175.1
25.3
2====
(c) Limit design (Eq. 1.6)
4
2bhsM y=
( )4
24872
2hh
=
inh 29.2=
inhb 145.1229.2
2===
say ininh2125.2 == , ininhb
41125.1
25.2
2====
18. The bar shown is subjected to two vertical loads, 1F and 2F , of 3000 lb. each, that are inL 10= apart and 3 in. ( a , d ) from the ends of the bar. The design factor is 4 based on the ultimate strength; bh 3= . Determine the dimensions h and b if the bar is made of (a) gray cast iron, SAE 111; (b) malleable cast iron, ASTM A47-52, grade 35 018; (c) AISI C1040, as rolled (Fig. AF 1). Sketch the shear and moment diagrams approximately to scale.
SECTION 1 DESIGN FOR SIMPLE STRESSES
19
Problems18, 19. Solution:
lbRRFF 30002121 ====
Moment Diagram
( )( ) inkipsinlbsaRM ==== 99000330001 N = factor of safety = 4 based on us
12
3bhI =
2h
c =
36123 4
3
hhh
I =
=
(a) For gray cast iron, SAE 111 ksisu 30= , Table AT 6
34
18
36
2hM
h
hM
IMc
Ns
s u =
===
( )3918
430
hs ==
inh 78.2=
inhb 93.0378.2
3===
say inh 5.3= , inb 1=
(b) For malleable cast iron, ASTM A47-52, grade 35 018
SECTION 1 DESIGN FOR SIMPLE STRESSES
20
ksisu 55= , Table AT 6
34
18
36
2hM
h
hM
IMc
Ns
s u =
===
( )3918
455
hs ==
inh 28.2=
inhb 76.0328.2
3===
say inh412= , inb
43
=
(c) For AISI C1040, as rolled ksisu 90= , Fig. AF 1
34
18
36
2hM
h
hM
IMc
Ns
s u =
===
( )3918
490
hs ==
inh 93.1=
inhb 64.0393.1
3===
say inh871= , inb
85
=
19. The same as 18, except that 1F acts up ( 2F acts down).
Solution:
[ ] = 0AM lbRR 187521 ==
SECTION 1 DESIGN FOR SIMPLE STRESSES
21
Shear Diagram
Moment Diagram
=M maximum moment = 5625 lb-in = 5.625 kips-in
(a) For gray cast iron
318
hM
Ns
s u ==
( )3625.518
430
h=
inh 38.2=
inhb 79.0338.2
3===
say inh412= , inb
43
=
(b) For malleable cast iron
318
hM
Ns
s u ==
( )3625.518
455
h=
inh 95.1=
inhb 65.0395.1
3===
say inh871= , inb
85
=
SECTION 1 DESIGN FOR SIMPLE STRESSES
22
(c) For AISI C1040, as rolled
318
hM
Ns
s u ==
( )3625.518
490
h=
inh 65.1=
inhb 55.0365.1
3===
say inh211= , inb
21
=
20. The bar shown, supported at A and B , is subjected to a static load F of 2500 lb. at 0= . Let ind 3= , inL 10= and bh 3= . Determine the dimensions of the section if the bar is made of (a) gray iron, SAE 110; (b) malleable cast iron, ASTM A47-52, grade 32 510; (c) AISI C1035 steel, as rolled. (d) For economic reasons, the pins at A, B, and C are to be the same size. What should be their diameter if the material is AISI C1035, as rolled, and the mounting is such that each is in double shear? Use the basic dimensions from (c) as needed. (e) What sectional dimensions would be used for the C1035 steel if the principle of limit design governs in (c)?
Problems 20, 21. Solution:
SECTION 1 DESIGN FOR SIMPLE STRESSES
23
[ ] = 0AM ( )2500133 =BR lbRB 833,10= [ ] = 0BM ( )2500103 =AR lbRA 8333= Shear Diagram
Moment Diagram
( )( ) inkipsinlbM === 25000,25102500
bh 3=
12
3bhI =
36
4hI =
2h
c =
34
18
36
2hM
h
hM
IMc
s =
==
(a) For gray cast iron, SAE 110 ksisu 20= , Table AT 6 6~5=N , say 6 for cast iron, dead load
318
hM
Ns
s u ==
( )32518
620
h=
SECTION 1 DESIGN FOR SIMPLE STRESSES
24
inh 13.5=
inhb 71.13
==
say inh415= , inb
431=
(b) For malleable cast iron, ASTM A47-32 grade 32510 ksisu 52= , ksisy 34= 4~3=N , say 4 for ductile, dead load
318
hM
Ns
s u ==
( )32518
452
h=
inh 26.3=
inhb 09.13
==
say inh433= , inb
411=
(c) For AISI C1035, as rolled ksisu 85= , ksisy 55=
4=N , based on ultimate strength
318
hM
Ns
s u ==
( )32518
485
h=
inh 77.2=
inhb 92.03
==
say inh 3= , inb 1=
(d) For AISI C1035, as rolled ksissu 64=
4=N , kipsRB 833.10=
AR
Ns
s Bsus ==
22
242 DDA pipi =
=
2
2
833.104
64
Dss pi
==
inD 657.0=
SECTION 1 DESIGN FOR SIMPLE STRESSES
25
say inD1611
=
(e) Limit Design
4
2bhsM y=
For AISI C1035 steel, ksisy 55=
3hb =
( )4
35525
2hh
M
==
inh 76.1=
inhb 59.03
==
say ininh871875.1 == , inb
85
=
21. The same as 20, except that o30= . Pin B takes all the horizontal thrust.
Solution:
cosFFV = [ ] = 0AM VB FR 133 = ( ) 30cos2500133 =BR
lbRB 9382= [ ] = 0BM VA FR 103 = ( ) 30cos2500103 =AR
lbRA 7217= Shear Diagram
SECTION 1 DESIGN FOR SIMPLE STRESSES
26
Moment Diagram
( )( ) inkipsinlbM === 65.21650,21102165 3
18hM
s =
(a) For gray cast iron, SAE 110 ksisu 20= , Table AT 6 6~5=N , say 6 for cast iron, dead load
318
hM
Ns
s u ==
( )3
65.2118620
h=
inh 89.4=
inhb 63.13
==
say inh415= , inb
431=
(b) For malleable cast iron, ASTM A47-32 grade 32510 ksisu 52= , ksisy 34= 4~3=N , say 4 for ductile, dead load
318
hM
Ns
s u ==
( )3
65.21184
52h
=
inh 11.3=
inhb 04.13
==
say inh 3= , inb 1= (c) For AISI C1035, as rolled
ksisu 85= , ksisy 55= 4=N , based on ultimate strength
SECTION 1 DESIGN FOR SIMPLE STRESSES
27
318
hM
Ns
s u ==
( )3
65.21184
85h
=
inh 64.2=
inhb 88.03
==
say inh852= , inb
87
=
(d) For AISI C1035, as rolled ksissu 64=
4=N , lbRBV 9382= lbFFR HBH 125030sin2500sin ====
( ) ( )22222 12509382 +=+= BHBVB RRR lbRB 9465=
AR
Ns
s Bsus ==
22
242 DDA pipi =
=
2
2
465.94
64
Dss pi
==
inD 614.0=
say inD85
=
(e) Limit Design
4
2bhsM y=
For AISI C1035 steel, ksisy 55=
3hb =
( )4
35565.21
2hh
M
==
inh 68.1=
inhb 56.03
==
say ininh871875.1 == , inb
85
=
SECTION 1 DESIGN FOR SIMPLE STRESSES
28
22. A cast-iron beam, ASTM 50, as shown, is 30 in. long and supports two gradually applied, repeated loads (in phase), one of 2000 lb. at ine 10= from the free end, and one of 1000 lb at the free end. (a) Determine the dimensions of the cross section if acb 3= . (b) The same as (a) except that the top of the tee is below.
Problem 22. Solution:
For cast iron, ASTM 50 ksisu 50= , ksisuc 164=
For gradually applied, repeated load 8~7=N , say 8
( )edFdFM ++= 21 where:
lbF 20001 = lbF 10002 =
ind 201030 == ined 30=+
( )( ) ( )( ) inkipsinlbM ==+= 70000,70301000202000
IMc
s =
Solving for I , moment of inertia
( )( ) ( )( ) ( )( ) ( )( )[ ]yaaaaaaaaaa 332
532
3 +=
+
23ay =
SECTION 1 DESIGN FOR SIMPLE STRESSES
29
( )( ) ( )( )( ) ( )( ) ( )( )( )2
1731233
123 42
32
3a
aaaaa
aaaaaI =+++=
(a)
23a
ct =
25a
cc =
Based on tension
IMc
Ns
s tut ==
( )
=
217
2370
850
4a
a
ina 255.1= Based on compression
IMc
Ns
s cucc ==
( )
=
217
2570
8164
4a
a
ina 001.1= Therefore ina 255.1=
Or say ina411=
And ( ) inacb 75.325.133 ====
SECTION 1 DESIGN FOR SIMPLE STRESSES
30
Or incb433==
(b) If the top of the tee is below
25a
ct =
23a
cc =
217 4aI =
inkipsM = 70
Based on tension
IMc
Ns
s tut ==
( )
=
217
2570
850
4a
a
ina 488.1= Based on compression
IMc
Ns
s cucc ==
( )
=
217
2370
8164
4a
a
ina 845.0= Therefore ina 488.1=
Or say ina211=
And inacb2143 ===
CHECK PROBLEMS
SECTION 1 DESIGN FOR SIMPLE STRESSES
31
23. An I-beam is made of structural steel, AISI C1020, as rolled. It has a depth of 3 in. and is subjected to two loads; 1F and 12 2FF = ; 1F is 5 in. from one end and
2F is 5 in. from the other ends. The beam is 25 in. long; flange width is inb 509.2= ; 49.2 inI x = . Determine (a) the approximate values of the load to
cause elastic failure, (b) the safe loads for a factor of safety of 3 based on the yield strength, (c) the safe load allowing for flange buckling (i1.24), (f) the maximum deflection caused by the safe loads.
Problems 23 25. Solution:
[ ] = 0AM ( ) BRFF 252205 11 =+ 18.1 FRB = [ ] = 0VF BA RRFF +=+ 11 2 111 2.18.13 FFFRA == Shear Diagram
Moment Diagram
SECTION 1 DESIGN FOR SIMPLE STRESSES
32
19FM = = maximum moment For AISI C1020, as rolled
ksisy 48=
(a) I
Mcsy =
where indc 5.123
2===
( )( )9.2
5.1948 1Fsy ==
kipsF 31.101 = kipsFF 62.202 12 ==
(b) I
McNs
sy
==
( )( )9.2
5.19348 1Fs ==
kipsF 44.31 = kipsFF 88.62 12 ==
(c) 1596.9509.225
or
( ) 23max 33
+=
aLbEILFay , ab >
SECTION 1 DESIGN FOR SIMPLE STRESSES
33
maxy caused by 1F
( ) 231111max 331
+=
aLbEIL
aFy , 11 ab >
where ksiE 000,30= ina 51 = inb 201 = inL 25=
49.2 inI =
( )( )( )( )
( )1
23
1max 0022.03
52520259.2000,303
51
FFy =
+=
maxy caused by 2F
( ) 232222max 332
+=
bLaEIL
bFy , 22 ba >
where inb 52 = ina 202 =
( )( )( )( )
( )1
23
1max 0043.03
52520259.2000,303
522
FFy =
+=
Total deflection = 111maxmax 0065.00043.0022.021 FFFyy =+=+=
Deflection caused by the safe loads in (a) ( ) ina 067.031.100065.0 ==
Deflection caused by the safe loads in (b) ( ) inb 022.044.30065.0 ==
Deflection caused by the safe loads in (c) ( ) inc 028.030.40065.0 ==
24. The same as 23, except that the material is aluminum alloy, 2024-T4, heat treated.
Solution:
For aluminum alloy, 2024-T4, heat treated ksisy 47=
(a) I
Mcsy =
SECTION 1 DESIGN FOR SIMPLE STRESSES
34
( )( )9.2
5.1947 1Fsy ==
kipsF 10.101 = kipsFF 20.202 12 ==
(b) I
McNs
sy
==
( )( )9.2
5.193
47 1Fs ==
kipsF 36.31 = kipsFF 72.62 12 ==
(c) 1596.9509.225
SECTION 1 DESIGN FOR SIMPLE STRESSES
35
Solution:
(a) For C1020, as rolled, ksisu 65= Consider flange buckling
3066.2
80==
bL
since 4015
SECTION 1 DESIGN FOR SIMPLE STRESSES
36
addl ( ) inkipsinlbwLM ==
== 513.0513
880
127.7
8
22
513.020 += FM = total moment
IMc
ss c ==
( )( )6
2513.02015 += F
kipsF 224.2= Therefore, the safe load should be less.
26. What is the stress in a band-saw blade due to being bent around a 13 -in. pulley? The blade thickness is 0.0265 in. (Additional stresses arise from the initial tension and forces of sawing.)
Solution:
intc 01325.00265.02
===
inr 76325.1301325.075.13 =+= Using Eq. (1.4) page 11 (Text)
r
Ecs =
where psiE 61030= ( )( ) psis 881,28
76325.1301325.01030 6
=
=
27. A cantilever beam of rectangular cross section is tapered so that the depth varies uniformly from 4 in. at the fixed end to 1 in. at the free end. The width is 2 in. and the length 30 in. What safe load, acting repeated with minor shock, may be applied to the free end? The material is AISI C1020, as rolled.
Solution: For AISI C1020, as rolled
ksisu 65= (Table AT 7) Designing based on ultimate strength,
6=N , for repeated, minor shock load
SECTION 1 DESIGN FOR SIMPLE STRESSES
37
ksiNs
s u 8.10665
===
Loading Diagram
x
h 130
14 =
110.0 += xh
12
3whI =
2h
c =
FxM =
( )( )2223 110.0
3326
12
2+
===
==
x
FxhFx
hFx
wh
hFx
IMc
s
Differentiating with respect to x then equate to zero to solve for x giving maximum stress.
( ) ( ) ( )( )( )( ) 0110.0
10.0110.021110.03 42
=
+
++=
x
xxxFdxds
( ) 010.02110.0 =+ xx inx 10=
( ) inh 211010.0 =+= 2
3hFx
Ns
s u ==
( )( )22
1038.10 F=
kipsF 44.1=
TORSIONAL STRESSES
DESIGN PROBLEMS
SECTION 1 DESIGN FOR SIMPLE STRESSES
38
28. A centrifugal pump is to be driven by a 15-hp electric motor at 1750 rpm. What should be the diameter of the pump shaft if it is made of AISI C1045 as rolled? Consider the load as gradually repeated.
Solution:
For C1045 as rolled, ksisy 59= ksisus 72=
Designing based on ultimate strength
Ns
s us= , 6=N (Table 1.1)
ksis 12672
==
Torque, ( )( ) kipsinlbinlbftnhpT ===== 540.054045
1750215000,33
2000,33
pipi
For diameter,
316
dT
spi
=
( )3
540.01612dpi
=
ind 612.0=
say ind85
=
29. A shaft in torsion only is to transmit 2500 hp at 570 rpm with medium shocks. Its material is AISI 1137 steel, annealed. (a) What should be the diameter of a solid shaft? (b) If the shaft is hollow, io DD 2= , what size is required? (c) What is the weight per foot of length of each of these shafts? Which is the lighter? By what percentage? (d) Which shaft is the more rigid? Compute the torsional deflection of each for a length of 10 ft.
Solution: ( )
( ) kipsinlbftnhpT ==== 276036,23
57022500000,33
2000,33
pipi
For AISI 1137, annealed ksisy 50= (Table AT 8)
ksiss yys 306.0 ==
Designing based on yield strength 3=N for medium shock, one direction
SECTION 1 DESIGN FOR SIMPLE STRESSES
39
Design stress
ksiNs
sys 10
330
===
(a) Let D = shaft diameter
JTc
s =
32
4DJ pi=
2D
c =
316
DT
spi
=
( )3
2761610Dpi
=
inD 20.5=
say inD415=
(b) ( ) ( )[ ]32
1532
232
44444iiiio DDDDDJ pipipi ===
iio DDDc ===
22
2
34 1532
3215 ii
i
DT
DTD
spipi
=
=
( )315
2763210iDpi
=
inDi 66.2= inDD io 32.52 ==
say
inDi 852=
inDo 415=
(c) Density, 3284.0 inlb= (Table AT 7)
SECTION 1 DESIGN FOR SIMPLE STRESSES
40
For solid shaft =w weight per foot of length
( )( ) ftlbDDw 8.7325.5284.0334
12 222 ===
= pipipi
For hollow shaft
( ) ( ) ( ) ( ) ( )[ ] ftlbDDDDw ioio 3.55625.225.5284.033412 222222 ==== pipipi
Therefore hollow shaft is lighter
Percentage lightness = ( ) %5.33%1003.55
3.558.73=
(d) Torsional Deflection
JGTL
=
where inftL 12010 ==
ksiG 3105.11 =
For solid shaft, 32
4DJ pi=
( )( )( ) ( ) ( )
o2.2180039.0039.0105.1125.5
32
12027634
=
==
=
pipi rad
For hollow shaft, ( )32
44io DDJ = pi
( )( )( ) ( )[ ]( ) ( )
o4.2180041.0041.0105.11625.225.5
32
120276344
=
==
=
pipi rad
Therefore, solid shaft is more rigid, oo 4.22.2 <
30. The same as 29, except that the material is AISI 4340, OQT 1200 F.
Solution: ( )
( ) kipsinlbftnhpT ==== 276036,23
57022500000,33
2000,33
pipi
For AISI 4340, OQT 1200 F ksisy 130=
( ) ksiss yys 781306.06.0 ===
Designing based on yield strength
SECTION 1 DESIGN FOR SIMPLE STRESSES
41
3=N for mild shock
Design stress
ksiNs
sys 26
378
===
(a) Let D = shaft diameter
JTc
s =
32
4DJ pi=
2D
c =
316
DT
spi
=
( )3
2761626Dpi
=
inD 78.3=
say inD433=
(b) ( ) ( )[ ]32
1532
232
44444iiiio DDDDDJ pipipi ===
iio DDDc ===
22
2
34 1532
3215 ii
i
DT
DTD
spipi
=
=
( )315
2763226iDpi
=
inDi 93.1= inDD io 86.32 ==
say inDi 2= inDo 4=
(c) Density, 3284.0 inlb= (Table AT 7)
SECTION 1 DESIGN FOR SIMPLE STRESSES
42
For solid shaft =w weight per foot of length
( )( ) ftlbDDw 6.3775.3284.0334
12 222 ===
= pipipi
For hollow shaft
( ) ( ) ( ) ( ) ( )[ ] ftlbDDDDw ioio 1.3224284.033412 222222 ==== pipipi
Therefore hollow shaft is lighter
Percentage lightness = ( ) %1.17%1001.32
1.326.37=
(d) Torsional Deflection
JGTL
=
where inftL 12010 ==
ksiG 3105.11 =
For solid shaft, 32
4DJ pi=
( )( )( ) ( ) ( )
o48.8180148.0148.0105.1175.3
32
12027634
=
==
=
pipi rad
For hollow shaft, ( )32
44io DDJ = pi
( )( )( ) ( )[ ]( ) ( )
o99.6180122.0122.0105.1124
32
120276344
=
==
=
pipi rad
Therefore, hollow shaft is more rigid, oo 48.899.6 < .
31. A steel shaft is transmitting 40 hp at 500 rpm with minor shock. (a) What should be its diameter if the deflection is not to exceed 1o in D20 ? (b) If deflection is primary what kind of steel would be satisfactory?
Solution:
(a) ( )( ) kipsinlbftnhpT ==== 04.5420
500240000,33
2000,33
pipi
ksiG 3105.11 = DL 20=
SECTION 1 DESIGN FOR SIMPLE STRESSES
43
rad180
1 pi == o
JGTL
=
( )( )( )34 105.11
32
2004.5180
=
DD
pi
pi
inD 72.1=
say inD431=
(b) ( )( ) ksiDT
s 8.475.104.51616
33 === pipi
Based on yield strength 3=N
( )( ) ksiNssys 4.148.43 === ksi
ss
ysy 246.0
4.146.0
===
Use C1117 normalized steel ksisy 35=
32. A square shaft of cold-finish AISI 1118 transmits a torsional moment of 1200 in-lb. For medium shock, what should be its size?
Solution:
For AISI 1118 cold-finish ksisy 75=
ksiss yys 456.0 == 3=N for medium shock
ZT
Ns
sys
==
where, bh =
92
92 32 bhbZ == (Table AT 1)
kipsinlbinT == 2.11200 ( )
3292.1
345
bs ==
inhb 71.0==
say inhb43
==
SECTION 1 DESIGN FOR SIMPLE STRESSES
44
CHECK PROBLEMS
33. A punch press is designed to exert a force sufficient to shear a 15/16-in. hole in a -in. steel plate, AISI C1020, as rolled. This force is exerted on the shaft at a radius of -in. (a) Compute the torsional stress in the 3.5-in. shaft (bending neglected). (b) What will be the corresponding design factor if the shaft is made of cold-rolled AISI 1035 steel (Table AT 10)? Considering the shock loading that is characteristics of this machine, do you thick the design is safe enough?
Solution: For AISI C1020, as rolled
ksisus 49=
( )DtsF us pi= where inD
1615
=
int21
=
( ) kipsF 2.7221
161549 =
= pi
FrT =
where inr43
=
( ) kipsinT =
= 2.54
432.72
(a) 316
dT
spi
=
where ind 5.3= ( )( ) ksis 44.65.3
2.54163 ==
pi
(b) For AISI 1035 steel, ksisus 64= for shock loading, traditional factor of safety, 15~10=N
Design factor , 94.944.6
64===
s
sN us , the design is safe ( 10N )
34. The same as 33, except that the shaft diameter is 2 in.
Solution:
SECTION 1 DESIGN FOR SIMPLE STRESSES
45
ind 75.2=
(a) 316
dT
spi
=
( )( ) ksis 3.1375.2
2.54163 ==
pi
(b) For AISI 1035 steel, ksisus 64= for shock loading, traditional factor of safety, 15~10=N
Design factor , 8.43.13
64===
s
sN us , the design is not safe ( 10
SECTION 1 DESIGN FOR SIMPLE STRESSES
46
STRESS ANALYSIS
DESIGN PROBLEMS
36. A hook is attached to a plate as shown and supports a static load of 12,000 lb. The material is to be AISI C1020, as rolled. (a) Set up strength equations for dimensions d , D , h , and t . Assume that the bending in the plate is negligible. (b) Determine the minimum permissible value of these dimensions. In estimating the strength of the nut, let dD 2.11 = . (c) Choose standard fractional dimensions which you think would be satisfactory.
Problems 36 38.
Solution: s = axial stress
ss = shear stress
(a)
22
4
41 d
F
d
Fs
pipi==
Equation (1) s
Fdpi
4=
SECTION 1 DESIGN FOR SIMPLE STRESSES
47
( ) ( ) ( )[ ] ( )2222212212 44.14
2.144
41 dD
FdD
FDD
F
DD
Fs
=
=
=
=
pipipipi
Equation (2) 244.14 ds
FD +=pi
dhF
hDF
sspipi 2.11
==
Equation (3) sds
Fhpi2.1
=
DtF
sspi
=
Equation (4) sDs
Ft
pi=
(b) Designing based on ultimate strength, Table AT 7, AISI C1020, as rolled
ksisu 65= ksisus 49=
4~3=N say 4, design factor for static load
ksiNs
s u 16465
===
ksiNs
s uss 12449
===
kipslbF 12000,12 ==
From Equation (1) ( )( ) ins
Fd 98.0161244
===
pipi
From Equation (2) ( )( ) ( ) inds
FD 53.198.044.11612444.14 22 =+=+=
pipi
From Equation (3)
( )( ) indsFh
s
27.01298.02.1
122.1
===
pipi
From Equation (4)
( )( ) inDsF
ts
21.01253.1
12===
pipi
SECTION 1 DESIGN FOR SIMPLE STRESSES
48
(c) Standard fractional dimensions
ind 1=
inD211=
inh41
=
int41
=
37. The same as 36, except that a shock load of 4000 lb. is repeatedly applied.
Solution:
(a) Same as 36.
(b) 15~10=N for shock load, based on ultimate strength say 15=N , others the same.
ksiNs
s u 41565
===
ksiNs
s uss 31549
===
kipslbF 44000 ==
From Equation (1) ( )( ) ins
Fd 13.14444
===
pipi
From Equation (2) ( )( ) ( ) inds
FD 76.113.144.144444.14 22 =+=+=
pipi
From Equation (3)
( )( ) indsFh
s
31.0313.12.1
42.1
===
pipi
From Equation (4)
( )( ) inDsF
ts
24.0376.1
4===
pipi
SECTION 1 DESIGN FOR SIMPLE STRESSES
49
(c) Standard fractional dimensions
ind811=
inD431=
inh83
=
int41
=
38. The connection between the plate and hook, as shown, is to support a load F . Determine the value of dimensions D , h , and t in terms of d if the connection is to be as strong as the rod of diameter d . Assume that dD 2.11 = , uus ss 75.0= , and that bending in the plate is negligible.
Solution:
2
41 d
Fs
pi=
sdF 241
pi=
(1)
=
NsdF u2
41
pi
SECTION 1 DESIGN FOR SIMPLE STRESSES
50
( ) ( )22212 44.141
41 dD
F
DD
Fs
=
=
pipi
( )sdDF 22 44.141
= pi
(2) ( )
=
NsdDF u22 44.1
41
pi
dhF
hDF
sspipi 2.11
==
sdhsF pi2.1=
=
=
Nsdh
NsdhF uus 75.02.12.1 pipi
(3)
=
NsdhF u59.0 pi
DtF
sspi
=
sDtsF pi=
=
=
NsDt
NsDtF uus 75.0pipi
(4)
=
NsDtF upi75.0
Equate (2) and (1) ( )
=
=
Nsd
NsdDF uu 222
4144.1
41
pipi
22 44.2 dD = dD 562.1=
Equate (3) and (1)
=
=
Nsd
NsdhF uu 2
419.0 pipi
( ) ddh 278.0
9.04==
Equate (4) and (1)
=
=
Nsd
NsDtF uu 2
4175.0 pipi
( )( )
=
=
Nsd
Ns
tdF uu 241562.175.0 pipi
( )( ) dd
t 214.0562.175.04
==
SECTION 1 DESIGN FOR SIMPLE STRESSES
51
39. (a) For the connection shown, set up strength equations representing the various methods by which it might fail. Neglect bending effects. (b) Design this connection for a load of 2500 lb. Both plates and rivets are of AISI C1020, as rolled. The load is repeated and reversed with mild shock. Make the connection equally strong on the basis of yield strengths in tension, shear, and compression.
Problems 39, 40 Solution:
(a)
=
2
415 D
Fss
pi
Equation (1) ss
FDpi54
=
( )DbtF
s2
=
Equation (2) Dts
Fb 2+=
DtF
s5
=
Equation (3) DsF
t5
=
(b) For AISI C1020, as rolled ksisy 48= (Table AT 7)
ksiss yys 286.0 ==
4=N for repeated and reversed load (mild shock) based on yield strength ksis 12
448
==
ksiss 7428
==
From Equation (1)
SECTION 1 DESIGN FOR SIMPLE STRESSES
52
ss
FDpi54
=
where kipslbF 5.22500 ==
( )( ) ins
FDs
30.0755.24
54
===
pipi say in
165
From Equation (3)
( )in
DsF
t 13.012
1655
5.25
=
== say in
325
From Equation (2)
( )inD
ts
Fb 96.11652
12325
5.22 =
+
=+= say in2
40. The same as 39, except that the material is 2024-T4, aluminum alloy.
Solution: (a) Same as 39.
(b) ) For 2024-T4, aluminum alloy ksisy 47= (Table AT 3)
ksiss yys 2555.0 ==
4=N for repeated and reversed load (mild shock) based on yield strength ksis 12
447
==
ksiss 6425
==
From Equation (1)
ss
FDpi54
=
where kipslbF 5.22500 ==
( )( ) ins
FDs
33.0655.24
54
===
pipi say in
83
From Equation (3)
SECTION 1 DESIGN FOR SIMPLE STRESSES
53
( )in
DsF
t 11.012
835
5.25
=
== say in
81
From Equation (2)
( )inD
ts
Fb 42.2832
1281
5.22 =
+
=+= say in
212
41. (a) For the connection shown, set up strength equations representing the various methods by which it might fail. (b) Design this connection for a load of 8000 lb. Use AISI C1015, as rolled, for the rivets, and AISI C1020, as rolled, for the plates. Let the load be repeatedly applied with minor shock in one direction and make the connection equally strong on the basis of ultimate strengths in tension, shear, and compression.
Problem 41. Solution:
(a)
( )DbtF
sP
= or ( )Dbt
FsP 2
43
= Equation (1)
( )2414 2
=
D
FssR
pi
Equation (2)
SECTION 1 DESIGN FOR SIMPLE STRESSES
54
DtF
sR 4= Equation (3)
(b) For AISI C1015, as rolled
ksisuR 61= , ksiss uRusR 4575.0 == For AISI C1020, as rolled
ksisuP 65=
6=N , based on ultimate strength
ksiNs
s uPP 8.10665
===
ksiNs
s uRR 1.10661
===
ksiN
ss usRsR 5.76
45===
kipslbF 88000 == Solving for D
22 DF
ssRpi
=
( ) insFD
sR
412.05.72
82
===
pipi say in
167
Solving for t
DtF
sR 4=
( )in
DsF
tR
453.01.10
1674
84
=
== say in
21
Solving for b
Using ( )DbtF
sP
=
( )inD
ts
FbP
92.1167
8.1021
8=+
=+= say in2
Using ( )DbtF
sP 243
=
SECTION 1 DESIGN FOR SIMPLE STRESSES
55
( )( )
inDts
FbP
99.11672
8.10214
83243
=
+
=+= say in2
Therefore inb 2=
inD167
=
int21
=
42. Give the strength equations for the connection shown, including that for the shear of the plate by the cotter.
Problems 42 44. Solution: Axial Stresses
212
1
4
41 D
F
D
Fs
pipi== Equation (1)
( )eDLF
s2
= Equation (2)
SECTION 1 DESIGN FOR SIMPLE STRESSES
56
eDF
s2
= Equation (3)
( ) ( )2222224
41 Da
F
Da
Fs
=
=
pipi Equation (4)
eDDF
eDD
Fs
222
222
44
41
=
=
pipi Equation (5)
Shear Stresses
ebF
ss 2= Equation (6)
( )teDLF
ss+
=
22 Equation (7)
SECTION 1 DESIGN FOR SIMPLE STRESSES
57
at
Fss
pi= Equation (8)
mDF
ss1pi
= Equation (9)
hDF
ss22
= Equation (10)
43. A steel rod, as-rolled AISI C1035, is fastened to a 7/8-in., as-rolled C1020 plate by means of a cotter that is made of as-rolled C1020, in the manner shown. (a) Determine all dimensions of this joint if it is to withstand a reversed shock load
kipsF 10= , basing the design on yield strengths. (b) If all fits are free-running fits, decide upon tolerances and allowances.
Solution: (See figure of Prob. 42) inint 875.0
87
== , ysy ss 6.0=
For steel rod, AISI C1035, as rolled ksisy 551 = ksissy 331 =
For plate and cotter, AISI C1020, as rolled ksisy 482 = ksissy 282 =
7~5=N based on yield strength say 7=N
From Equation (1) (Prob. 42)
21
41DF
Ns
sy
pi==
( )21
104755
Dpi=
inD 27.11 =
say inD4111 =
SECTION 1 DESIGN FOR SIMPLE STRESSES
58
From Equation (9)
mDF
Ns
ssy
s
1
1
pi==
m
=
411
10733
pi
inm 54.0=
say inm169
=
From Equation (3)
eDF
Ns
sy
2
1==
eDs
2
10755
==
273.12 =eD From Equation (5)
eDDF
Ns
sy
222 441
==
pi
( )( )273.14
104755
22
=
Dpi
inD 80.12 =
say inD4312 =
and 273.12 =eD
273.1431 =
e
ine 73.0=
say ine43
=
By further adjustment Say inD 22 = , ine 8
5=
From Equation (8)
at
FN
ss
sys
pi==
2
( )875.010
728
api=
ina 91.0= say ina 1=
SECTION 1 DESIGN FOR SIMPLE STRESSES
59
From Equation (4)
( )22242
DaF
Ns
sy
==
pi
( )( )22 2
104748
=
api
ina 42.2=
say ina212=
use ina212=
From Equation (7)
( )teDLF
Ns
ssy
s+
==
222
( )875.08522
10728
+
=
L
inL 80.2= say inL 3= From Equation (6)
ebF
Ns
ssy
s 22
==
b
=
852
10728
inb 2= From Equation (10)
hDF
Ns
ssy
s
222
==
( )h2210
728
=
ininh85625.0 ==
Summary of Dimensions inL 3=
inh85
=
inb 2=
int87
=
SECTION 1 DESIGN FOR SIMPLE STRESSES
60
inm169
=
ina212=
inD4111 =
inD 22 =
ine85
=
(b) Tolerances and allowances, No fit, tolerance = in010.0 inL 010.03 =
inh 010.0625.0 =
int 010.0875.0 = inm 010.05625.0 =
ina 010.0500.2 = inD 010.025.11 =
For Free Running Fits (RC 7) Table 3.1 Female Male
inb0000.00030.0
0.2
+= inb
0058.00040.0
0.2
=
allowance = 0.0040 in
inD0000.00030.0
0.22
+= inD
0058.00040.0
0.22
=
allowance = 0.0040 in
ine0000.00016.0
625.0
+= ine
0030.00020.0
625.0
=
allowance = 0.0020 in
44. A 1-in. ( 1D ) steel rod (as-rolled AISI C1035) is to be anchored to a 1-in. steel plate (as-rolled C1020) by means of a cotter (as rolled C1035) as shown. (a) Determine all the dimensions for this connection so that all parts have the same ultimate strength as the rod. The load F reverses direction. (b) Decide upon tolerances and allowances for loose-running fits.
Solution: (Refer to Prob. 42)
(a) For AISI C1035, as rolled ksisu 851 = ksisus 641 =
For AISI C1020, as rolled
SECTION 1 DESIGN FOR SIMPLE STRESSES
61
ksisu 652 = ksisus 482 =
Ultimate strength Use Equation (1)
( ) ( ) kipsDsF uu 8.6614185
41 22
11 =
=
= pipi
Equation (9) mDsF usu 11pi=
( )( )( )m1648.66 pi= inm 33.0=
say inm83
=
From Equation (3) eDsF uu 21=
( ) eD2858.66 = 7859.02 =eD
From Equation (5)
= eDDsF uu 2
224
11
pi
( )
= 7859.0
41858.66 22Dpi
inD 42.12 =
say inD8312 =
7859.08312 =
= eeD
ine 57.0=
say ine169
=
From Equation (4) ( )
=
22
2
41
2DasF uu pi
( )
=
22
831
41658.66 api
ina 79.1=
say ina431=
From Equation (8)
SECTION 1 DESIGN FOR SIMPLE STRESSES
62
atsF usu pi2= ( )( )( )( )1488.66 api=
ina 44.0=
say ina21
=
use ina431=
From Equation (2) ( )eDLsF uu 22 =
( )
=
169
831658.66 L
inL 20.3=
say inL413=
From Equation (7) ( )teDLsF usu = 222
( ) ( )1169
8314828.66
= L
inL 51.1=
say inL211=
use inL413=
From Equation (6) ebsF usu 12=
( ) b
=
1696428.66
inb 93.0= say inb 1= From Equation (10)
hDsF usu 212=
( ) h
=
8316428.66
inh 38.0=
say inh83
=
Dimensions
inL413=
SECTION 1 DESIGN FOR SIMPLE STRESSES
63
inh83
=
inb 1= int 1=
inm83
=
ina431=
inD 11 =
inD8312 =
ine169
=
(b) Tolerances and allowances, No fit, tolerance = in010.0 inL 010.025.3 = inh 010.0375.0 =
int 010.0000.1 = inm 010.0375.0 =
ina 010.075.1 = inD 010.0000.11 =
For Loose Running Fits (RC 8) Table 3.1 Female Male
inb0000.00035.0
0.1
+= inb
0065.00045.0
0.1
=
allowance = 0.0045 in
inD0000.00040.0
375.12
+= inD
0075.00050.0
375.12
=
allowance = 0.0050 in
ine0000.00028.0
5625.0
+= ine
0051.00035.0
5625.0
=
allowance = 0.0035 in
45. Give all the simple strength equations for the connection shown. (b) Determine the ratio of the dimensions a , b , c , d , m , and n to the dimension D so that the connection will be equally strong in tension, shear, and compression. Base the calculations on ultimate strengths and assume uus ss 75.0= .
SECTION 1 DESIGN FOR SIMPLE STRESSES
64
Problems 45 47. Solution: (a) Neglecting bending
Equation (1):
=
2
41 DsF pi
Equation (2):
=
2
412 csF s pi
Equation (3): ( )bcsF 2= Equation (4): ( )acsF = Equation (5): ( )[ ]bcdsF = 2 Equation (6): ( )mbsF s 4= Equation (7): ( )nbsF s 2= Equation (8): ( )acdsF =
(b) Ns
s u= and Ns
s uss =
Therefore sss 75.0=
Equate (2) and (1)
=
=
22
41
412 DscsF s pipi
=
2241
2175.0 Dscs
Dc 8165.0= Equate (3) and (1)
( )
==
2
412 DsbcsF pi
( ) 2418165.02 DDb pi=
Db 4810.0=
SECTION 1 DESIGN FOR SIMPLE STRESSES
65
Equate (4) and (1)
==
2
41 DssacF pi
( ) 2418165.0 DDa pi=
Da 9619.0= Equate (5) and (1)
( )[ ]
==
2
412 DsbcdsF pi
( )( ) 2414810.08165.02 DDd pi=
Dd 6329.1= Equate (6) and (1)
( )
==
2
414 DsmbsF s pi
( )( ) 2414810.0475.0 DDm pi=
Dm 5443.0= Equate (7) and (1)
( )
==
2
412 DsnbsF s pi
( )( ) 2414810.0275.0 DDn pi=
Dn 0886.1= Equate (8) and (1)
( )
==
2
41 DsacdsF pi
( ) 2418165.06329.1 DaDD pi=
Da 9620.0=
Summary Da 9620.0= Db 4810.0= Dc 8165.0= Dd 6329.1= Dm 5443.0=
Dn 0886.1=
SECTION 1 DESIGN FOR SIMPLE STRESSES
66
46. The same as 45, except that the calculations are to be based on yield strengths. Let ysy ss 6.0= .
Solution: (Refer to Prob. 45) (a) Neglecting bending
Equation (1):
=
2
41 DsF pi
Equation (2):
=
2
412 csF s pi
Equation (3): ( )bcsF 2= Equation (4): ( )acsF = Equation (5): ( )[ ]bcdsF = 2 Equation (6): ( )mbsF s 4= Equation (7): ( )nbsF s 2= Equation (8): ( )acdsF =
(b) Ns
sy
= and Ns
ssy
s =
Therefore sss 6.0=
Equate (2) and (1)
=
=
22
41
412 DscsF s pipi
=
2241
216.0 Dscs
Dc 9129.0= Equate (3) and (1)
( )
==
2
412 DsbcsF pi
( ) 2419129.02 DDb pi=
Db 4302.0=
Equate (4) and (1)
==
2
41 DssacF pi
( ) 2419129.0 DDa pi=
Da 8603.0=
SECTION 1 DESIGN FOR SIMPLE STRESSES
67
Equate (5) and (1) ( )[ ]
==
2
412 DsbcdsF pi
( )( ) 2414302.09129.02 DDd pi=
Dd 8257.1= Equate (6) and (1)
( )
==
2
414 DsmbsF s pi
( )( ) 2414302.046.0 DDm pi=
Dm 7607.0= Equate (7) and (1)
( )
==
2
412 DsnbsF s pi
( )( ) 2414302.026.0 DDn pi=
Dn 5214.1= Equate (8) and (1)
( )
==
2
41 DsacdsF pi
( ) 2419129.08257.1 DaDD pi=
Da 8604.0=
Summary Da 8604.0= Db 4302.0= Dc 9129.0= Dd 8257.1= Dm 7607.0=
Dn 5214.1=
47. Design a connection similar to the one shown for a gradually applied and reversed load of 12 kips. Base design stresses on yield strengths and let the material be AISI C1040 steel, annealed. Examine the computed dimensions for proportion, making changes that you deem advisable.
Solution: (See figure in Prob. 45 and refer to Prob. 46)
SECTION 1 DESIGN FOR SIMPLE STRESSES
68
4=N based on yield strength for gradually applied and reversed load. For AISI C1040, annealed
ksisy 47= (Fig. AF 7) ksiss ysy 286.0 ==
ksiNs
sy 75.11
447
===
=
2
41 DsF pi
=
2
4175.1112 Dpi
inD 14.1=
say inD811=
inDa 97.08118604.08604.0 =
==
but Da >
say ina411=
inb 48.08114302.0 =
=
say inb21
=
inc 030.18119129.0 =
=
say inc 1=
ind 05.28118257.1 =
=
say ind 2=
inm 86.08117607.0 =
=
say inm87
=
inn 71.18115214.1 =
=
say inn431=
Dimension:
ina411=
SECTION 1 DESIGN FOR SIMPLE STRESSES
69
inb21
=
inc 1= ind 2=
inm87
=
inn431=
inD811=
48. Give all the strength equations for the union of rods shown.
Problems 48 68. Solution:
=
2
41 dsF pi Equation (1)
( )adsF s pi= Equation (2)
( )tcsF s 2= Equation (3)
SECTION 1 DESIGN FOR SIMPLE STRESSES
70
( )[ ]beDsF s = 2 Equation (4)
setF = Equation (5)
( )teDsF = Equation (6)
( )
=
22
41
eksF pi Equation (7)
( ) ( )
= tememsF 22
41
pi Equation (8)
( )efsF s 2= Equation (9)
SECTION 1 DESIGN FOR SIMPLE STRESSES
71
= etesF 2
41
pi Equation (10)
49-68. Design a union-of-rods joint similar to that shown for a reversing load and material given in the accompanying table. The taper of cotter is to be in. in 12 in. (see 172). (a) Using design stresses based on yield strengths determine all dimensions to satisfy the necessary strength equations. (b) Modify dimensions as necessary for good proportions, being careful not to weaken the joint. (c) Decide upon tolerances and allowances for loose fits. (d) Sketch to scale each part of the joint showing all dimensions needed for manufacture, with tolerances and allowances.
Prob. No. Load, lb. AISI No., As Rolled
49 3000 1020 50 3500 1030 51 4000 1117 52 4500 1020
52 5000 1015 54 5500 1035 55 6000 1040 56 6500 1020
57 7000 1015 58 7500 1118 59 8000 1022 60 8500 1035
61 9000 1040 62 9500 1117 63 10,000 1035 64 10,500 1022
65 11,000 1137 66 11,500 1035 67 12,000 1045 68 12,500 1030
SECTION 1 DESIGN FOR SIMPLE STRESSES
72
Solution: (For Prob. 49 only)
(a) For AISI 1020, as rolled
ksisy 48= ( ) ksiss yys 8.28486.06.0 ===
For reversing load, 4=N based on yield strength
ksiNs
sy 12
448
===
ksiNs
sys
s 2.748.28
===
kipslbF 33000 ==
Equation (1)
=
2
41 dsF pi
=
2
41123 dpi
ind 5642.0=
say ind169
=
Equation (2) ( )adsF s pi= ( )
=
1692.73 api
ina 236.0=
say ina41
=
Equation (5) setF =
et123 = 25.0=et
Equation (10)
= etesF 2
41
pi
= 25.0
41123 2epi
ine 798.0=
say ine1613
=
25.0=et
SECTION 1 DESIGN FOR SIMPLE STRESSES
73
25.01613
=
t
int 308..0=
say int165
=
Equation (6) ( )teDsF =
=
165
1613123 D
inD 6125.1=
say inD851=
Equation (4) ( )[ ]beDsF s = 2
= b
1613
85122.73
inb 256.0=
say inb41
=
Equation (7) ( )
=
22
41
eksF pi
=
22
1613
41123 kpi
ink 989.0= say ink 1= Equation (9)
( )efsF s 2= ( ) f
=
161322.73
inf 256.0= say inf
41
=
Equation (8) ( ) ( )
= tememsF 22
41
pi
=
165
1613
1613
41123
22 mmpi
SECTION 1 DESIGN FOR SIMPLE STRESSES
74
2539.03125.05185.07854.025.0 2 += mm 05146.03125.07854.0 2 = mm
06552.03979.02 = mm inm 032.1=
say inm 1= Equation (3)
( )tcsF s 2= ( ) c
=
16522.73
inc 667.0=
say inc1611
=
DIMENSIONS:
ind169
=
ina41
=
inb41
=
inc1611
=
inf41
=
ine1613
=
int165
=
ink 1=
inD851=
inm 1=
(b) Modified dimensions ind
169
=
ina41
=
inb43
=
inc1611
=
SECTION 1 DESIGN FOR SIMPLE STRESSES
75
inf21
=
ine1613
=
int165
=
ink 1=
inD851=
inm411=
(c) Tolerances and allowances No fit, in010.0
ind 010.05625.0 = ina 010.0250.0 = inf 010.0500.0 = inD 010.0625.1 = ink 010.0000.1 = inm 010.0250.1 =
Fits, Table 3.1, loose-running fits, say RC 8
Female Male
inb0000.00035.0
750.0
+= inb
0065.00045.0
750.0
=
allowance = 0.0045 in
inc0000.00028.0
6875.0
+= inc
0051.00035.0
6875.0
=
allowance = 0.0035 in
ine0000.00035.0
8125.0
+= ine
0065.00045.0
8125.0
=
allowance = 0.0045
int0000.00022.0
3125.0
+= int
0040.00030.0
3125.0
=
allowance = 0.0030 in
SECTION 1 DESIGN FOR SIMPLE STRESSES
76
(d)
ROD
COTTER
SECTION 1 DESIGN FOR SIMPLE STRESSES
77
SOCKET
CHECK PROBLEMS
69. The connection shown has the following dimensions: ind411= , inD
212= ,
inD2111 = , inh 8
5= , int
21
= ; it supports a load of 15 kips. Compute the tensile,
compressive, and shear stresses induced in the connection. What is the corresponding design factor based on the yield strength if the rod and nut are made of AISI C1045, as rolled, and the plate is structural steel (1020)?
SECTION 1 DESIGN FOR SIMPLE STRESSES
78
Problem 69. Solution: Tensile Stresses
(1) ksid
Fs 22.12
411
41
15
41 221
=
==
pipi
(2) ksiD
Fs 4.8
211
41
15
41 22
1
2 =
==
pipi
Compressive Stress
(3) ( ) ksiDDF
s 78.4
211
212
41
15
41 222
12
3 =
=
=
pipi
Shear Stresses
(4) ksiDtF
ss 82.3
21
212
154
=
==
pipi
(5) ksihD
Fss 09.5
85
211
151
5=
==
pipi
For AISI C1045, as rolled (rod and nut) ksisy 591 =
( ) ksiss yys 4.35596.06.01 === For structural steel plate (1020)
ksisy 482 = ( ) ksiss yys 8.28486.06.01 ===
Solving for design factor
SECTION 1 DESIGN FOR SIMPLE STRESSES
79
(1) 83.422.12
591
11
===
s
sN y
(2) 95.649.8
592
21
===
s
sN y
(3) 04.1078.4
483
32
===
s
sN y
(4) 54.782.3
8.28
4
24 ===
s
ys
s
sN
(5) 96.609.5
4.35
5
15 ===
s
ys
s
sN
The corresponding design factor is 83.4=N
70. In the figure, let inD43
= , int167
= , inb433= , and let the load, which is applied
centrally so that it tends to pull the plates apart, be 15 kips. (a) Compute the stresses in the various parts of the connection. (b) If the material is AISI C1020, as rolled, what is the design factor of the connection based on yield strengths?
Problem 70. Solution:
(a) Tensile stresses
( ) ksiDbtF
s 43.11
43
433
167
151 =
=
=
( )( )
ksiDbt
Fs 43.11
432
433
167
1543
243
2 =
=
=
Compressive bearing stress
ksiDtF
s 43.11
167
434
1543
=
==
SECTION 1 DESIGN FOR SIMPLE STRESSES
80
Shearing stress
( ) ( )ksi
D
Fss 24.4
24315
2414
22
4 =
=
=
pipi
(b) For AISI C1020, as rolled ksisy 48=
ksiss yys 8.286.0 ==
s
sN y= or
s
ys
s
sN =
Using s
sN y=
2.443.11
48===
s
sN y
Using s
ys
s
sN =
8.624.4
8.28===
s
ys
s
sN
Therefore the design factor is 2.4=N
71. For the connection shown, let ina1615
= , inb169
= , inc43
= , ind211= ,
inD43
= , innm1615
== . The material is AISI C1040, annealed (see Fig. AF 1). (a) For a load of 7500 lb., compute the various tensile, compressive, and shear stresses. Determine the factor of safety based on (b) ultimate strength, (c) yield strengths.
Problem 71.
Solution:
(a) Tensile stresses
SECTION 1 DESIGN FOR SIMPLE STRESSES
81
ksiD
Fs 98.16
43
41
5.7
41 221
=
==
pipi
( ) ksicdbF
s 89.8
43
211
1692
5.722
=
=
=
( ) ksicdaF
s 67.10
43
211
1615
5.73 =
=
=
Compressive Stresses (Bearing) ksi
bcF
s 89.8
43
1692
5.724
=
==
ksiac
Fs 67.10
43
1615
5.75 =
==
Shearing Stresses
ksimbF
ss 56.3
169
16154
5.746
=
==
ksinbF
ss 11.7
169
16152
5.727
=
==
For AISI C1040, annealed,Fig. AF 1 ksisy 47= ksisu 79=
ksiss yys 286.0 == ksiss uus 44760 .. ==
(b) Based on ultimate strength 65.4
98.1679
1
===
s
sN u
(c) Based on yield strength 77.2
98.1647
1
===
s
sN y
72. The upper head of a 60,000-lb. tensile-testing machine is supported by two steel rods, one of which A is shown. These rods A are attached to the head B by split rings C. The test specimen is attached to the upper head B so that the tensile force
SECTION 1 DESIGN FOR SIMPLE STRESSES
82
in the specimen pulls down on the head and exerts a compressive force on the rods A. When the machine is exerting the full load, compute (a) the compressive stress in the rods, (b) the bearing stress between the rods and the rings, (c) the shearing stress in the rings,
Problem 72. Solution:
lbsF 000,60=
(a) ( )( )
ksipsisc 75.11753,113
213
41
2000,602
2==
=
pi
(b) ( )( )
ksipsisb 19.10186,10
2134
41
2000,602
2
==
=
pi
(c) ( )( )( ) ksipsisc 18.3183,3132000,60
===
pi
DEFORMATIONS
73. A load of 22,000 lb. is gradually applied to a 2-in. round rod, 10 ft. long. The total elongation is observed to be 0.03 in. If the stretching is entirely elastic, (a) what is the modulus of elasticity, and (b) what material would you judge it to be, wrought iron or stainless steel (from information available in the tables)? (c) How much energy is absorbed by the rod? (d) Suppose that the material is aluminum alloy 3003-H14; compute its elongation for the same load. Is this within elastic action?
Solution: lbsF 000,22=
inD 2= inftL 12010 ==
in03.0=
SECTION 1 DESIGN FOR SIMPLE STRESSES
83
(a) EAFL
= ( )( )( )( )( ) psiD
FLA
FLE 622 1028203.0120000,2244
====pipi
(b) Use both stainless steel, Table AT 4, psiE 61028= and wrought iron , Table AT 7, psiE 61028= .
(c) Energy absorbed = ( )( ) inlbF == 33003.0000,2221
21
(d) For Aluminum alloy, 3003-H14
psiE 61010= ksisy 21=
( )( )( )( )( ) inDE
FLEAFL 084.0
21010120000,2244
262 ====
pipi
( )( )( ) ysksipsiD
Fs
SECTION 1 DESIGN FOR SIMPLE STRESSES
84
( )( )( ) ysksipsiD
Fs >==== 0.28011,28
2000,8844
22 pipi, not within the elastic limit, therefore
not valid.
75. (a) A square bar of SAE 1020, as rolled, is to carry a tensile load of 40 kips. The bar is to be 4 ft. long. A design factor of 5 based on the ultimate stress is desired. Moreover, the total deformation should not exceed 0.024 in. What should be the dimensions of the section? (b) Using SAE 1045, as rolled, but with the other data the same, find the dimensions. (c) Using SAE 4640, OQT 1000 F, but with other data the same as in (a), find the dimensions. Is there a change in dimensions as compared with part (b)? Explain the difference or the lack of difference in the answers.
Solution: inftL 484 ==
(a) For SAE 1020, as rolled ksisu 65= , ksiE 000,30=
AF
Ns
s u ==
240
565
x=
inx 754.1=
EAFL
= ( )( )
( ) 2000,304840024.0
x=
inx 633.1=
Therefore say inx431=
(b) For SAE 1045, as rolled ksisu 96= , ksiE 000,30=
AF
Ns
s u ==
240
596
x=
inx 443.1=
EAFL
= ( )( )
( ) 2000,304840024.0
x=
inx 633.1=
SECTION 1 DESIGN FOR SIMPLE STRESSES
85
Therefore say inx851=
(c) For SAE 4640, as rolled ksisu 152= , ksiE 000,30=
AF
Ns
s u ==
240
5152
x=
inx 15.1=
EAFL
= ( )( )
( ) 2000,304840024.0
x=
inx 633.1=
Therefore say inx851=
There is lack of difference in the answers due to same dimensions required to satisfy the required elongation.
76. The steel rails on a railroad track are laid when the temperature is 40 F. The rails are welded together and held in place by the ties so that no expansion is possible due to temperature changes. What will be the stress in the rails when heated by
the sun to 120 F (i1.29)? Solution:
LtL
LEs
==
For steel Finin = 000007.0 psiE 61030=
( )( )( )6103040120000007.0 == tEs psis 800,16=
77. Two steel rivets are inserted in a riveted connection. One rivet connects plates that have a total thickness of 2 in., while the other connects plates with a total thickness of 3 in. If it is assumed that, after heading, the rivets cool from 600 F and that the coefficient of expansion as given in the Text applies, compute the stresses in each rivet after it has cooled to a temperature of 70 F, (no external load). See i1.29. Also assume that the plates are not deformed under load. Is such a stress likely? Why is the actual stress smaller?
SECTION 1 DESIGN FOR SIMPLE STRESSES
86
Solution: tEs =
For steel Finin = 000007.0 psiE 61030=
( )( )( ) ksis 30.111000,3070600000007.0 ==
The stress is unlikely because it is near the ultimate strength of steel. Actual stress must be smaller to allow for safety.
78. Three flat plates are assembled as shown; the center one B of chromium steel, AISI 5140 OQT 1000 F, and the outer two A and C of aluminum alloy 3003-H14, are fastened together so that they will stretch equal amounts. The steel plate is 2 x in., the aluminum plates are each 2 x 1/8 in., inL 30= ., and the load is 24,000 lb. Determine (a) the stress in each plate, (b) the total elongation, (c) the energy absorbed by the steel plate if the load is gradually applied, (d) the energy absorbed by the aluminum plate. (e) What will be the stress in each plate if in addition to the load of 24,000 lb. the temperature of the assembly is increased by 100 F?
Problem 78, 79. Solution: For chromium steel, AISI 5140 OQT 1000F (Table AT 7)
Finin = 000007.01 ksipsiE 000,301030 61 ==
For aluminum alloy, 3003-H14 (Table AT 3) Finin = 0000129.02
ksipsiE 000,101010 62 ==
(a) CA PP = FPPP CBA =++
(1) kipsFPP BA 242 ==+ ( ) 22 25.08
12 inA =
=
( ) 21 1212 inA =
=
SECTION 1 DESIGN FOR SIMPLE STRESSES
87
BA =
1122 EALP
EALP BA
=
( )( ) ( )( )000,301000,1025.0BA PP
=
(2) AB PP 12=
(1) kipsPP AA 24122 =+ kipsPA 714.1=
( ) kipsPB 568.20714.112 ==
Stresses: Aluminum plate
ksiAP
ss ACA 856.625.0714.1
2
====
Chromium steel plate
ksiAP
s BB 568.201568.20
1
===
(b) ( )( )( )( ) inEALPA 021.0
000,1025.030714.1
22
===
(c) Energy absorbed by steel plate ( )( ) inkipsPB === 216.0021.0568.2021
21
(d) Energy absorbed by aluminum plate ( )( ) inkipsPA === 018.0021.0714.121
21
(e) kipsFPP BA 242 ==+ BTAT BA
+=+ tL
AT= 2
tLBT
= 1 ( )( )( ) in
AT0387.0100300000129.0 ==
( )( )( ) inBT
021.010030000007.0 == ( )
( )( ) AAA
A PP
EALP 012.0
000,1025.030
22
===
( )( )( ) B
BBB P
PEALP 001.0
000,30130
11
===
Then BA PP 001.0021.0012.00387.0 +=+
( )AA PP 224001.0012.00177.0 =+ AA PP 002.0024.0012.00177.0 =+
SECTION 1 DESIGN FOR SIMPLE STRESSES
88
kipsPA 45.0= ( ) kipsPB 1.2345.0224 ==
Stresses: Aluminum plate
ksiAP
s AA 8.125.045.0
2
===
Chromium steel plate
ksiAP
s BB 1.2311.23
1
===
79. The same as 78, except that the outer plates are aluminum bronze, B150-1, annealed.
Solution:
For aluminum bronze, B150-1, annealed (Table AT 3) ksiE 000,152 =
Finin = 0000092.02
(a)
(1) kipsFPP BA 242 ==+ BA =
1122 EALP
EALP BA
=
( )( ) ( )( )000,301000,1525.0BA PP
=
(2) AB PP 8= kipsPP AA 2482 =+
kipsPA 4.2= ( ) kipsPB 2.194.28 ==
Stresses: Aluminum plate
ksiAP
ss ACA 6.925.04.2
2
====
Chromium steel plate
ksiAP
s BB 2.1912.19
1
===
SECTION 1 DESIGN FOR SIMPLE STRESSES
89
(b) ( )( )( )( ) inEALPA 019.0
000,1525.0304.2
22
===
(c) Energy absorbed by steel plate ( )( ) inkipsPB === 182.0019.02.1921
21
(d) Energy absorbed by aluminum plate ( )( ) inkipsPA === 023.0019.04.221
21
(e) kipsFPP BA 242 ==+ BTAT BA
+=+ tL
AT= 2
tLBT
= 1 ( )( )( ) in
AT0276.0100300000092.0 ==
( )( )( ) inBT
021.010030000007.0 == ( )
( )( ) AAA
A PP
EALP 008.0
000,1525.030
22
===
( )( )( ) B
BBB P
PEALP 001.0
000,30130
11
===
Then BA PP 001.0021.0008.00276.0 +=+
( )AA PP 224001.0008.00066.0 =+ AA PP 002.0024.0008.00066.0 =+
kipsPA 74.1= ( ) kipsPB 52.2074.1224 ==
Stresses: Aluminum plate
ksiAP
s AA 96.625.074.1
2
===
Chromium steel plate
ksiAP
s BB 52.20152.20
1
===
80. A machine part shown is made of AISI C1040, annealed steel; inL 151 = .,
inL 62 = ., inD 43
1 = ., and inD 21
2 = . Determine (a) the elongation due to a force lbF 6000= ., (b) the energy absorbed by each section of the part if the load is
gradually applied.
SECTION 1 DESIGN FOR SIMPLE STRESSES
90
Problems 80, 81 Solution: For AISI C1040, annealed steel
psiE 61030=
(a) 21 += ( )( )( )
inEA
FL 0068.01030
43
4
1560006
21
11 =
==
pi
( )( )( )
inEA
FL 0061.01030
21
4
660006
22
22 =
==
pi
in0129.00061.00068.021 =+=+=
(b) Energy absorbed ( )( ) inlbFU ==== 4.200068.06000
21
21
11
( )( ) inlbFU ==== 3.180061.0600021
21
22
81. A rod as shown is made of AISI 2340 steel, OQT 1000 F, and has the following dimensions: inL 201 = ., inL 122 = ., inD 8
71 = ., and inD 4
32 = . The unit strain at
point A is measured with a strain gage and found to be 0.0025 in./in. Determine (a) the total elongation, and (b) the force on the rod.
Solution:
For steel ksiE 30000=
(a) EA
FL 22
2==
SECTION 1 DESIGN FOR SIMPLE STRESSES
91
EAF 2=
1
2
1
21
1
2
1
121 LD
DLAA
EAELA
=
==
( ) inLLDD
T 067.0122087430025.0
2
21
2
1
221 =
+
=
+
=+=
(b) ( ) kipsEAF 13.33000,3043
40025.0
2
2 =
==
pi
82. A rigid bar H is supported as shown in a horizontal position by the two rods (aluminum 2024 T4, and steel AISI 1045, as rolled), whose ends were both in contact with H before loading was applied. The ground and block B are also to be considered rigid. What must be the cross-sectional area of the steel rod if, for the assembly, 2=N based on the yield strengths?
Problem 82. Solution:
For aluminum 2024-T4 (Table AT 3) ksisy 471 = , ksiE 600101 ,=
For steel AISI 1045, as rolled (Table AT 7) ksisy 592 = , ksiE 000,302 =
[ ]0= GM ( ) ( ) ( )20241224 21 =+ RR 402 21 =+ RR Equation (1)
SECTION 1 DESIGN FOR SIMPLE STRESSES
92
122421
=
21 2 =
11
111 AE
LR=
22
222 AE
LR=
inftL 9681 == inftL 144122 ==
21 5.0 inA =
21 2 =
22
22
11
11 2AELR
AELR
=
( )( )( )
( )( ) 2
21
000301442
506001096
A
RR
,.,=
2
21
530A
RR
.=
But Ns
AR
sy2
2
22 ==
5.292
592
2==
AR
( ) kipsR 64155295301 ... ==
Ns
AR
sy1
1
11 ==
247
5.01
=R
kipsR 75.111 = use kipsR 75.111 =
( ) kipsR 5.1675.112402 == 22
2 56.05.295.16
5.29inRA ===
SECTION 1 DESIGN FOR SIMPLE STRESSES
93
83. The bar shown supports a static load kipsF 5.2= with 0= ; ind 3= .,
inL 10= ., inh432= . inb 1= . It is made of AISI 1035, as rolled. (a) How far
does point C move upon gradual application of the load if the movement of A and B is negligible? (b) How much energy is absorbed?
Problem 83. Solution:
[ ] = 0AM ( )FLddRB += ( )( )5.21033 +=BR kipsRB 83.10= [ ] = 0BM LFdRA =
( )5.2103 =AR kipsRA 33.8=
SECTION 1 DESIGN FOR SIMPLE STRESSES
94
3= xRxRM BA
383.1033.822
== xxdy
ydEIM
122 3415.5165.4 Cxx
dydyEI +=
2133 3805.1388.1 CxCxxEIy ++=
When 0=x , 0=y ( ) ( ) ( ) 2133 00805.10388.10 CCEI ++=
02 =C When 3=x , 0=y
( ) ( ) ( ) 030805.13388.10 133 ++= CEI 492.121 =C
xxxEIy 492.123805.1388.1 33 = When inLdx 13=+=
( ) ( ) 108213492.1210805.113388.1 33 ==EIy For AISI 1035, as rolled , ksiE 000,30=
( )( ) 433 7331.112
75.2112
inbhI ===
1082=EIy ( )( ) 10827331.1000,30 =y
iny 021.0= , upward.
SECTION 1 DESIGN FOR SIMPLE STRESSES
95
PRESSURE VESSELS
84. A storage tank for air, 36 in. in diameter, is to withstand an internal pressure of 200 psi with a design factor of 4 based on us . The steel has the strength equivalent of C1020 annealed and the welded joints should have a relative strength (efficiency) of 90 %. Determine a suitable plate thickness. Compute the stress on a diametral section and compare it with the longitudinal stress.
Solution: For C1020 annealed
ksisu 57=
ksiNs
s u 25.144
57===
Solving for plate thickness
tpD
s2
=
ksipsip 2.0200 == inD 36=
( )( )( )9.02
362.525.14t
s ==
int 281.0=
say int165
=
Stress on diametral section ( )( )
( )ksi
t
pDs 40.6
9.01654
362.04
=
==
Stress on longitudinal section ( )( )
( )ksi
t
pDs 80.12
9.01652
362.02
=
==
Stress on diametral section < stress on longitudinal section
85. A spherical air tank stores air at 3000 psig. The tank is to have an inside diameter of 7 in. (a) What should be the wall thickness and weight of the tank if it is made of 301, -hard, stainless steel, with a design factor of 1.5 based on the yield strength and a joint efficiency of 90 %. (b) Compute the wall thickness and weight if annealed titanium (B265, gr. 5) is used? (c) What is the additional saving in weight if the titanium is hardened? Can you think of circumstances for which the higher cost of titanium would be justified?
SECTION 1 DESIGN FOR SIMPLE STRESSES
96
Solution:
(a) For 301, hard, stainless steel ksisy 75= (Table AT 4)
ksiNs
sy 50
5.175
===
ksipsip 33000 ==
tpD
s4
=
( )( )( )90.04
7350t
=
int 117.0=
3286.0 inlb= ( ) ( )( ) lbtDtrW 2.5286.0117.074 222 ==== pipipi
(b) For annealed titanium B265, gr. 5 ksisy 130= (Table AT 3)
ksiNs
sy 67.86
5.1130
===
ksipsip 33000 ==
tpD
s4
=
( )( )( )90.04
7367.86t
=
int 061.0=
3160.0 inlb= ( ) ( )( ) lbtDtrW 5.1160.0061.074 222 ==== pipipi
(c) For hardened titanium ksisy 158= (Table AT 3)
ksiNs
sy 105
5.1158
===
ksipsip 33000 ==
tpD
s4
=
( )( )( )90.04
73105t
=
SECTION 1 DESIGN FOR SIMPLE STRESSES
97
int 056.0=
3160.0 inlb= ( ) ( )( ) lbtDtrW 38.1160.0056.074 222 ==== pipipi
Savings in weight = ( ) %8%10050.1
38.150.1=
Circumstances: less in weight and small thickness.
86. Decide upon a material and estimate a safe wall thickness of a cylindrical vessel to contain helium at 300 F and 2750 psi. The welded joint should have a relative strength 87 %, and the initial computations are to be for a 12-in.-diameter, 30-ft.-long tank. (Note: Mechanical properties of metals at this low temperature are not available in the Text. Refer to INCO Nickel Topics, vol. 16, no. 7, 1963, or elsewhere.)
Solution: From Kents Handbook, Table 8 Material Hot Rolled Nickel At 300 F, ksisu 100= , 4=N (Table 1.1)
ksiNs
s u 254
100===
tpD
s2
=
ksipsip 75.22750 == inD 12=
%87= ( )( )
( )87.021275.225
ts ==
int 759.0=
say int43
=
CONTACT STRESSES
87. (a) A 0.75-in. diameter roller is in contact with a plate-cam surface whose width is 0.5-in. The maximum load is 2.5 kips where the radius of curvature of the cam surface is 3.333 in. Compute the Hertz compressive stress. (b) The same as (a) except that the follower has a plane flat face. (c) The same as (a) except that the roller runs in a grooved face and contacts the concave surface. (d) What is the maximum shear stress for part (a) and how far below the surface does it exist?
Solution:
SECTION 1 DESIGN FOR SIMPLE STRESSES
98
(a) inr 75.02 1 = , inr 375.01 = inr 333.32 =
kipsF 5.2= inb 5.0=
21
21
21max 11
1135.0
+
+
=
EEb
rrF
sc
ksiE 000,30=
( )ksisc 279
000,3025.0
333.31
375.015.235.0
21
max =
+
=
(b) ( )
ksisc 126
000,3025.0
333.31
333.315.235.0
21
max =
+
=
(c) ( )
ksisc 249
000,3025.0
333.31
375.015.235.0
21
max =
=
(d) Maximum shear stress ( ) ksiss cs 842793.03.0 maxmax ===
Location:
( ) ( )( )in
rr
EEs
w
c
023.0
333.31
375.01
000,3023.012794
11
1114 2
21
21
2max
=
+
=
+
+
=
88. Two 20o involute teeth are in contact along a line where the radii of curvature of the profiles are respectively 1.03 and 3.42 in. The face width of the gears is 3 in. If the maximum permissible contact stress for carburized teeth is 200 ksi, what normal load may these teeth support?
SECTION 1 DESIGN FOR SIMPLE STRESSES
99
Solution: inr 03.11 = inr 42.32 =
inb 3= ksisc 200max =
21
21
21max 11
1135.0
+
+
=
EEb
rrF
sc
ksiE 000,30=
21
max
000,3023
42.31
03.1135.0
200
+
==
Fsc
kipsF 18=
TOLERANCES AND ALLOWANCES
89. The pin for a yoke connection has a diameter of D of in., a total length of 2 in., with a head that is 1 in. in diameter and 3/8 in. thick. The tolerance on D (both pin and hole) is 0.003 in., with an allowance of 0.001 in., basic-hole system. Sketch the pin showing all dimensions with appropriate tolerances.
Solution: inD 75.0=
For pin
inD003.0000.0
749.0
+=
For hole
inD000.0003.0
750.0
+=
Sketch
SECTION 1 DESIGN FOR SIMPLE STRESSES
100
90. A shaft with a nominal diameter of 8 in. is to fit in a hole. Specify the allowance, tolerances, and the limit diameters of the shaft and hole on a sketch for: (a) a close sliding fit, (b) a precision-running fit, (c) medium-running fit, (d) a loose-running fit.
Solution: inD 8=
(a) For close-sliding fit, RC 1
Hole, in Shaft, in +0.0008 - 0.0006 -0.0000 -0.0012
Allowance = 0.0006 in With tolerances,
Hole inD0000.00008.0
0000.8
+=
Shaft inD0006.00000.0
9994.7
+=
Limit dimension, Hole intoD 0008.80000.8= Shaft intoD 9988.79994.7= Sketch
SECTION 1 DESIGN FOR SIMPLE STRESSES
101
(b) For a precision-running fit, RC 3 Hole, in Shaft, in +0.0012 -0.0020 -0.0000 -0.0032 Allowance = 0.0020 in With tolerances,
Hole inD0000.00012.0
0000.8
+=
Shaft inD0012.00000.0
9980.7
+=
Limit dimension, Hole intoD 0012.80000.8= Shaft intoD 9968.79980.7= Sketch
(c) For medium-running fit, RC5, RC 6. Say RC 5
Hole, in Shaft, in +0.0018 -0.0040 -0.0000 -0.0058
Allowance = 0.0040 in With tolerances,
Hole inD0000.00018.0
0000.8
+=
Shaft inD0018.00000.0
9960.7
+=
Limit dimension, Hole intoD 0018.80000.8= Shaft intoD 9942.79960.7= Sketch
SECTION 1 DESIGN FOR SIMPLE STRESSES
102
(d) For loose-running fit, RC 8, RC 9. Say RC 8
Hole, in Shaft, in +0.0070 -0.0100 -0.0000 -0.0145
Allowance = 0.010 in With tolerances,
Hole inD0000.00070.0
0000.8
+=
Shaft inD0045.00000.0
9900.7
+=
Limit dimension, Hole intoD 0070.80000.8= Shaft intoD 9855.79900.7= Sketch
91. The same as 90, except that the nominal diameter is 4 in.
Solution: inD 4=
(a) For close-sliding fit, RC 1
SECTION 1 DESIGN FOR SIMPLE STRESSES
103
Hole, in Shaft, in +0.0006 -0.0005 -0.0000 -0.0009