Chapter 6
Eq. (221):
Eq. (68):
Table 62:
Eq. (619):
Sut 3.4 H B 3.4(300) 1020 MPa
Se 0.5Sut 0.5(1020) 510 MPa
a 1.58, b 0.085
b
ka aSut 1.58(1020) 0.085 0.877
Eq. (620):
61
kb 1.24d 0.107 1.24(10) 0.107 0.969
Se ka kb Se (0.877)(0.969)(510) 433 MPa
Chapter 2
21
From Tables A20, A21, A22, and A24c,
(a) UNS G10200 HR: S ut = 380 (55) MPa (kpsi), S yt = 210 (30) Mpa (kpsi) Ans.
(b) SAE 1050 CD: S ut = 690 (100) MPa (kpsi), S yt = 580 (84) Mpa (kpsi) Ans.
(c) AISI 1141 Q&T at 540C (1000F): S ut = 8
Chapter 1
Problems 11 through 16 are for student research. No standard solutions are provided.
From Fig. 12, cost of grinding to 0.0005 in is 270%. Cost of turning to 0.003 in is
60%.
Relative cost of grinding vs. turning = 270/60 = 4.5 times
Ans.
_
1
Contents
Preface xi
2.6
2.7
2.8
2.9
2.10
Chapter 1
Introduction 3
1.1
1.2
1.3
1.4
1.5
1.6
1.7
1.8
1.9
1.10
1.11
1.12
1.13
1.14
Preliminary Remarks 3
The Concept of a Fluid 4
The Fluid as a Continuum 6
Dimensions and Units 7
Properties of the Velocity Fiel
StudyGuide for Fluid Mechanics Preface
The following materials are provided as a study guide for the text Fluid Mechanics by Frank White. A brief summary of the key concepts and theory is presented for each chapter along with the final form of basic equat
XI. Turbomachinery
This chapter considers the theory and performance characteristics of the mechanical devices associated with the fluid circulation. General Classification: Turbomachine  A device which adds or extracts energy from a fluid. Adds energy:
Ch. 10 OpenChannel Flow
Previous internal flow analyses have considered only closed conduits where the fluid typically fills the entire conduit and may be either a liquid or a gas. This chapter considers only partially filled channels of liquid flow refe
VII. Boundary Layer Flows The previous chapter considered only viscous internal flows. Viscous internal flows have the following major boundary layer characteristics: * An entrance region where the boundary layer grows and dP/dx constant, * A fully develo
IX. Compressible Flow
Compressible flow is the study of fluids flowing at speeds comparable to the local
speed of sound. This occurs when fluid speeds are about 30% or more of the local
acoustic velocity. Then, the fluid density no longer remains constant
Chapter 4
For a torsion bar, k T = T/ = Fl/, and so = Fl/k T . For a cantilever, k l = F/ , = F/k l . For
the assembly, k = F/y, or, y = F/k = l +
Thus
F Fl 2 F
y
k
kT kl
Solving for k
kk
1
k 2
2l T
Ans.
l
1 kl l kT
kT kl
_
41
For a torsion bar, k T =
Chapter 7
71
(a) DEGerber, Eq. (710):
A 4 K f M a 3 K fsTa 4 (2.2)(70) 3 (1.8)(45) 338.4 N m
2
2
2
2
B 4 K f M m 3 K fsTm 4 (2.2)(55) 3 (1.8)(35) 265.5 N m
2
2
2
6
8(2)(338.4) 2(265.5) 210 10
d
1 1
6
6
210 10 338.4 700 10
3
d = 25.85 (10 ) m = 25.8
Chapter 16
161 Given: r = 300/2 = 150 mm, a = R = 125 mm, b = 40 mm, f = 0.28, F = 2.2 kN, 1 = 0, 2 = 120, and a = 90. From which, sin a = sin90 = 1. Eq. (162):
Mf 0.28 pa (0.040)(0.150) 120 0 sin (0.150 0.125 cos ) d 1 2.993 10 4 pa N m
Eq. (163):
MN
Chapter 14
d
141
N
22
3.667 in
P
6
Table 142:
Y = 0.331
dn (3.667)(1200)
Eq. (1334): V
1152 ft/min
12
12
1200 1152
Eq. (144b): K v
1.96
1200
H
15
Eq. (1335) : W t 33 000
33 000
429.7 lbf
V
1152
K vW t P 1.96(429.7)(6)
7633 psi 7.63 kpsi Ans.
Chapter 15
151
Given: Uncrowned, throughhardened 300 Brinell core and case, Grade 1, N C =
109 rev of pinion at R = 0.999, N P = 20 teeth, N G = 60 teeth, Q v = 6, P d = 6
teeth/in, shaft angle = 90, n p = 900 rev/min, J P = 0.249 and J G = 0.216 (Fig.
Chapter 13
d P 17 / 8 2.125 in
N
1120
dG 2 d P
2.125 4.375 in
N3
544
131
NG PdG 8 4.375 35 teeth
Ans.
C 2.125 4.375 / 2 3.25 in
Ans.
_
nG 1600 15 / 60 400 rev/min
p m 3 mm Ans.
132
Ans.
C 3 15 60 2 112.5 mm Ans.
_
NG 16 4 64 teeth
133
Ans.
dG NG m 64
Chapter 12
121
Given: d max = 25 mm, b min = 25.03 mm, l/d = 1/2, W = 1.2 kN, = 55 mPas, and N =
1100 rev/min.
b d max 25.03 25
0.015 mm
cmin min
2
2
r 25/2 = 12.5 mm
r/c = 12.5/0.015 = 833.3
N = 1100/60 = 18.33 rev/s
P = W/ (ld) = 1200/ [12.5(25)] = 3.
Chapter 8
Note to the Instructor for Probs. 841 to 844. These problems, as well as many others in this
chapter are best implemented using a spreadsheet.
81
(a) Thread depth= 2.5 mm Ans.
Width = 2.5 mm Ans.
d m = 25  1.25  1.25 = 22.5 mm
d r = 25  5
Chapter 10
101
From Eqs. (104) and (105)
KW K B
4C 1 0.615 4C 2
4C 4
C
4C 3
Plot 100(K W K B )/ K W vs. C for 4 C 12 obtaining
We see the maximum and minimum occur at C = 4 and 12 respectively where
Maximum = 1.36 % Ans.,
and Minimum = 0.743 % Ans.
_
Chapter 11
111
For the deepgroove 02series ball bearing with R = 0.90, the design life x D , in multiples
of rating life, is
L
60D nD 60 25000 350
xD D
525 Ans.
LR
L10
106
The design radial load is
FD 1.2 2.5 3.0 kN
1/3
Eq. (116):
525
C10 3.0
1/1.4
Chapter 9
Figure for Probs.
91 to 94
91
Given, b = 50 mm, d = 50 mm, h = 5 mm, allow = 140 MPa.
F = 0.707 hl allow = 0.707(5)[2(50)](140)(103) = 49.5 kN Ans.
_
92
Given, b = 2 in, d = 2 in, h = 5/16 in, allow = 25 kpsi.
F = 0.707 hl allow = 0.707(5/16
VI. VISCOUS INTERNAL FLOW
To date, we have considered only problems where the viscous effects were either: a. known: i.e.  known FD or hf b. negligible: i.e.  inviscid flow This chapter presents methodologies for predicting viscous effects and viscous f
Ch. VIII Potential Flow and Computational Fluid Dynamics
Review of VelocityPotential Concepts This chapter presents examples of problems and their solution for which the assumption of potential flow is appropriate. For low speed flows where viscous effec
The Lehigh River, White Haven, Pennsylvania. Open channel flows are everywhere, often rough and turbulent, as in this photo. They are analyzed by the methods of the present chapter. (Courtesy of Dr. E. R. Degginger/ColorPic Inc.)
658
v
v


eText Main
Roosevelt Dam in Arizona. Hydrostatic pressure, due to the weight of a standing fluid, can cause enormous forces and moments on largescale structures such as a dam. Hydrostatic fluid analysis is the subject of the present chapter. (Courtesy of Dr. E.R. D
Steam pipe bridge in a geothermal power plant. Pipe flows are everywhere, often occurring in groups or networks. They are designed using the principles outlined in this chapter. (Courtesy of Dr. E. R. Degginger/ColorPic Inc.)
324
v
v


eText Main Menu
Table tennis ball suspended by an air jet. The control volume momentum principle, studied in this chapter, requires a force to change the direction of a flow. The jet flow deflects around the ball, and the force is the balls weight. (Courtesy of Paul Silv
Hurricane Elena in the Gulf of Mexico. Unlike most smallscale fluids engineering applications,
hurricanes are strongly affected by the Coriolis acceleration due to the rotation of the earth, which
causes them to swirl counterclockwise in the Northern Hem
Inviscid potential flow past an array of cylinders. The mathematics of potential theory, presented in this chapter, is both beautiful and manageable, but results may be unrealistic when
there are solid boundaries. See Figure 8.13b for the real (viscous) f
Wind tunnel test of an F18 fighter plane model. Testing of models is imperative in the design of complex, expensive fluidsengineering devices. Such tests use the principles of dimensional analysis and modeling from this chapter. (Courtesy of Mark E. Gib