M.E. 80 - DYNAMICS OF MACHINERY
SEPTEMIBER 1959
Instructor Office Phone Hours
TEXTS: Mechanisms and Dynamics of Machinery, Mabie and Ocvirk,
Wiley.
Machine Analysis and Design Problems, Alvord, Pearson,
Hall.
OBJECTIVES: (1) To Apply the Principles of Dynamics to Machine
Elements and Assemblies.
(2) To Study Some Typical Accepted Designs.
(3) To Further Develop Engineering Analytical
Ability.
SC HEDULE
Date Period Reading Assign. Topic Prob.
Chapt Ass
1 --- --- Introduction: Schematics #8a
2 3 40-47 Cams #7a4
3 33 48-55 Motion #8 bod
4 Lecture Differentiation By Finite Diff.#8e,f,g
5 10 209-223 Velocity - Cams and Linkages #14
6 10 223-227 Velocity - Rolling "17
7 --- --- Bluebook #1 Lect. 1-4
8 Lecture Related Scales and Acceleration #23
9 10 Ex. 1,2 Acceleration - Quadric Linkage
10 10 227-231 Acceleration - Coriolis #24
11 10 231-234 Acceleration - Sliders
12 Acceleration
13 Bluebook #2 Lect. 6-11

Page 2 - M. E. 80 Con't.
Date Period Reading Assign. Topic Prob.
Chapty pp Assign.
14 Lecture Static Force Analysis #33
15 Lecture Friction #41
16 11 267-276 Inertia Force Analysis 51
8 WEEKS! -
17 11 276-280 Inertia Force Analysis 53
18 11 280-284 Superposition
19 — a — Dynamic Superposition 59
THANKSGIVING
20 Bluebook #3 Lect. 12-18
21 Dynamic Force Analysis 59
22 11 284 --- Engine Dynamics
23 11 --- 298 Engine Dynamics
24 11 299-305 Flywheels #63
25 12 341-351 Balancing #68, 70...- -...-... CHRISTMAS ------.. —
27 Bluebook #4 Lect. 19-24
28 12 351-353 Balancing # 3
29 12 353-365 Balancing
30 --- Balancing

Date Period Sa ubject Read Problems
17 Dynamic Force Analysis Chapel 11
par. 7-8
- 18 Dynamic Force Analysis Chap'. 11
par. 9
19 Dynamic Force Analysis Chap. 11
par. 10412
20 Energy Storage Flywheels Chap. 13
par. 11
(See also p. 490, prob. 12-21)
21 Energy Storage Flywheels
22 Bluebook #3
23 Balancing Rotat ion Chap. 12
par. 1-7
24 Balancing - Reciprocation Chap, 12
par. 11-14
25 Engine Balance Chap. 12
par. L5$31
26 Engine Balance
27 Vibrations - Free Chap 14
par. 1.5
28 Vibration Analysis Forced Chap. 14
par. 6=
29 Bluebook #4
30 Vibration Analyses Self Excited
31 Vibration Analyses Critical Speeds

2Date Period ubject Problems
18 Dynamic Force Analysis Chap. 11
par. 10-15 48
19 Dynamic Force Analysis Chap. 11
pare 10-15 60
20 Flywheel Analysis Chap. 13
par. 11 63,67
(See also p. 490, prob. 12-21)
21 Balancing Rotating Masses Chap, 12
par. 1-7 69,70
22 Bluebook #3
23 Balancing Machines Chap. 12
par * 111 72
24 Reciprocating Balance Chap. 12
par. 15-31 73
25 Vibration Analysis Chapi, 14
par.. 1-5 75
26 Vibration Analysis Chap. 4
par. 6-8 76
27 Vibration Analysis 78
28 Vibration Analysis 79
29 Bluebook #4
30 Review
31 nin-a Examination

ME3 80i tcss of Macliner
Instructor Off ice Hours
Text: Mechanics of Machinery, Ham, Crane & Rogers, McGraw Hill.
Course Objectives:
1. To acquire facility in the application of dynamics to machinery.
2. To obtain knowledge of common practice in the construction of
machinery.
Schedule: (The reading assignments listed should be read before the
period indicated.
Date Period Subject Read Problems
1 Introduction and Motion Analysis Chap, 1 1,2
2 Motion Analysis Chap, 2
par. 136 3,4
3 Motion Analysis Chap. 3 7
4 Cam Analysis Chap. 3 8
5 Velocity Analysis Chap. 3
par. 1-14 11, 10
6 Velocity Analysis Chap. o8
par. 15-26 12,16
7 Velocity Analysis Chapo a
par. 23 17, 19
8 Bluebook #1
9 Acceleration Analysis Chap. 9
par. 1-8 23
10 Acceleration Analysis Chap. 9
par. 1..8 24
11 Acceleration Analysis 25
12 Acceleration Analysis Chap. 8
par,. 27
Chap. 9
par. 17 27
13 Static Forces Chap. 10
par. 1-4 33
14 Static Forces Chap. 10
par. 6-16 35
15 Bluebook #2 - Closed BoEok
16 Inertia Forces Chap. 11
par. 1-9 44,47
17 Inertia Forces Chap. 11
E}~ a 1 3 9 r50

ILV UQ a ics a- of Machinert
Instructor., Office Hours r
Text: Mechanics of Machinery, Ham, Crane & Rogers, McGraw Hill.
Course Objectives:
1. To acquire facility in the application of dynamics to machinery.
2. To obtain knowledge of conmmon practice in the construction of
machinery.
Schedule: (The reading assignments listed should be read before the
period indicated.)
Date Period _ Sub., ect Read Pr oblems
1 Introduction & Motion Analysis Chap. 3
2 Cams Chap. 3 A-1,2,3
3 Graphical Differentiation Lecture A-4
4 Diff. by Finite Differences Lecture A-5
Chap. 3
5 Velocity Analysis - Quadric Chap. 8 12
Linkages par. 1-14
6 Velocity Analysis - Cams Chap. 8 B
par. 10
7 Velocity Analysis - Rolling Chap. 8 21
par. 23
8 Bluebook #1
9 Acceleration Analysis - Chap. 9
Quadric Linkages par. 1 8
10 Acceleration Analysis - Lecture
Coriolis
11 Acceleration Analysis - Chap. 9
Sliders par. 11-14
12 Acceleration Analysis - Cams Chap. 9
par. 15
Chap. 9
par. 17
13 Inertia Forces Chap. 11
14 Inertia Forces Chap. 11
par.!-6
15 Bluebook #2
16 Static Forces & Friction Chap. 10

MACHINE ANALYSIS AND DESIGN PROBLEMS
H. H. ALVORD
J. R. PEARSON
K. W. HALL
DEPARTMENT OF MECHANICAL ENGINEERING
THE UNIVERSITY OF MICHIGAN
1958

CONTENTS
Page
DYNAMICS OF MACHINERY PROBLEMS
I MOTION ANALYSIS AND CAMS 2
II - VELOCITY ANALYSIS 5
III - ACCELERAT ION ANALYS IS 13
IV - STATIC FORCES 18
V - INERTIA FORCES 23
VI - DYNAMIC FORCE ANALYSIS 26
VII - FLYWHEELS 34
VIII - BALANCING 36
IX - VIBRATIONS 40
MACHINE DESIGN PROBLEMS
X - MATER IALS 44
XT - STRESS AND STRENGTH 45
X I I - FITS AND TOLERANCES 48
XIII I SPRINGS 49
XIV - THREADED FASTENERS 54
XV - POWER SCREWS 57
XVI - BELTS AND CHAINS 59
XV II - WIRE ROPES 61
XVIII - SPUR GEARS 63
XIX - HELICAL GEARS 67
XX - BEVEL GEARS 70
XXI - WORM GEARS 73
XX II - COUPLINGS AND CLUTCHES 75
XXIII - HYDRAULIC COUPLINGS AND TORQUE CONVERTERS 79
XXIV - BRAKES 81
XXV - SHAFTS 86
XXVI -.SLIDING BEARINGS 89
XXVII - ROLLING BEARINGS 92
XXVIII - MISCELLANEOUS 94

PREFACE
This problem book and the accompanying illustrations are intended for use in
courses in DYNAMICS OF MACHINERY and MACHINE DESIGN.
The presentation of these problems is believed to be unique in three respects:
(1) most of the problems refer to one or more machines shown by assembly drawings, (2) the Dynamics of Machinery problems emphasize the application of
dynamics to actual machines, and (3) the Machine Design problems emphasize
synthesis of machine elements as well as analysis of these elements. It is felt
that this presentation will help to make the student familiar with the construction and use of machinery and its elements, and will make the analysis of
accelerations, inertia, forces, vibrations, etc., more meaningful to the student,
and will teach the student how to combine his knowledge of mechanics, materials,
and manufacturing with his own judgement and common sense to design machinery.
Knowledge of the performance of common driving and driven machines, a better
understanding of machine drawings, and an improved ability to write brief, clear,
descriptions and explanations should also result from this presentation.
In addition to the problems in this book, each instructor will be able to make up
many other problems based on the illustrations, if he so desires. It is hoped
that such problems will use this- same presentation, and not revert to the formula
plugging and manipulation exercises so commonly found in machine design courses.
It is also felt that the descriptions asked for in the Machine Design problems
are very worthwhile,. but should be omitted when a particular machine has already
been described in a previously assigned problem.
The authors wish to express their thanks to the many industrial concerns whose
drawings and illustrations were used to provide the illustrations for these
problems.

DYNAMICS OF MACHINERY
GENERAL DIRECTIONS
All problems have been planned for 8- x 11 paper with the long edge vertical
except where otherwise indicated. Transparent paper will be convenient so
that space line diagrams can be traced directly from the drawings. Curves
should be drawn on standard decimal graph paper of the same size.
Figure, space and vector diagram scales are given in the following form:
Space scale is 2 inches per inch. This means 2 inches on the machine per
inch measured on the figure, or the machine is twice the size of the drawing. Velocity scale is 20 inches per second per inch. The velocity then
is the length of the vector multiplied by 20 inches per second. Accelerations and forces are treated similarly with appropriate units. Where scales
are to be determined by the student, they should be selected to give the
largest drawing, diagram, or curve possible for the space available.
In most problems it is necessary to determine machine dimensions as part of
the required data. It is intended that this be done by measurement of the
figure and multiplication by the scale.
Location of vector polygon poles and other points are given by x and y
coordinates with the lower left corner as the origin. The figure below is
a typical layout.
I i
\II I
B
_- rr 1 I- Fcw o I An,o. Rft J

DYNAMICS OF MACHINERY MOTION ANALYSIS AND CAMS
I - MOTION ANALYSIS AND CAMS
PROBLEM 1
a. A cam displacement easement curve has the following characteristics:
The acceleration, a, = 2 inches per second per second.
Time range-sec. Action Displacement Motion Equat ion
from t=O to t=l advance 1 inch parabolic s = t2
from t=l to t=2 advance 1 inch parabolic s = -2+4t-t2
from t=2 to t=3 dwell - - s = 2
from t=3 to t=6 return symmetrical about t=3
1. Plot the displacement-time curve.
2. Derive the velocity-time curve analytically and plot.
3. Derive the acceleration-time curve analytically and plot.
4. Check a few significant points by graphical differentiation.
Note: lay the curves out on graph paper in the manner shown below.
Draw the cruves as large as the graph paper will permit.
inches
v "
in/s c.
a 2
in/sec.
t-sec.
PROBLEM 2
a. A cam displacement easement curve has the following characteristics:
Time range-sec. Action Displacement Motion Equation
from t=O to t=2 advance 2 inches S H M s=l-cosxt
from t=2 to t=3 dwell none none s=2
from t=3 to t=6 return - symmetrical about t=3
1. Plot the displacement-time curve.

DYUAMICS OF MACHINERY MOTION ANALYSIS AND CAMS
2. Derive the velocity-time curve analytically and plot
3. Derive the acceleration-time curve analytically and plot
4. Check a few points by graphical differentiation
Note: Lay the curves out as indicated in problem 1.
PROBLEM 3
a. A cam displacement easement curve has the following characteristics:
Time range-sec. Action Displacement Motion Equation
from t=O to t=2 advance 2 inches cycloidal s=t-l sinl tt
from t=2 to t=3 dwell none none s=2
from t=3 to t=6 return - symmetrical about t=3
1. Plot the displacement-time curve
2. Derive and plot the velocity-time and acceleration-time curves in
the manner indicated in problem 1.
3. Check the velocity and acceleration by graphical differentiation at
t=O, t=0.5; t=2.00; and t=2.25.
PROBLEM 4
a,. Compare the curves of problems 1, 2, and 3
1. Assuming the weight of the follower to be 1.5 lbs., which of these
motions will result in the largest dynamic force on the follower
and what is its value?
2. Which-of these three motions will give the greatest pulse values?
Explain.
PROBLEM 5
a. Lay out the cam profile to give the motion described in problem 1 to
a roller follower. Base circle for the roller center of the cam has a
4 inch radius with center Ob (4,5.5). The path is vertical and radial.
Follower roller has a 0.5 inch radius. S5 = 2 inches/inch.

DYNAMICS OF MACHINERY MOTION ANALYSIS AND CAMS
PROBLEM 6
a. Lay out the cam profile to give the motion described in problem 2 to a
roller follower. Base circle for the roller center of the cam has a 4"
radius with center Ob (4,5.5). The path is vertical and offset by
1.5 inches from the vertical radius of the base circle. Follower
roller radius is 0.5 inches. S~ = 2 inches /inch.
PROBLEM 7, FIGURE 1, DIESEL ENGINE
a. The required motion for the diesel engine injector cam roller center
is as follows:
Cam rotation, degrees 0 5 10 15 20
Roller lift, inches 0.0000 0.0038 0.0150 0.0338 0.0599
25 30 35 40 45 50 55 60
0.0924 0.1254 0.1584 0.1854 0.2028 0.2178 0.2328 0.2478
65 70 75 79 80 86 90 96
0.2627 0.2742 0.2807 0.2823 0.2833 0.2774 0.2702 0.2534
100 106 110 116 120 126 130 136
0.2382 0.2094 0.1867 0.1525 0.1297 0.0955 0.0729 0.0441
140 146 150 156 158
0.0288 0.0121 0.0049 0.0001 0.0000
1. Trace the flow of force from cam to injector piston.
2. Plot the displacement-time curve for one revolution of the cam.
See the figure of problem 1 for the layout of the curve.
3. Draw the velocity-time and acceleration-time curves by graphical
different iat ion.
4. Design the cam profile to produce this motion. Locate the center
of the base circle, Ob, at 4,6. SS = 0.2 inches/inch. Note that
the drawing will be 5 times larger than the machine piece.
5. Determine the maximum inertia force of the follower slide cylinder
and roller assembly.

DYNAMICS OF MACHINERY MOTION ANALYSIS AND CAMS
PROBLEM 8, FIGURE 24, INDEXING MECHANISM
The figure scale is 1 inch per inch. The automatic screw machine tool
turret table rack is driven by the gear sector. The sector is an integral
part of the cam follower rocker which is driven by the cam. The camshaft
rotates at 2 rpm. The length of the rack is 1.300 inches. The total
weight of the moving parts on the table is 15 lbs.
Required:
a. Construct a skeleton linkage diagram of the cam, gear sector rocker,
and rack for the position shown at full scale. Locate the camshaft
center at 6:3, paper horizontal.
b. Lay out the path of the follower roller center showing successive
positions for every 30 degrees of cam rotation and for any other
critical intermediary positions.
c. Lay out the path of the rack showing positions corresponding to
those of "b". Use the right end of the rack as a point of reference.
d. Draw a displacement-time curve for the rack.
e. Graphically differentiate the displacement-time curve and draw the
velocity-time curve.
f. Graphically differentiate the velcoity-time curve for the acceleration-time curve and draw it.
g. Determine approximately the value of the maximum inertia force of
the table assembly.
II - VELOCrITY ANALYSIS
PROBLEM 9, PIGUREB 1, DIESEL ENGINE
Engine rpm is 2200. Ss = 2.5 inch/inch. Determine the relative (sliding)
velocity between the connecting rod bushing and the crank pin.

DYNAMICS OF MACH INERY VELOCITY ANALYS IS
PROBLEM 10, FIGURE 1, DIESEL ENGINE
Engine rpm equals 1800. Ss equals 2.5 inch/inch.
Locate the space diagram with crank center at 2,4. Locate the velocity
vector polygon poles at 5,10 for (a), 5,7 for (b), 5,2 for (c).
Required:
a. Determine the velocity of the piston for a crank position of 45 degrees
from top dead center. The crank pin velocity vector length is 2".
b. Same for crank angle of 120 degrees.
c. Same for crank angle of 270 degrees.
PROBLEM 11, FIGURE 1, DIESEL ENGINE
Engine rpm equals 2000. Engine blower drive-camshaft speed ratio is 2:1.
The velocity vector for the blower blade tip is 2" in length. For the space
diagram, locate the upper impeller center at 2,8.5 for (a) and 6,8.5 for
(b).
Required:
a. Determine the relative velocity of the blades at the tip for the
position shown. Clockwise rotation.
b. Determine the relative velocity for the position in which the tip is
just leaving contact.
PROBLEM 12, FIGURE 2, TRANSPORT
n =- 5.00 inch/inch. The transport is used to transfer ingots from one
operation to another. It is driven by a 2 HP, 900 rpm motor. The drive
is through a bevel gear reducer of 5.28:1 speed ratio; 2 chain drives of
1:1 and 3:1 speed ratio; and a pair of gears of 1.5:1 ratio.
Required:
a. Trace the flow of power from motor to finger link.
b. Draw the linkage skeleton space diagram for the position shown at a
size 2 times that of the figure. Set the paper horizontal and locate
the drive crank center at 8.5.

DYNAMICS OF MACHINERY VELOCITY ANALYS IS
c. Draw the path of the finger link-coupler pin joint showing positions
for every 30 degrees of crank rotation starting at extended dead end
for the four bar linkage.
d. Determine the velocity of the ingots for 30 degree intervals of
crank angle. Velocity vector length for the driver crank-coupler
pin is 1.5 inches. Locate the velocity vector polygon poles along
a line 6.5 inches up from the bottom, starting at 1,6.5.
e. Plot distance vs. time and velocity vs. time on graph paper. Use
a common abscissa and check points of maximum velocity by graphical
differentiation. Start at extended dead center.
PROBLEM 13, FIGURE 24, SCREW MACHINE GENEVA INDEXING MECHANISM
Figure scale, S,is 0.733 inches/inch. In put shaft rotates at 240 rpm.
Speed ratio of input to crankshaft is 1:1. Drive disk pin circle diameter
is 1.100 inches.
Required:
a. Trace the power flow for actuation of the Geneva Motion.
b. Explain the function and the operation of the shot pin.
c. Determine the angular velocity of the turret shaft 15 degrees
after pin engagement.
d. Same for 21.5 degrees after engagement. Locate the center of the
drive pin disc at 3,7 for the space diagram. Scale of space diagram is 2 inches per inch. Locate velocity vector polygon pole
at 3,5. Pin velocity vector length is 2 inches.
e. What is the maximum angular velocity of the turret?
f. What is the maximum relative velocity between pin and slot surface?

DYNAMICS OF MACHINERY VELOCITY- ANALYSIS
PROBLEM 14, FIGURE 25, SHAPER
Figure scale is 5.00 inches per inch. The ram of the shaper is driven by
a quick return linkage designed to reduce the non-cutting time of the
machine to a minimum. The linkage is driven by the motor through a V-belt
and gear train. The motor is a 5 HP, 1725 rpm squirrel cage induction
type driving through the V-belt drive with a 1.5 speed ratio and drives a
40 tooth pinion on the output shaft. The pinion meshes with a 73 tooth
gear. A second speed reduction is effected through a 56 tooth-96 tooth
pair and the final reduction is from a 48 tooth pinion to the 171 tooth
-bull gear.
Requir ed:
a. Determine the speed of the bull gear-driveR crank.
b. Draw the space diagram of the quick return- linkage- in the dead end
posit-ion at the beginning of the cutting stroke. The space diagram
scale is 5.00 inches per inch. Locate the bull gear crank center
at 8.5,4.25. Paper horizontal.
c. Determine the ram velocity for 12 positions including the two dead
end positions and the two positions for which the' follower crank
is vertical. Locate the velocity vector polygon poles along horizontal lines 4 inches and 3 inches up. The driver-crank pin
velocity vector length is 1.5 inches.
d, Plot a slider position vs. velocity curve using the values of part
b.
e,. Determine the approximate maximum cutting speed.
f. Determine the ratio of cutting to idling (return) time.

DYNAMICS OF'MACHINERY VELOC ITY ANALYS IS
PROBIEM 15, FIGURE 1, DIESEL ENGINE
Engine rpm is 1800. Figure scale- is:2.5 inches per inch.
Draw space diagrams twice natural size of the Diesel injector cam and
follower roller at cam angles of 30 degrees, 60 degrees, and 90 degrees from
the position shown. Locate base circle centers at 2.5,3; 2.5,8; and 6,5.5.
Required:
a. Determine the velocity of the follower roller center forj each of
the three Positions with velocity vector polygons. Locate polygon
poles at the cam base circle centers. The velocity vector for a
point on the base circle is 2 inches in length.
PROBLEM 16, FIGURE 1, DIESEL ENGINE
Engine rpm is 2400. Scale of figure is 2.5 inches per inch.
Required:
a, Draw a space diagram of the injector drive linkage from cam to
injector piston with the cam at 45 degrees from the position shown.
Lay the paoer horizontally right over the draw~ing and locate the
cam base circle center at 2,2.5.
b. Draw the velocity vector polygon for the linkage with the pole
located at -8,4. The- velocity vector length for a point on the base
circle is 2 inches.
c. Determine the velocity of the injector piston.
d. Determine- the relative velocity of rocker arm to piston.
e. Determine the rotational velocity,3, of the rocker arm.
PROBLEM 17, FIGURE Q, SCRAPER HOIST
The drive motor of the scraper hoist runs at 1725 rpm. The power flows
through the reverted gear train which has a 26 tooth drive pinion, a

DYNAMICS OF MACHINEY VELOCITY ANALYSIS
countershaft with a 70 tooth gear and a 32 tooth pinion coupled, and a
64 tooth output gear. Power then flows into the planetary gear trains.
In the left planetary the sun gear has a pitch diameter of 2.500 inches.
The planets have pitch diameters of 3.500 inches.
Required:
a. Determine the pitch diameter of the annular ring gear.
b. Make a space diagram of the planetary train showing both front and
side views Space scale is 2.5 inches/inch. Set the paper horizontal and locate the center of the sun pitch circle at 4,4.
c. Indicate the flow of power in the side view.
d. Determine by graphical velocity vector analysis the velocity of the
planet-carrier bearing center when the brake is applied to the ring
gear. The sun gear-planet pitch point velocity vector is 2 inches
in length.
e. Determine the output rpm.
f. Derive a general expression for the speed ratio of the train,
rpm input/ rpm output in terms of the numbers of teeth on the gears.
g. Write a general equation for the number of teeth on the ring gear
in terms of the numbers of teeth on sun and planets.
PROBLEM 18, FIGURE 28, STRAIGHT PRESS
Figure scale is 8 inches/inch. Power flow is from 1140 revolutions per
minute motor through the V-belt drive and pinion and gear to the crankshaft.
Crank rotates counterclockwise.
Required:
a. Locate the crank center at 6,8 and draw the space diagram at 2
inches per inch for the position shown.
10

DYNAMICS OF MACHINERY VELOCITY ANALYSIS
b. Draw the velocity vector polygon with the pole at 4,9.5 and the
velocity vector for the crankpin 4.00 inches in length. Determine
the velocity of the crosshead.
c. Determine the velocity of the crosshead analytically.
d. Determine the maximum velocity of the crosshead and the crank angle
at which it occurs.
PROBLEM 19, FIGURE 29, WORM GEAR SPEED REDUCER
Figure scale is 2 inches per inch. Single worm drives a 47 tooth gear.
The lead angle on the worm equals the helix angle of the gear and is 20
degrees. Input worm rotates at 760 revolutions per minute clockwise from
input end.
Require d:
a. Determine the pitch line velocity of the gear.
b. Determine the direction of rotation of the output gear.
c. Draw the velocity vector polygon for the pitch point with the worm
pitch point velocity vector 8 inches long. Locate the pole at
4,1.5.
PROBLEM 20, FIGURE 30, OVERHEAD CRANE
Figure scale is 4.00 inches per inch. Cable drum rotates at 12 rpm.
Required:
a. Determine the velocity of the hook.
b. Determine the hook sheave angular velocities.
PROBLEM 21, FIGURE 12, BEVEL GEAR SPEED REDUCER
Figure scale is 2 inches per inch.A Input pinion has 23 teeth. Output gear
has 94 teeth. Diametral pitch is 8 teeth per inch of diameter at the
11

DYNAMICS OF MACHINERY VELOCITY ANALYSIS
maximum pitch diameter.
Required:,W Determine the mean pitch line velocity.
L Determine the velocity of the point of contact between the inner
race and the tapered roller of the bearing. oV 0- 4+
Determine the rpm of roller axis. & "V %
PROBLEM 22, FIGURE 14, AUTOMATIC TRANSMISSION
Diameter of the forward sun gear, Dfs, is 1.800 inches; of the rear sun
gear,Drs, is 1.550 inches; of the planets, Dp, is 0.950 inches; of the
ring gear, Dr, is 3.700 inches. The numbers of teeth are T = 36; Tr
31; Tp = 19; Tr = 74. Flywheel speed is 2700 rpm. The following
chart indicates the combination of clutches and brakes engaged for the
various speeds.
Clutches Brakes Power Output
"Speed" Forward Rear Forward Rear Flow Speed Speed Ratio
First X X
Second X X
High X X
Reverse X X
Required:
a. Trace the power flow for each case.
b. Determine by velocity vector analysis the pitch line velocity of
the ring gear.
c. Determine the ring gear output speed in rpm for each case.
12

DYNAMICS OF MACHINERY VELOCITY ANALYS IS
d. Determine the speed ratio, rpmin/rpmout for each case. Use crosssection A-A for the space diagram for (b) with paper center over
sun center and paper horizontal. Use the rear sun planet pitch
points for polygon poles. Forward sun pitch point velocity vector
length is 1.5 inches.
III - ACCELERATION ANALYSIS
PROBLEM 23, FIGURE 2, TRANSPORT
Figure scale is 5.00 inches / inch. See problem 12. The transport quadric
linkage is driven by a 900 rpm motor through a bevel gear speed reducer of
5.28/1 ratio, 2 chain drives of 1:1 and 3:1 ratios and finally through a
pair of gears of 1.5:1 ratio.
Requir ed:
a. Draw the quadric linkage space diagram for the position shown at a
scale of 2.5 inches / inch. Set the paper horizontally and locate
the drive crank center at 8.5,2.
b. Determine the velocity scale. Velocity vector length for the
driver crank-coupler pin is 1.500 inches.
c. Determine the acceleration scale by the related scales method.
d. Draw the acceleration vector polygon for the linkage in the position
shown using the related scales method. Locate the velocity vector
polygon pole at the drive crank-coupler pin and the acceleration
pole, q, at the follower crank-coupler pin.
e. Determine the acceleration of the coupler-follower crank pi..
f. Determine the acceleration of the coupler-finger link pin.
g. Determine the acceleration of the ingots for 30 degree intervals
13

DYNAMICS OF MACHINERY ACCELERATION ANALYS IS
of the driver crank and plot on graph paper. Start at extended
dead center. Locate poles on a horizontal line 6.5 inches up from
the bottom.
PROBLEM 24, FIGURE 25, SHAPER
Figure scale is 5.00 inches per inch. The drive of the shaper is described
in problem 14.
Required:
a. Determine the ram acceleration for 12 positions including the 2
for which the follower crank is vertical (position shown) and the
2 dead center positions. Use the related scales method with a
drive crank pin velocity vector length of 1.5 inches. Space diagram
scale is 5.00 inches per inch. Locate the bull gear crank center
at 8.5, 4.25. Locate poles on horizontal lines 1.5, 3.5, 5.5, and
7.5 inches up from the bottom. Paper is horizontal.
b. Plot a slider position-acceleration curve on graph paper.
PROBLEM 25, FIGURE 1, DIESEL ENGINE
Figure scale is 2.500 inches per inch. Assume an engine speed of 2400 rpm.
a. Lay out the piston-crankshaft linkage space diagram at the same
scale as the figure with the crankshaft center located at 4.25,
4.5. Use the position shown in the end view.
b. Determine the displacements of the piston for 30 degree intervals
of the crank angle.
c. Lay out coordinates on graph paper for the s-t, v-t, and a-t curves
in the fashion recommended in problem 1. Plot the displacements of
part (b) thereon.
d. Determine the velocity and acceleration of the piston for the 12
positions by Klein's Method and plot.
14

DYNAMICS OF MACHINERY ACCELERATION ANALYSIS
e. Superimpose the simple harmonic motion acceleration curve on the
piston acceleration curve and study the deviation. (Note: the
corresponding simple harmonic motion curve is s = R (l-cosst)
where R equals the crank throw and equals the crankshaft speed in
radians per second.).
f. Where does the maximum velocity occur? Where does the maximum
acceleration occur? Are dead end accelerations the same?
What would be the magnitude of the maximum inertial force at the
wrist pin if the piston weighs 4;00 lbs.?
PROBLEM 26, FIGURE 1, DIESEL ENGINE INJECTOR CAM
Figure scale is 2.5 inches per inch. Positions of cam and follower roller
are indicated in problem 7.
a. Draw the cam profile and follower in the position for which cam
angle is 30 degrees at a scale of 0.200 inches per inch. Locate
the camshaft center at 3.5, 2.5.
b. Draw the velocity vector polygon and determine therefrom the
velocity of the follower center. Engine speed is 2400 rpm. Locate
pole at 3,5.5 and take the velocity vector length of a point on
the base circle at 1.500 inches.
c. Draw the acceleration vector polygon and determine the acceleration
of the follower. Locate the pole at 6,10. Use the related scales
method.
d. Compare the result with the curve of problem 7.
PROBLEM 27, FIGURE 11, V-8 ENGINE
Figure scale is 2 inches per inch.
a. Determine the value and crank angle location for the maximum
velocity and acceleration analytically.
15

DYNAMICS OF MACHINERY ACCELERATION ANALYSIS
b. Compute the displacement, velocity, and acceleration of the piston
for 60 degree intervals of the crank angle and plot on graph paper
in the manner described in problem 1.
c. Superimpose the simple harmonic motion acceleration curve for the
same crank throw and compare.
PROBLEM 28, FIGURE 11, V-8 ENGINE CAM AND FOLLOWER
Figure scale is 2 inches per inch. Engine speed is 3600 rpm.
a. Draw a space diagram at a scale of 0.5 inches per inch of the
exhaust cam and follower of the right bank cylinder. Set the
angular position of the cam to correspond with a crank angle of
210 degrees after extended dead center. Locate the cam center at
2,6.
*b. Determine the velocity of the follower. Locate velocity vector
polygon pole at 3,2. Velocity vector length of a point on the base
circle is 1.5 inches.
c. Determine the acceleration of the follower. Relate the scales and
locate the pole at 7,4.
PROBLEM 29, FIGURE 11, V-8 ENGINE VALVE LINKAGE
Figure scale is 2 inches per inch. Engine speed is 2400 rpm.
a.: Draw the space diagram of the right bank cylinder exhaust valve cam
and linkage at the figure scale. Locate the cam center at 1.5,6 and
the crankshaft center vertically below it. Rotate the cam 150
degrees from the position shown.
b. Draw the velocity vector polygon with pole at 6,5 and the pitch line
velocity vector length equal to 1.0- inches.
c. Draw the acceleration vector polygonm with pole at 4,4. Relate the
scales.
16

DYNAMICS OF MACHINERY ACCELERATION ANALYSIS
PROBLEM 30, FIGURE 11, V-8 ENGINE VALVE LINKAGE SPRING
Figure scale is 2 inches per inch. Engine speed is 2400 rpm.
a. Assume that the exhaust valve opens with uniformly accelerated and
decelerated motion. Determine the acceleration of an element of
mass on the helical spring at the third coil down from the top.
b. Explain the meaning of surge in helical springs.
PROBLEM 31, FIGURE 20, CRUSHER
Figure scale is 10 inches per inch. Flywheel speed is 60 rpm. The toggle
joints are designed for pure rolling to reduce' friction and simplify lubrication.
a. The contour on the connecting rod block at the toggle joint is
circular with radius of 1 inch. Develop the contour for the
coupler block at full size.
b. Draw the -space diagram at a scale of 10 inches per inch with the
drive shaft center at 9,6. Paper horizontal. Set the crankshaft
at 135 degrees from the position shown.
c. Draw the velocity vector polygon with the pole at 8,1 and the
velocity vector length of the eccentric center equal to 2.00 inches.
d. Draw the acceleration vector diagram with pole at 1.5,7. Relate
the scales.
e. Determine the velocity and acceleration of the extreme end of the
crusher jaw plate.
PROBLEM 32, FIGURE 24, GENEVA INDEX-ING MECHANISM
Figure scale is 0.733 inches per inch. Geneva drive shaft rotates at 240
rpm.
17

DYNAMICS OF MACHINERY ACCELERATION ANALYSIS
a. Draw the space diagram of the Geneva driver and driven disks 45
degrees after engagement at a scale of 0.25 inches per inch. Locate
the drive disk center at with paper horizontal.
b. Draw the velocity vector diagram with pole at JQ6 The velocity
scale is aW~ —inches- per second per inch.
c. Draw the acceleration vector polygon for the Geneva disks with pole
at Hi.. Relate the scales.
d. Determine the angular acceleration of the turret shaft.
IV - STATIC FORCES
PROBLEM- 33, FIGURE 2, TRANSPORT
The transport moves 4 x 4 x 30 inch steel ingots from one operation to the
next. The ingot rail coefficient of friction is 0.90. The overall speed
ratio is 25;:1 and the motor speed is 900 rpm.
a. Set up each member of the linkage as a free body diagram.
b. Draw the force vector polygon for the position shown at a scale of
75 lbs. per inch. Locate the pole at 3,7. Neglect joint friction.
c. Determine the force on the follower crank pin.
d. Determine the motor torque.
PROBLEM 34, FIGURE 20, CRUSHER
Figure scale is 10 inches per inch. The rock crusher delivers a force of
20 tons 15 inches up from the bottom edge of the swinging jaw. Output'
speed is 60 cycles per minute.
a. Trace the flow of power from input shaft to output jaw.
b. Draw a space diagram of the linkage at the figure scale with the
18

DYNAMICS OF MACHINERY STATIC FORCES
eccentric center at 3,8.
c. Following the path of force set up each link as a-free body diagram
d. Draw the force polygon at a scale of 10,000 lbs. per inch with
origin of the load vector at 1.5,4. Neglect- frictionaleforces.
e. Determine the torque on the eccentric shaft.
PROBLEMI 35, FIGURE 15,..THIRUSTOR BRAKE
Figure scale is 2.5 inches per inch. The torque on the brake drum is 1200
lb. ft.
a. Draw a free body diagram of each link.
b.,Draw the static force polygon at a scale of 400 lbs. per inch with
the origin of the brake shoe pivot: bolt force vector at 4,5.5.
c. Determine the spring force necessary for engagement.
d. Determine the thrustor solenoid force necessary for disengagement.
PROBLEM 36, FIGURE 24, INDEXING MECHANISM TURRET TABLE DRIVE
Figure scale is 0.75'inches per inch. Rack and gear sector have teeth of
20 degree pressure angle. Load at the turret is 1.5 lbs.
a. Trace the flow of force from- the turret to the cam shaft.
b. Draw a space diagram of the turret table, gear sector cam follower,
cam, and shaft at the figure scale with.-the cam-shaft center at
5,2. Paper horizontal. Set cam at 30 degrees counterclockwise
from position shown.
c. Draw each member as a free body diagram.
d. Set up the force polygon with the origin of the load vector at
10.5, 2.5 at a scale of 0.5 lbs. per inch. Neglect friction.
19

DYNAMICS OF MACHINERY STATIC FORCES
e. Determine the torque of the cam shaft.
PROBLEM 37, FIGURE 3, POWER STEERING UNIT
Figure scale is full. Hydraulic pressure in the actuator is 100 lbs. per
square inch. Pressure angle of the rack and sector teeth is 20 degrees.
a. Set each member up as a free body diagram.
b. Draw the force vector polygon at a scale of 100 lbs. per inch;
actuator piston force vector origin at 7,8. The piston is moving
to the left.
c. Determine the torque on the gear sector shaft.
d. Determine the torque at the steering wheel.
PROBLEM 38, FIGURE 14, AUTOMATIC TRANSMISSION SECTION A-A
Figure scale is 1 inch per inch. The pressure in the hydraulic actuator is
40 psi.
a. Draw the force polygon at a scale of 75 lbs. per inch-with the
origin of the actuator piston force vector at 4,4.
b. Determine the force applied by the rocker to the brank band.
c. Determine the force on the rocker pivot pin.
PROBLEM 39, FIGURE 28, STRAIGHT PRESS
Pigure scale is- 5 inches per inch. C apacity of- the press is 80 tons.
a. Draw a space diagram of the ram,coupler,and crank at a crank angle
of 40 degrees from bottom dead center at a scale of 2.5 inches per
inch. Locate the crank center at 1.5,9.
b. Set up each member as a free body diagram.
c. Neglecting friction, draw the force polygon at a scale of 20 tons
20

DYNAMICS OFP- CHINBRY STATIC PAFCES
per inch. Locate the origin of the load vector at 3.5, 4.5.
d. Determine the torque on the crankshaft.
e. Draw a force polygon including friction with the force vector origin
at 3.5, 6.5. Assume the coefficient of friction to be 0.25 at all
points. (This value is exaggerated),
f. Determine the input torque.
g. What is- the efficiency of this part of the drive for such a coefficient of frict ion?
PROBLEM 40, FIGURE 2,'TRANSPORT
Figure scale is 5 inches per inch. Ingots are 27.5 inches long. The
coefficient of friction for ingot to rail is 1.00 and for all bearings is
0.15. Overall speed ratio of the power train is 25/1 and motor speed is
900.
a. Draw a space diagram at a -scale of 2.5 inches per inch with the
paper horizontal and the follower crank center at 0.5, 7.5 for the
position shown.
b4 Set up each member as a free body diagram.
c. Draw a force vector polygon at a scale of 75 lbs. per inch with the
load vector origin at 5,-1, friction omitted.
d, Draw a force vector polygon with friction considered, load vector
origin at 10,1.
e. Determine the efficiency for the crank angle position shown and for
the assumed coefficients of friction.
f. Approximately how will the efficiency vary with respect to input
crank angle?
21 i

DYNAMICS OF MACHINERY STATIC- FORCES
g. About where will the minimum efficiency occur?
PROBLEM 41, FIGURE 11, V-8 ENGINE CRANKROD,AND PISTON LINKAGE
Figure scale is 2 inches per inch. Main bearing is 2.500 inches in diameter.
Coefficient of friction for all bearing surfaces is 0.25. (This is an
exaggerated value).
a. Set up each member as a free body- diagram.
b. Draw a.force vector polygon. Assume the pressure in the cylinder.
is 100 lbs. per square inch in the left bank cylinder. Force scale
is 200 lbs. per inch. Locate the origin of the load vector at
2,8.
c. Determine the torque on the crank shaft.
d. What would the torque be if the friction were neglected?
PROBLEM 42, FIGURE 24, INDEXING MECHANISM TURRET TABLE DRIVE
Figure scale is 0.75 inches per inch. Rack and gear sector have teeth
of 20 degree pressure angle. Load at the turret is 20 lbs.
a. Draw a space diagram of the turret table and drive with the cam
rotated counterclockwise 135 degrees at the figure scale. Locate
the cam shaft center at 5,2. ~with the paper!horizontal.
b. Draw each member as a free body diagram.
c. Assuming the coefficient of friction to be 0.2 at all bearing
surfaces, draw a force polygon at a scale of 5 lbs. per inch.
Locate the origin of the'load vector at 10.5, 2:5.
d-. Determine the roller cam load, the camshaft load, and the camshaft
torque.
22

DYNAMICS OFP MACHINERY STATIC FCRCES
PROBLEM 43, FIGURE 25, SHAPER
Figure scale is 5 inches per inch. Cutting load is 300 lbs. Assume the
coefficient Of friction for flat sliding joints to be 0.25 and for pin
joints to be. 0.50 These are exaggerated values. Force scale Sf is
150 lbs. per inch.
a. Draw a space diagram of the drive linkage at a scale of 5 inches
per inch with the crank angle at 135 degrees from position shown.
Locate the bull gear center at 4,4.5.
b. Draw free body diagrams of all links.
c. Draw a force polygon including friction forces. Locate the origin
of the load vector at 9,3.
d. Determine the torque inputs at thee bull gear shaft.
V - INERTIA FORCES
PROBLEM 44, FIGURE 22, TRUCK CHASSIS
Figure scale is 15 inches per inch. The truck when loaded weighs 3 tons.
The center of gravity of the whole unit is located 60 inches to the rear
of the front axle and 30 inches above the ground level.
a. What is the ground load on the front left wheel with the vehicle
standing?
b. What is the ground load on the left front wheel if the truck is
accelerated from rest to 20 miles per hour in 4 s'econds?
c. What is the ground load if the brakes are applied and the truck
decelerated from 20 miles per hour to rest in 4 seconds-?
d. Which way will the springs deflect in each case?
23

DYNAMICS OF MACHINERY -INERTIA InPr..q
PROBLEM 45, FIGURE 20, CRUSHER
Figure scale i-s 10 inches Der inch. The center of gravity~ of the swinging
iawr is at- 9, inches to the right?of the jaw face and 25 inches from the
pivot.- center on a line parallel to the jaw face The- velocity of the jaw
coupler joint is 15 inches ner second and the acceleration of the jaw is
0.20 radians per second per second. -The weight of the jaw is 1000 lbs.
a. Draw a space diagram of the jaw showing the center of gravity
of the jaw-coupler joint, and the pivot center.
b. Determine the inertia force on the jaw and show its value, direction and location on the diagram.
PROBLEM 46, FIGURE 24, INDEXING MECHANISM
Figure scale is 1.00 inches per inch. The center of gravity of the rockerfollower is 0.75 inches from the pivot pin center at 45 degrees up from the
horizontal in the position shown. Cam turns at 10 rpm'
a.- Draw a space diagram of the cam and follower -at 120 degrees of cam
angle from the position shown, at full scale. Locate the cam center
at 2,3.
b. Determine the acceleration of the roller center with an acceleration
polygon. Locate the Dole for velocity at 6.5,7 and for acceleration
at 6.5,4. Make the velocity vector for a point on the base circle
ot the cam I inch and use related scales.
c. Determine the acceleration of the center of gravity.
d. Determine the inertia force and locate it Droperly by vector on
the space diagram. (The moment of inertia is 0.0013 lb-in-sec. 2).
e. Determine the distance from -ivot center to center of percussion
on the space- diagram.
f. Determine the radius of gyration. about the center of gravity.
24

DYNAMICS OF MACHINERY INERTIA FORCES
PROBLEM 47, FIGURE 5, BEVEL GEAR REVERSING UNIT
Figure scale:is 1 inch per inch. An AC induction motor rated at 10 HP
and 1160 rpm drives'a pulley through the reversing unit. The motor
characteristics are those of design B on the performance curves of Figure
31. The moment of inertia of the motor armature is 1/10th that for pulley
plus rever sing gear elements. The motor comes up to speed in 4 seconds.:a. Assuming a constant acceleration determine the approximate moment
of inertia of reversing gear plus pulley and of the motor armature.
b. Is the assumption o'f constant acceleration reasonable? Explain.
PROBLEM 48, FIGURE 11, V-8 ENGINE
Figure scale is 2 inches per inch. Engine speed is 2700 rpm. Piston
weight is 2: lbs. and connecting rod weight is 1.5 lbs. The radius of
gyration of: the rod is -4 inches and its center of gravity is 2 inches
from the crank pin centeri.
a Draw. a space diagram at 2 inches per inch with the crankshaft
center located at 3. 5, 4.5.
b. Determine- the accelerations of both wrist pins and the gravity
centers for both rods. Make the crankpin velocity vector 1.75
inches long. Locate velocity polygon poles at the wrist pins-and
acceleration polygon poles at the crankshaft center.
c. Determine the connecting rod inertia forces and draw them in as
vec-tors properly loca-ted and oriented.
d. Determine the piston -inertia forces and show them as vectors on
the space diagram.
e. Give the magnitude and location of the inertia force for the'
cr ank: i coskerw ev2t ae
25~

DYNAMICS OF MACHINERY INERTIA FORCES
PROBLEM 49, FIGURE 1, DIESEL ENGINE
Figure scale is 2.5 inches per inch. Engine speed is 1800 rpm. Piston
weight is 2.5 lbs. and connecting rod weight is 2.0 lbs. The center of:gravity of the rod is at 7.5 inches below the wrist pin center. The rod
is suspended from the wrist pin center and swung as a pendulum to determine
its full cycle period of one second.
a. Draw space diagrams of the linkage for the position shown; with
crank perpendicular to connecting rod; at 135 degrees from top
dead center;: and at 180 degrees from top dead center. Locate the
crankshaft centers- 2.5 inches up and at 1,3,5, and 7 from left edge.
b. Determine the acceleration of the piston and center of gravity- for
each case. It is suggested that you use Klein's construction..
In any case make the crankpin velocity vector equal to the drawing
length of the crank and locate both acceleration and velocity
vector polygon poles at the crankshaft center. Relate the scales.
c. Determine the inertia force of the pistons and connecting rods,
and show them properly located and oriented as vectors on the space
diagram.
VI - DYNAMIC FORCE ANALYS IS
PROBLEM 50, FIGURE 2, TRANSPORT
Figure scale is 5.00 inches per inch. The speed of the linkage drive
crank is constant at 120 rpm. All elements are of uniform thickness.
Weights and Moments of Inertia are as follows:
Element Crank Coupler Rocker Finger Link Unit
Weight: 1.5 3.5 } 2.0 75- pounds
Moment of
inert ia 0.026 Qua ~- 400 lbin-sec.2
0,' 67 a L Uan d

DYNAMICS OF MACHINERY DYNAMIC FORCE ANALYSIS
a. Draw a space diagram of the linkage in the position shown at a scale
of 2 5 inches per inch with the follower rocker center located at-,
0.5, 7.5. Paper horizontal.
b. Draw the velocity vector polygon with pole at 4,2.5 and driver
crankpin velocity vector length of 2.5 inches.
c. Draw the acceleration diagram with pole at 10,5.5. Relate the
scales.
d. Determine the acceleration of the center of gravity for crank,
coupler, and rocker.
e. Determine the inertia force for each of those members.
f. Show by vector the proper location and orienta'tion of each on the
space. diagram.
g. Determine the inertia force of. the finger link and its location
and orientation.
h. What will be the reaction to this force on the rear coupler fingerlink ~joint: pin.?
PROBLEM 51, FIGURE 25, SHAPER
Figure scale is 5.00 inches per- inch. Speed of the bull gear is 106 rpm.
Weights and Moments of Inertia are as'follows:
Element Bull Gear Sl'ider Rocker Coupler Ram Units
Crank
Weight 100 5.00 85 10 200 pounds
Radius of
gyrat ion
about c.g. 6 2.50 16.5 4.5 30 inches
a:- Draw a -space diagram of the linkage in the position for a crank
angle 315 degrees later than that shown at a scale of 5.00 inches
per inch. Locate the bull gear center at 2.0,4.5, with paper
27

DYNAMICS OF MACHINERY DYNAMIC FORCE ANALYSIS
horizontal.
b. Draw the velocity vector polygon with pole at 7,2.5 and crank pin
velocity vector length 2 inches.
c. Draw the acceleration vector polygon with pole at 10,4.5. Relate
the scales.
d. Assume the center of gravity of the drive crank bull gear to be
located at 5/8 inches from the center toward the crank pin. All
other gravity centers are at midpoints. Determine the acceleration
of the gravity centers.
e. Determine the inertia force for each member. Locate and orientate
them- on the space diagram.
PROBLEM 52, FIGURE 28, STRAIGHT PRESS
Figure scale is 5 inches,per -inch. The data and acceleration diagram for
the linkage is as shown: S = 100 in/sec. /in.
Weight Momentof Center of O~
inertia gravity (on axis)
Crank 16 0.160 -1.5 from crankshaft
Conn. Rod 30 2.500 2. 5 from crankpin
Crosshead.100 - 2.5 from balljoint
Units pounds: lb-in-sec. inches
a. Draw a space diagram of the linkage in the position shown at a scale
of 5 inches per inch; -paper horizontal.- Locate the crankshaft
center at 2,6.
b. Draw each member as a free body diagram showing static and -inertia
forces.
c.- Construct the force polygon at a scale of 25 lbs. per inch with the
orig in:of- the weight - edtor- at 8.6.
d. Determine the force from frame to crosshead.
28

DYNAMICS- OF MACHINERY DYNAMIC FORCE ANALYS IS.e-. Determine the torque input on the crank shaft.
PROBLEM 53, FIGURE 1, DIESEL ENGINE.
Figure scale is 2.5- inches per inch. Engine speed is 1800 rpm. Gas
pressure after injection is 1,200 lbs. per square inch and 900 lbs. per
square inch 30 degrees of crank angle later.'Pertinent mass data is as
follows:
Weight Moment Center of
of gravity
inertia
Crank 8.00 0.326 1.5 from- crankshaft axis
Conn. Rod 12.00 1.280 6.5 from wristpin
Piston 9.00 - 0.625 above wristpin
Units pounds- lb- in-sec. inches
a. Draw a space diagram with crank angle 30 degrees from top dead
center and crankshaft center at 2, 1.5.
b. Determine the acceleration of centers of gravity by Klein's
construct ion.
c. Determine the inertia forces for each element and show them on the
space diagram.
d. Draw a force polygon- including inertia forces but neglecting
fr-ictiof, locating origin of the gas pressure force vector at 5,6.
Make that vector 4. -inches in length.
e. Determine the crankpin and wristpin loads.
f. Do the.same for the position shown, i.e., top dead center after
injection.
PROBLEM 54, FIGURE 11, V-8 ENGINE
Figure scale is 2 inches per inch. Engine speed is 3000 rpm. Gas pressure
for the position shown is 500 lbs. per square inch in the right bank
29

DYNAMICS OF MACHINERY DYNAMIC FORCE ANALYSIS
cylinder and 100 lbs. per square inch in the left bank cylinder.
Pertinent mass data is as follows:
Weight Moment of Center of
inertia gravity
Crank 4.00 0.042 0.75 from crank center
Conn. Rod 4.50 0.268 4.00 from wrist pin
Piston 5.00 0.75 from wrist pin
Units pounds lb-in-sec. inches
a. Draw a space diagram of the linkage in the position shown at a scale
of 2 inches per inch with the crankshaft center located at 3,4.5;
paper horizontal.
b. Determine the acceleration of the centers of gravity by Klein's
construction. (draw the inertia force vectors on the space diagram).
c. Draw a force polygon including inertia forces but neglecting
friction, locating the origin of the gas pressure force for the
right bank cylinder at 8,6. The force scale is 1000 lbs. per inch.
d.. Determine the crankpin, wristpin, and cylinder wall-piston loads.
PROBLEM 55, FIGURE 24, INDEXING MECHANISM GENEVA LINKAGE
Figure scale is 0.75 inches per inch. The output shaft with tools, turret,
shaft and Geneva cross has a combined weight of 1.5 lbs. The unit is suspended by a wire as a torsional pendulum to determine its moment of inertia.
The wire has a torsional spring stiffness of 0.05 lb. inches per radian and
the period is measured at 7.9 seconds. The clutch shaft speed is 240 rpm.
a. Make a space diagram of the Geneva drive disk and cross at a scale
of 0.25 inches per inch, drive disk center located at 2,7. Set
the position so that the drive pin center is at midstroke in the
groove.
b. Determine the angular acceleration of the output shaft unit.
30

DYNAMICS OF -MACHINERY DYNAMICS FORCE ANALYSIS
c; Determine the inertia torque of the output shaft.
d. Determine the torque at the clutch. What effect would the addition
of tools to the turret have?
PROBLEM 56,P FIGURE 2, TRANSPORT
Figure scale is 5.00 inches per inch. Speed of the driver crank is- 120 rpm.
The mass data is given in problem 50. The product being transferred weighs
75 lbs per unit. The coefficient of friction between product and frame
is 0.4.
a. Using the inertia forces determined in problem 50, make a dynamic
force analysis.. Locate the force polygon pole at 2,2. Force scale
is 30 lbs per inch. Draw free body diagrams.
b. Determine the forces on the.two frame bearings.
c. Determine the input torque on the drive crank.
PROBLEM 57, FIGURE 2, TRANSPORT'Figure scale is 5 inches per inch. Mass data is given in problem 50.
Speed of the driver crank is 120 rpm. The product being transferred is 75
lbs per unit. The coefficient of friction between product and rails is
0.4. The crank angle is 45 degrees later than that shown.
a. Make a space diagram at a scale of 2.5 inches per inch with follower rocker center located at 0.5,7.5 with paper horizontal.
b. Draw a velocity vector polygon with driver crank pin velocity
vector length of 2.5 inches and with pole located at 8.5,6.
c. Draw an acceleration vector polygon with pole at 10,5,7. Relate
the scales.
d. Show the inertia forces at the centers of gravity on the space
diagram.
31

DYNAMIC$ OF MACHINERY DYNAMIC- FORCE ANALYSIS
e. Draw a force, polygon including static and inertia forces with the
pole located at 2,2.
f.~- Determine the frame bear ing;forces.g. Determine the torque input.
PROBLEM 58,- FIGURE 2, TRANSPORT
The same as problem 57 with a crank angle of 180 degrees from the position
shown.
PROBLEM 59, FIGURE 25, SHAPER
Figure scale is,5 inches per~ inch. Data is as iindicated in problem 51.
a. Draw a space diagram of the linkage in the position for a crank
angle of 315 degriees later tha-n that shown a-t- a scale of 5 inches
per inch. Locate the bull gear center at 5,7.
b. Using the inertia force values determined in problem 51, make a
dynamic force analysis with force polygon pole at 2,2. Neglect
friction-.:.- Force -scale -is 200, lbsi. per inch.
c. Determine the loads on all bearings.
d. Determine the torque, input.,
PROBLEM 60; FPIGURE 25, SPER:
Figure scale is 5 inches- per inch. Cutting load is 300 lbs. Other data
is -as founds in probleim 51.
a. Draw a space diagram of the linkage in the position for a crank
angle 135' degrees -la-ter-:than that: shown.
b. Draw a velocity vector polygon with, the crank pin vector length
l. 5 inches and pole at 6,8.
c. Draw the acceleration vector polygon with related scale at 1.5,8.
32

DYNAMICS. OF MACHINERY DYNAMIG FORCE ANALYSIS!
d. Determine the inertia forces and show them in proper location and
orientation on the space diagram.
e., Do a dynamic analysis with force polygon pole at 7.5,3 and a force
scale of 200 lbs. per inch.
f. Determine the torque input.
g. Determine the shaking force on the — frame.
PROBLEM 61, FIGURE 25, SHAPER
Same as problem 60 but add friction forces. Assume coefficient of friction
to be 0.25 for flat sliding joints and 0.50 for pin joints. These values
are, of course, exaggerated, but will illustrate the effect of friction on
the polygon,
PROBLEM:62, FIGURE- 9, SCRAPER HOIST
Pigure scale is 4 inches per inch. The sun gear of the planetary gear train
on the left is accelerated from 0 to 120 rpm in 6 se6con-ds with a- 150 lb.
load at the root of the left cable drum. The moments of inertia of the sun
gear, planet gear, carrier and drum are 0.085, 0.500, 0.935, and 4.140
lb-in-sec. respectively.
a. Make a force analysis for the condition of constant speed at 120
rpm.
b. Determine the t planet bearing loads; the sun gear bearing load.
c. Determine the torque on the sun gear and on the ring gear.
d. Do the'same for the period of acceleration.
33

DYNAMICS OF MACHINERY FLYWHEELS
VII - FLYWHEELS
PROBLEM, 63, F IGURE 21, "C" FRAME PRESS
Figure scale is 4 inches per inch. The press is driven by a design B
electric motor rated at one HP and 570 rpm. See the performance curves of
Figure 31 for torque speed characteristics. A multiples V-belt drive
reduces the speed by 8/1. The press is to be used to punch a hole of 1
inch diameter in' inch SAE 1020 cold rolled steel plate with an ultimate
-shear;str eng;th of 50,!000 lbs. per square inch.
a. Determine the coefficient of speed fluctuation in the flywheel.
b. Determine the maximum and minimum flywheel speeds.
c. Determine the maximum and minimum torque output of the motor.Determine the motor horsepower that would be necessary without
-the flywheel.
PROBLEM 64, FIGURE 20, CRUSHER
Figure scale is 10 inches per inch. The crusher flywheel turns at a
maximum speed of 114 rpm and has a speed fluctuation coefficient of 0.2.
Assuming that the crushing takes place in 0.1 of the total cycle time:
a. Determine the horsepower load on the motor. Recommend the motor
design.
b. Estimate the resultant load at 15 inches up from the bottom edge of
the swinging jaw.
c. Explain why the flywheel is necessary.
PROBLEM 65, FIGURE 2, TRANSPORT
Figure scale is 5.00 inches per inch. The transport is driven by an
34

IDYNAMICS, OF MACHINERY FLYWHEELS
electric motor rated at 855 rpm. The speed is reduced -through the drive
to 120 rpm, at the linkage drive crank shaft. A load of 900 lbs. imposed
On the finger link is moved 6 inches each cycle of the machine. The load
is in contact with the finger link for 90 degrees of rotation of the crank
angle. A flywheel coefficient of speed fluctation of 0.05 has been recomme nde d.
a. Design a flywheel for the transport to be mounted on the motor shaft.
Give material, mean rim radius, and rim cross-sectional dimensions.
b. Design a flywheel to be mounted on the linkage drive crank shaft.
c. Determine the saving in motor horsepower demand by use of the
flywheel.
d. Recommend a motor rating and design type.
PROBLEM 66, FIGURE 16, CONE CLUTCH
Figure scale is 2 inches per inch. The cone clutch assembly varies in
speed from 1140 to 1026 rpm in 36 degrees of rotation and regains its speed
in the remainder of the revolution.
a. Determine the energy available in the flywheel effect of the
assembly.
b. Determine the horsepower transmitted through the clutch.
PROBLEM 67, FIGURE 1, DIESEL -ENGINE and FIGURE 10, MARINE REDUCTION AND
REVERSE GEAR
Figure scales are 2.5 inches per inch for Figure 1 and 2 inches per inch
for Figure 10. You have been presented with a proposal to combine the
marine reduction and reverse gear with a 6 cylinder die8sel engine of the
same design as that of Figure 1, except that it has 3 more cylinders.
The specific problem posed to you here is to determine whether the flywheel
effect of the fluid coupling housing is sufficient. If it is not you are

DYNAMICS OP MACHINERY FLYWHEELS
to redesign the: housing for proper flywheel effect and attachment to the
engine crar:kshaft.
The turning effort diagram of the engine has a force scale (ordinate) of
1200 lbs. per inch and a space (abscissa) scale of 1 inch per inch. It
shows a mean tangential effort value of 2.7 inches. The area above the
mean turning effort line under one of the loops is 4.00 square inches.
The coefficient of speed fluctutation recommended for engines is 0.033.
a. Check the weight of the fluid coupling housing to see whether it
will serve as a. flywheel.
b. Check the weight of the flywheel on the engine.
c. Make any design modifications necessary and present them on a
scaled drawings,! dimensioned.
VIII - BALANCING
PROBLEM 68, FIGURE 2, TRANSPORT
Figure scale is 5 inches per inch. The drive crank pin rod is of cold
rolled steel and the cranks are of cast iron.
~a. What are the loads on the crank shaft by cranks and crankpin only,
for 120, 240, and 2400 rpm?
b. Determine the magnitude,- location, and orientation of counterweights
necessary to balance cranks and crankpin.
c. Are counterweights necessary for this machine? Explain.
PROBLEM 69, FIGURE 14, AUTOMATIC TRANSMISSION
Figure scale is 1 inch per inch. The double planet gears in mesh with
forward sun and ring gears weigh 0.250 lbs. The single planets in mesh
with the forward sun gear weigh 0.125 lbs. The planetary system is locked

DYNAMICS OF MACHINERY -BALANCING
in high gear and rvotating at 3000 rpm.,
A. Compute the forces -imposed on-the carrierb. Draw a force vector polygon including the forces for all 6 gears
to.. ch.ckt the..alanc-e of the. planetary assembly. Locate the Dole
at 5,4 and make the force vector'for the! double. planet gear 4
inches long.
c. Is there any dynamic unbalance on the assembly? Explain.
PROBLEM 7-0-, PFIURE l, DIESEL BNGINE:Figure scale: is 2.5 inches per inch. Engine speed is 1800 rpm. The
counterweight: on the for ward end of- the: cam shaft, weighs 3. -lbs.: Its
center of gravity is at a- radius of 2.2 -inches. The - camshaft drive gear
on the rear of the shaft has a counterwieght built integrally into it.
Design: a.a uterbalance sector to be integrated -intoo the gear
giving weight and location vf center of gravity.,
b. Wl! this camshaft- be sta:tically balanced? -Prove it.
c. Will this camshaft be dynamically balanced?
d. Determine the loads imposed on the camshaft bearings by the counterbalances. Assume two end bearings only.
PROBLEM 71, FIGURE 1, DIESEL ENGINE
Figure scale is 2.5 inches per inch. The unbalanced weight of the crank
in the center cylinder is 20 lbs. The connecting rod weighs 18 lbs. and
its center of -gravity is located 6. 5 inches down- from- the wr-istpin.
a. Draw the vector polygon to determine the dynamic unbalance of the
crankshaft wi-thout any counterweights Locate- the pole at 4,4 and
make the vector for crank in the middle 2 inches long.,
b. Drawthe vector polygon to determine:the static unibalance. Locate

DYNAMICS OFI MACHINERY BALANCING
the pole at 4,7 with the middle crank vector 2 inches long.
c. Determine the weight and orientation of counterweights to be
located in planes of cylinders 1 and 3.
d. Design the counterweights. Submit a sketch with -"material and
dimensionions, indicating -size and location of center of gravity.
PROBLEM 72, FIGURE 1, DIESEL ENGINE
Figure scale is 2.5 inches per inch. Weight data for the crank, rod, and
piston and the location of the rod center of gravity are as given in
problem 53. Engine speed is 2100 rpm.
a. Draw a polar- shaking force diagram for the middle:cylinder only,
diegarding all counterbalance effects. Force scale is 5000
lbiS..- per inchh.b. Add;-a counterweight equal to-the total weight- of rotative and
reciprocative masses and draw in the shaking-for;ce curve.
c. Add a counterweight equal to the total weight of rotative and
one half reciprocative masses and draw in the shaking force curve.
d. Devise a method by which a single cylinder engine might be
Completely balanc-ed.
PROBLEM 73, FIGURE 1, DIESEL ENGINE
Figure scale is 2.5 inches per inch. Weight data for the crank, rod, and
piston and location of the rod gravity center are given in problem 53.
a. Draw~ the unbalance vector polygons arranged in the tabular form
indicated below, at twice that size.
b. Mtate the type (force or moment) and cause (rotative- primary
reciprocative or secondary reciprocative) of unbalance.
c, xplain how; each factor was counterbalanced in this engine.
38

DYNAMICS OF MACHINERY BALANCING'
d. Determine the magnitude of all counterweights.
e. Draw a curve of moment vs. crank angle to show the debit unbalance
after counterweights have been credited.
-f. Suggest a: method by which the engine might have been completely
balanced.
Reciprocat ive
Causes Rotative: Primar y Secondar
Type
r
S
i______ 5|-S 4000 lbs/in. _ _,
M.
3000 bs
S 3000 lbs.ft.
inE
PROBLEM 74, FIGURE 11, V-8 ENGINE
Figure scale is 2 inches per inch. Weight data for the engine is as
indicated in problem 54. Crank configuration is 0-90-270-180 taken clockwise. Bank angle is 90 degrees.
a. Lay out a space diagram as indicated below at twice that size.
The unbalance analysis tabular arrangement is as indicated in
problem 73.
b. Draw the force and moment polygons in the positions indicated for
39

DYNAMICS, OF MACHINERY BALANCING
each bank separately. Use scale to provide-polygons as-large as
the space will permit.
c. State type and cause of unbalance.
d. Determine the magnitude, location, — and -orientation of. the counterweights necessary to completely balance the engine.
IX - VIBRATIONS
PROBLEM 75, FIGURE 2, TRANSPORT
Figure scale is 5 inches per inch. Transport carries 12 ingots of steel
of the section size indicated and 30 inches long. Beams and columns are
standard structural steel 3 x 2 3/8 I bars with a -weight of 5.7 lbs. per
ft. length. The moment of inertia about the neutral axis perpendicular to
the web at center: is 2i.55 inches, and about the neutral axis parallel to
4
the web at the center is 0.56 inches.
a. What would be the natural frequency of vribration for motion along
the length of the transport?
40

DYNAMICS OF MACHINERY VIBRATIONS
b. Determine the natural frequency for transverse vibrations.. Is the operating speed- of 240 rpm critical? Explain.
d. Assume that the machine is transporting hot ingots with a coefficient of friction equal to 1.00 and that the frictional force is
an harmonic shaking force. Assume also that the damping factor
is 0.15. Determine the amplitude of the vibration. Are these
assumptions valid? Explain.
e. Under the condition assumed in d, what would the amplitude be for
the shaking force frequency equivalent to 240 rpm of the linkage?
PROBLEM 76, FIGURE 9, SCRAPER HOIST
Figure scale is 4 inches per inch. The weight of the left planetary sun
gear is 6 lbs. and of the right planetary sun gear is 3 lbs. Assume
that 6,500 inch pitch diameter drive gear on the right end of the shaft
has a negligible effect.
a, Determine the natural frequency of transverse vibration of the shaft.
b. Is the shaft operating at critical speed with a motor speed of
1800 rpm?
PROBLEM 77, FIGURE 7, HELICAL GEAR SPEED REDUCER
Figure scale is 2 inches per inch. Motor speed is 1800 rpm. Gear reduction ratio is 18/70.
a. Determine the critical speed of the shaft as drawn.
b. Is the operating speed critical? Explain.
c. Assume that the frequency of tooth engagement is a disturbing
force frequency and that the damping factor is 0.2, and determine
the amplitude magnification factor.
41

DYNAMICS -OFP MACH INERY VIBRATIONS
PROBLEM 78, FIGURE 4, REAR AXLE
Figure scale is 4 inches per inch. The -moment of inertia of wheel plus
tire is 4.50 lbs-in-sec.2 and of gears etc., inside the differential is
0.280 lb-in-sec.2 Assume the shaft to be uniform in diameter at 1.250
inches.
a, What is the critical speed for torsional vibration of the axle?
b. Approximately how far from the differential end of the axle will
the node occur?
c. Is resonance likely to occur?
PROBLEM 79, FIGURE 11, V-8 ENGINE
The crankshaft of the engine can be reduced to a system in which the polar
moments of inertia I = I = I- = I = 0.1lb-in-sec.2. The shaft stiff1 2 3 4
ness between cylinder centers is 6 x 106 lbs-inches per radian.
"a. Show the "normal" curves to indicate the configuration of the
system for the first, second, and third nodes.
b. Determine the fundamental natural frequency and the second and
third harmonics.
c; Put all three cases into a Holzer tabulation to check the values.
PROBLEM 80, FIGIRE 1, DIESEL. ENGINE
The engine can be reduced to a dynamically equivalent system as indicated
below in which I I= 0.600 lb-in-sec.2 2 = 0.250 and I = 12.00
1 3 2 4
lb-in-sec.2 The torsional stiffnesses are ktl = kt2 = 36 x 106 and
kt3 = 180 x 106 pound inches per radian.
42

DYNAMICS OF MACHINERY VIBRATIONS
a. Reduce the system to an approximately equivalent two mass system
and compute the first estimate of the fundamental natural frequency.
b. Use the first approximation of part "ta" in a Holzer tabulation
check.
c. Plot the residual torque values of trials to date against the
frequency estimates.
d. From the curve of "c" make an estimate of the second harmonic.
e. Follow the same procedure to get the third harmonic.
f. Draw the configuration curves of angular displacement amplitude,
O, against position on shaft.
c, ktt:3!4
43

MACHINE DES IGN PROBLEMS
X - MATER IALS
PROBLEM 81
a. Briefly explain the difference between cast iron and steel so far as
chemical composition is concerned.
b. Give the approximate carbon content of low, medium, and high carbon
steels.
c. State 2 ways of changing the composition of steel to increase its
strength.
d-. A piece of 1040 steel is to be hardened by heat treating. State the
3 main steps of this heat treating process.
e. What carbon content would you specify for steel to be used for each
of the following: (i) structural beam, (2) high strength machine shaft,
(3) a spring, (4) a piece to- be carburized, (5) a lathe tool bit?
f. Describe the carburizing process, and explain why a steel such as 1050
is not used for carburizing.
g. What approximate relationship exists between the tensile strength and
shear strength of steel?
h. What approximate relationship exists between the Brinell hardness and
the tensile strength of steel?
PROBLEM 82
List what you would iconsider to be the comparative advantages and disadvantages of the following materials so far as use in machinery is.concerned:
1. steel 4. magnesium
2. cast iron 5. brass
3. aluminum 6. bronze

MACHINE DESIGN MATER IALS
PROBLEM 83
A beam having a rectangular cross section; is to be made from each of the
following mater ials:
0
1. Rolled 4640 steel, quenched- and tempered at 1000 F
2. Aluminum 24 S alloy, T 4, HT
3. Extruded AZ 61-X-magnesium
In each case the beam width is to be 1",: and all: 3 of the beams are to have
the same strength in bending. Compare the weights of the 3 beams.XI - STRESS AND STRENGTH
PROBLEM 84,
a. Using words, not equations, define "stress" and "strength", -and discuss
the relationship that must exist between "stress" and "strength" in a
properly designed machine part.
b. List the main reasons for using a safety margin, or safety factor, when
designing machine parts.
c. Explain why lower safety margins are commonly used in aircraft design,
where failure may be disastrous, than in-many industrial machines where
failure endangers no one.
PROBLEM 85 - FIGURE 19, EXTERNAL SHOE BRAKE
a. Describe the construction and operation of the brake.
b. A brake similar to that shown is applied by a spring which exerts a
downward force of 800 lbs on the cylinder rod. The rod is to be made
of 1020.steel as rolled. What rod diameter would you recommend to carry
the 800 lb load?
c. Discuss what considerations, other than the ability to carry the 800 lb
load, might influence the'final decision as the diameter of rod to be used.
4.5

MACHINE DESIGN STRESS AND STRENGTH
PROBLEM 86, FIGURE 19, EXTERNAL SHOE BRAKE
a. Describe the operation and construction of the brake.
b. A brake similar to that shown is applied by~a spring which exerts a
downward force of 800 lbs on the cylinder rod. The bell crank link
which is pin connected to the top of the right hand brake- shoe lever
is to be made of ASTM A47-33 malleable iron. The distances between
pin joints can be taken as 4 times the distances shown on the drawing.
Establish the cross section >dimensions needed on the horizontal arm
of the bell crank link midway between the two pins, making the depth
4 times the thickness.
c. Discuss What considerations, other than the strength of the link,
might influence the de'cision as to the actual dimensions to be used
for the link.
PROBLEM 87
a. State the maximum shear theory of failure, and. the maximum normal
stress theory of failure, and name the common materials to which each
theory is considered to apply.
b. Discuss fatigue failure of metals, and the loading conditions which
cause this type of failure.
c. Define the following in words:
1. completely reversed bending
2. partially reversed. loading
3. endurance 1 imit4. stress concentration factor
5. notch sensitivity
d. Discuss the relationship of Brinell hardness, ultimate tensile strength,
and flexural endurance limit for steel.
46

MACHINE DESIGN STRESS AND STRENGTH
PROBLEM 88
a. Two pieces cut from a common steel bar are hardened to 250 and 500
Brinell respectively. Discuss how the ultimate strength in tension,
and the endurance limit in completely reversed bending, would compare
for these two pieces.
b. Formulate some general rules to be followed when designing parts to
carry variable loads.
PROBLEM 89, FIGURE 1,- DIESEL ENGINE
a. Describe the construction and operation of the engine.
b. An engine similar to that shown has a 4*" cylinder bore. When this
engine is developing its rated horsepower at 2000 rpm, the piston
exerts a force on the piston pin which varies from zero to 15,000 lbs
during each revolution of the engine. To obtain sufficient bearing
area, the outside diameter of the pin is to be 1i", and to provide a
hard surface the pin is to be carburized. Select a material for the
pin, and determine the inside diameters of the pin. Show these diameters
on a neat sketch, drawn full scale.
PROBLEM 90, FIGURE- 1, DIESEL ENGINE
a. Describe the construction and operation of the engine.
b. An engine similar to that shown has a 4*" cylinder bore. The load on
the push rod which actuates the fuel injector rocker arm varies from
zero to 1000 lbs during each revolution of the engine. Establish a
satisfactory combination of:
1. pushrod material and hardness
2. pushrod diameter

MACHINE: DESIGN FITS AND TOLERANCES
XZI I FITS AND TOLERANCES:
PROBLEM 91
a. Explain why tolerances are necessary on manufactured machine ~parts.
b. Discuss the way in which the design and construction of the following
are affected by the necessity of having tolerances:
1. The coupling which connects the motor shaft to the pinion shaft
on the Helical Gear Speed Reducer, Figure 7.
2. The pinion mounting of the Bevel Gear Speed Reducer, Figure 12.
3. The operating linkage of the Thrustor Brake,- Figure 15.
PROBLEM 92, FIGURE 7, HELICAL GEAR SPEED REDUCER
a. Describe the construction and use of the speed reducer.
b. The cast steel gear is to be a shrink fit on the 4"1 diameter steel
shaft. Establish the maximum and minimuii dimensinsi for the'shaft
diameter, and for ihe he in the gear. State thetype of machining
operation you would recommend to finish'the'shaft and bore.
c. Determine a satisfactory hub diameter for the shaft and hole dimensions
found above.
PROBLEM 93
Discuss the "basic hole" system of dimensioning, why it was developed, and
wnether-or not it should-be, used I fo-r dimensioning the shaft and gear hole
of problem 92.
PROBLEM 94, FIGURE 12, BEVEL GEAR SPEED REDUCER
a. Describe the construction and use of the speed reducer.
b. An actual speed reducer is to be the size shown. Make a neat sketch,
to scale, of the cartridge which contains the input shaft bearings.
On this sketch show the following dimensions with suitable tolerances:

MACHINE DESIGN FITS AND TOLERANCES
1. locating or piloting diameter of cartridge
2. diameter of housing bore into which cartridge pilots or fits
3. bearing diameters
4. diameter of bore into which bearings fit
5. concentricity limits of bearing- bore diameter and cartridge pilot
diameter
6. distance between bearing shoulders
PROBLEM- 95, FIGURE 12, BEVEL GEAR SPEED REDUCER
a. Describe the construction and use of the speed reducer.
b. The drawing is 4 the size of an actual speed reducer. All lengthwise
dimensions parallel to the output shaft are to have a tolerance of
0.010", except for the bearing assemblies which have a tolerance of
0.005". A 0.015" thick gasket is to be used between the housing and
the top cover. Plastic shims beneath the end caps are to allow correct
positioning of the bevel gear, and to remove clearance from the bearings. The minimum shim thickness at either cap is to be 0.010".
Determine all necessary linear dimensions of the output shaft assembly
and the housing assembly., Show these- dimensions on a neat sketch, and
determine the -maximum combined shim tihicknes- that could be r-equired
at- the two,caps.
XIII SPRINGS
PROBLEM 96, FIGURE 19, EXTERNAL SHOW BRAKEa. Describe the construction and operation of the brake.
b. To apply a brake similar to that shown, the spring must exert a force
of 800 lbs. The br ake is to be released by compressed air at 80 psi,
which will move the plunger 1-". To hold the spring in position, the
inside diameter of the cylinder is to be no more than -i" larger than
49

MACHINE DES IGN SPRINGS
the outside diameter of the spring. The brake is to be applied and
released at an average rate of once every 10 minutes during a normal
8 hour work day.
Design the spring, stating a satisfactory combination of:
1. outside diameter of coil
2. wire diameter (W-M std. gage)
3. wire material
4. number of coils
5. type of ends
6. pitch of coils
7. approximate free length
8. inside diameter of air cylinder
PROBLEM 97, FIGURE 8, CLUTCH-AND TRANSMISSION
a. Describe the construction and operation of the clutch, including the
way in which the clutch is engaged and dis-engaged.
b..A force of 1000 lbs is required to apply a clutch of the type shown.
This —force is to be supplied by 6 springs equally spaced around the
pressure:plate. Available space limits the outside diameter of the
springs to 1i" maximum, and the length of the springs to 1 3/4" when
the clutch is engaged. The pressure plate must move 1/8" to disengage
the friction surfaces, and the lowest spring rate reasonably possible
is desired.
Design the springs, stating a satisfactory combination of:
1. outside diameter of coil
2. wire diameter
3. wire material
4. number of coils
5. type of ends
6. pitch of coils
7, approximate free length
50

MACHINE DESIGN SPR INGS
PROBLEM 98, F IGIURE 15, THRUSTOR BRAKE
a. Briefly describe the- construction and operation of the brake.
-b. A spring force of 300 lbs is required to apply a brake similar to that
shown. When the brake is released by the thrustor, the spring is
further compressed 4" which should increase the spring force by no
more than 25%. Design the spring, stating a satisfactory combination
of:
1. outside diameter of coil
2.. wire diameter
3. wire material
4. number of coils
5. type of ends
6. pitch of coils
7. approximate free length
PROBLEM 99, FIGURE 11, V8 ENGINE
a. Describe the construction and operation of the engine, including the
valve operating linkage.
b. An exhaust valve spring is to be designed for an engine with performance
as shown by the curve of Figure 31. Valve lift is to be 3/8", and the
spring is to exert a force of 40 to 45 lbs when the valve is closed,
and 88 to 93 lbs when the valve is fully open. Available space limits
the outside diameter -of the spring to 1 5/8"' maximum-, and limits the
length of the spring to 1 5/8" maximum when the valve is closed.
Determine a satisfactory combination of:
1. mean coil diameter 7. approximate free length
2. wire diameter (W-M std. gage)
3. wire material and treatment
4. number of coils
5. type of ends
6. pitch of coils
51

MACH INE:DES IGN SPR INGS
PROBLEM 100,.FIGURE 1, DIESEL ENGINE
a. Describe the operation of the Diesel engine, including the valve operating linkage.
b. A valve spring is to be designed for a Diesel engine similar to that
shown. Valve- lift is to be 0-.390". The spring is-to exert a force
of 14Q lbs! when the valve is fully open, and 44 lbs when the valve is
closed. Available space limits the length of the spring to 21" maximum
when the valve is closed. and limits the outisde diameter of the coil
to a maximum of 1"2:. Engine speed is to be 2100 rpm. Establish a
satisfactory combination of:
-1. mean coil diameter
2. wire diameter (W-M std. gage)
3..- wire material and treatment
4. number of coils
5. type of ends
6. pitch of coils
7. approximate free- length
PROBLEM 101, FIGURE 9, SCRAPER HOIST
a. Describe the construction and operation of the hoist.
b.- The two tension springs which pull the band brake free of the ring gear
arte to: exert a force of 30 lbs each, are to have a spring rate of 60 lbs/
inch, and are to be wound with an initial tension of 10 lbs. Design the
springs, stating a satisfactory combination of:
1. mean co il diameter
2. wire diameter
3. wire material
4,. number of coils
5. type of ends
6. approximate free length of coiled section
52

MACHINE DES IGN:SPRINGS
PROBLEM 102, FIGURE 14, AUTOMATIC TRANSMISSION'
a. Describe the operation of the band brake operating- linkage.s
b. Neatly sketch a characteristic load vs. deflection curve for a conical
coil,sring like that usedz in the brake actuating cylinder.: Discuss
the shape of the curve, and label any significant::points.
c. What is the probable advantage of the conical coil spring as compared
to a cylindrical coil spring in the installation shown?
PROBLEM 103, FPIGURE 22, TRUCK CHASSIS
a. Describe the three separate functions performed by the leaf spring in
the suspension shown.
b. Sketch and describe what is commonly known as a "torque.tube" drive for
automobiles.
c. Discuss the comparative advantages and dis-advantages of coil springs
and leaf springs'when used in passenger automobile rear suspensions so
far as comfort, stability, and Steering are concerned.
d. Explain: the function of the rebound clips used on -the leaf springs.
PROBLEM 104, FIGURE 22, TRUCK CHASSIS
a. Describe tne construction and operation of the rear suspension shown on
the truck.
b. The rear springs of a small truck are to hold a maximum load of 750 lbs
each, and to have a deflection rate of 250 lbs/inch. The engine develops
a maximum torque of;200 lbft, the rear end ratio is 3:1; and- the 4 ply
tires are ssize 6,70-x 15.
Design the leaf spring, and make a' neat sketch -showing all necessary
dimensions,. Tabulate a satisfactory combination of:
53

MACHINE DESIGN- SPRINGS
1. spring length and width
2,. number of leaves
3. thickness of leaves
4. camber in free position
5. material and treatment
6. length of each leaf
XIV - THREADED FASTENERS
PROBLEM 105
a. When machine parts are bolted together, what condition commonly exists
which causes the bolts to be relatively more elastic than the parts
being fastened:?
b. Discuss the- significan'ce of the initial tightening load, and of the
applied load, so far as bolts are concerned. Explain which of the above
loads must be the larger for a properly designed bolted joint, and how
each affects the total load on fthe bolt.
c. Discuss the problem of establishing bolt loads with reasonable accuracy
when the bolts are tightened with ordinary box-end or socket wrenches.
d. Explain why the connecting rod bolts of the Diesel Engine, Figure 1,
have a reduced diameter along the body of the bolt.
PROBLEM 106, FIGURE 9, SCRAPER HOIST
a. Describe the construction and operation of the scraper hoist.
b. A scraper hoist which is 5 times the size shown is to be fastened down
to a foundation by a row of bolts along the flange of each skid, The
hoist is powered by an AC induction motor having characteristics as
shown by the curve of Figure 31 for design D motors. When the motor
develops its rated horsepower, the shorter of the two drums is to be
54

MACHINE DES:IGN THREADED FASTENERS'
capable of- exerting'a pull of- 4000 lbs on:a wire rope. Determine a
sat.iisfact.ory combination of:
1. number of bolts to be provided in each flange
2. bolt diameter
3. bolt material
PROBLEM 107, FIGURE 9,: SCRAPER HOIST
a. Describe the operation and use of the scraper hoist.
b.- Discuss -the problem of.bestablishing the sizebolts to be used where parts
of the frame or supporting structure are bolted together, and where the
side: pieces are bolted to the ring gears,
PROBLEM 108, FIGURE 28, STRAIGHT PRESS
a. Describe the construction and- operation-'of the press.
b. A 40 ton capacity press is 8 times: the size shown. The 3 piece cast iron
frame of the press is held together by 4 tie rods as shown. Determine
a satisfactory combination of:
1. tie rod diameter, material, and heat treatment:2u recommended tightening torque
PROBLEM 109, FIGURE 27, AIR CYLINDER
a. Describe the construction and use of the cylinder.
b. A cylinder having a 6" bore and a 10" stroke is to be actuated by air at
100 psi. Determine- a satisfactory combination of:
1. number of tie-rod bolts to be used
2. diameter, material, and heat treatment of tie-rod; bolts
3. recommended tightening torque
c. It is Proposed that the construction by changed to have the end pieces
extend further into the cylinder. Sealing of the ends would then be
accomplished by an "0" ring static seal, rather than by the.comoression
55

MACHINE DES IGN THR ED PFASTENERS
gasket shown. Skeitch this new construction and discuss its advantages
and dis-advantages so far as the tie-rod construction is. concerned.
PROBLEM 110, FIGURE 14, AUTOMATIC TRANSMISSION
a. Describe the construction of the hydraulic torque conver,-ter.
b. The drawing is 3/4 of the actual size of an automatic ttansmission used
with a gasoline engine which performs as shown by the curve of Figure 31.
To prevent overheating, oil is pumped through the converter at 30 psi by
the front pump of the,transmission, Establish a- satisfactory combination.of
1. number of bolts reqlulired to fasten the converter cover to the
converter pump
2. size, material, and heat treatment of bolts
3. recommended tightening torque
PROBLEM,ll, FIGURE 1, DIESEL ENGINI
a. Describe the construction and operation of the engine, and explain why
a flywheel is necessary.
b. The drawing is - the size of an actual engine which performs as shown
by the curve of Figure 31. Design the bolts which fasten the flywheel
to the crankshaft, stating a satisfactory combination of:
1. number of bolts
2. bolt diameter, material, and heat treatment
3. bol't Circle diameter
4. recommended tilghtening torque
PROBLEM 112, FPIGURE 1,, DIESEL ENGINE
a. Descr ibe the construction and operation of the engine.
be. A DViesel" engine -has a 4'": bore and a 6" stroke. When firing, the maximum
cytinkder pressure is 1200 psi. The cylinder head and block are made of
cast` iron, and a copper-asbestos gasket 3/32" thick is used between the
56

MGCHINE DES-IGN THREADED FPASTENERS
head and block. Each of the 3 heads are fastened to the block by 4
stud bolts. Determine a satisfactory combination of:
1. -Bolt diameter and number of threads/inch
2. bolt mater ial and heat treatment
-3. length. bolt threads i-nto block
4.:recommended tightening torque
XV:- POWER SCRE-WS
PROBLEM -113
a. Discuss the desirable and undesirable characteristics of a power screw
as a means'of obtaining linear motion in a machine.,
b. Describe the relative advantages and dis-advantages. of the square,
Acme, and Buttress threads.
c. Considering the power screw to be an inclined plane, show that if the
screw is self-locking, the efficiency can be no more than 50%.
PROBLEM 114, FIGURE 21. C FRAME PRESSa. Describe the construct-ion and operation of the press, including the
power screw in its base.
b. The power screw in- the base of the press is to be capable of exerting
a force of 3000 lbs' and is to have a linear travel of 12 inches.
Establish a satisfactory combination of:
1. -screw diameter and number of threads/ inch.
2. number of independent threads on screw
3. thread form
4. length and outside diameter of nut
5. material and heat treatment of screw and nut
6. length of handle to be used for turning nut

MACHINE DES IGN POWER SCREWS
PROBLEM 1151, PFIGURE 6, SCREW JACK
a. Describe the construction and operation of the jack.
b. A jack similar to that shown is to be used as an adjusting and positioning device in a large conveyor system. The jack will be permanently
installed in the conveyor machinery aind must be capable of raising or
lowering a 4 ton piece of equipment 3 feet in approximately 4 minutes.
Operation of the jack will be infrequent, but to allow remote control,
the jack is to be dr-iven by a-n AC induction motor, with performance as
shown by the curve of. Figure 31 for design D motors. It is estimated
that the efficiency of the worm will be approximately 40%.
Establish a satisfactory combination of:
1. screw diameter and numberof threads/inch
2. number of- indende dent threads
3. thread form
4. material and treatment of screw and nut
5. length of nut
6. worm gear ratio required
7. rated HP and synchronous speed of motor
PROBLEM 116, FIGURE 6, SCREW JACK
a. Describe the construction and operation of the jack.
b. A jack similar to that shown requires a torque of 200 lb-inches applied
to the nut by the worm to raise a given load, and a torque of
120 lb-inches applied to the nut to lower this same load. What is the
efficiency of the screw?
PROBLEM 117, FIGURE 3, POWER STEERING UNIT
a. Descr'ibe the construction and operation of the power steering mechanism.
b. A power screw with a circulating ball nut is to be designed for a power
steering mechanism. The nut is to be capable of exerting a linear force
of 600 lbs when a torque of 80 lb-inches is applied to the steering wheel
<~ ~ ~ ~~~~5

MACHINE DES IGN POWER SCREWS
shaft, and the nut -is to travel " for each complete revolution of the
steering wheel shaft. Establish a satisfactory combination of:
1. screw diameter and number of grooves/inch
2. number of independent grooves
3. ball diameter
4. length of nut
5. material and heat treatment for screw, nut, and balls
XVi - BELTS AND CHAINS
PROBLEM 118
a. Does the following equation correctly describe the relation of the
tensions in a flat belt for all conditions of operation? Discuss
briefly.
1 c 0s5
F -F
2 c
b. Explain why the small pulley of a flat belt drive is often made of wood
or leather, while the large pulley is made of cast iron.
c. Show why a V belt can develop a greater friction force than a flat belt.
d. Explain in words, not equations, the conditions under which a V-flat
drive would perform- as satisfactorily as a regular V belt drive.
PROBLEM 119, FIGURE 28, STRAIGHT PRESS
a. Describe the construction and operation of the press.
b. A; press similar to that shown is to punch holes in parts formed from
steel Plate. The press is to make 40 punches/inute, with each punch
requiring 5000 ft-lbs of energy. The bull gear and pinion will provide
an 8:1 ratio, and the flywheel will be designed so that the speed
variation during a punching cycle is no more than 10% of the maximum
speed. A 1200 rpm AC induction motor is to drive the press through
59

MACHINE:IDES IGN BELTS AND CHAINS
V belts, as shown. Establish a satisfactory: combination of:
1.- belt -size and mnumber of belts
2. sheave diameters (do not design flywheel)3. approximate center distance of sheaves
PROBLEM 120, FIGURE 20, CRUSHER
a. Describe the construct.ion and operation of the crusher.
b. A crusher similar to that shown is to be V-belt driven from a 30 HP,
1200 rpm AC motor; The flywheel is to act as the large V-belt sheave,
and the belt drive is to provide a 5:1 spe
satisfactory' combination of:
1. belt...:siz-e and number, of-belts
-.sheave- diameter-s (do not design flywheel)-3. approximate center distance of sheaves
c. Using the belt size, sheave diameters, and center distance found above,
determine how many additional belts would be needed for a V-flat. drive.
PROBLEM a121, FIGURE 25, SHAPER
a. Describe the construction and operation of the shaner.
b. A shaper similar to that shown is to be V-bel.t driven from a 5 HP,
1200 rpm motor. The motor weighs 170 lbs., has a 12 3/4"' diameter, is
17*" long, nas a Dear ng span of 15", and the center of the sheave is
4" froth the first bearing.
Five size A belts are to be used, with sheave diameters of 5" and 15",
and a center distance of 22". A pivoted motor mounting is to be used.
Decsign -suchd a moun-tihng, and-make a-neat sketch, -to scale, showing the
location of the pivost point, motor location, -ad other significant
dimensions,.
c.. Determine the motor bearing loads due to the belts only.
60

MACHINE DESIGN BELTS AND CHAINS
PROBLEM 122
a. Discuss the relative advantages and dis-advantages of belts, chains, and
gears as means of transmitting power.
b. What consideration dictates the minimum number of teeth in a roller
chain sprocket?
c. Explain why roller chains tend to be noisy when they become worn.
Illustrate the explanation with a neat sketch, and describe how the
cause of the noise can be partially eliminated by the proper shape of
the sprocket teeth.
d. Sketch the rocker pin construction commonly used with silent chains.
Describe the operation of the rocker pins, and discuss the advantages
of this construction.
PROBLEM 123, FIGURE 2, TRANSPORT MACHINE
a. Describe the construction, operation, and use of the transport machine.
b. The transport machine is driven by a 3 HP, 900 rpm AC induction motor.
The enclosed bevel gear speed reducer provides a 6:1 reduction, and has
a 2" diameter output shaft. The roller chain is to provide a 1.5:1
reduction, with a center distance of approximately 30". Establish a
satisfactory combination of:
1. pitch of chain
2. number of strands
3. number of links per strand
4. numbers of teeth in sprockets
XVII - WIRE ROPES
PROBLEM 124
a. Explain why there is no strand of wire in'.: center of most wire ropes.
b. Explain briefly in words, not equations, %ne meaning of the "bending
61

MACHINE DES IGN WIRE ROPES
load" in wire ropes.
c. Derive the equation for the bending load
PROBLEM 125
a. Neatly sketch and label a 4 rope "independent" suspension, as might be
used' on a passenger elevator.
b. Neatly sketch and label a 4 rope "dependent" suspension, as might be
used on an overhead travelling crane.
c. Discuss the need for using rather large safety margins when selecting
wire ropes for hoisting equipment.
PROBLEM 126, FIGURE- 9, SCRAPER HOIST
a. Describe the construction and operation of the scraper hoist.
b. A scraper hoist similar to that shown is to be;caplable of pulling a
2700 l1b load at 200 ft/min,, iwhen the AC induction ~motor is developing
its rated horsepower. Motor characteristics are shown by the curve of
Fiiure 31 for design D motors. Establish a satisfactory combination of:
1. rope adameter ana pattern
2 rope. mater ial
3. hoist drum diameter
c. Select a standard 1200 or 1800 rpm AC induction motor, and establish
-the total gear ratio needed.
PROBLEM 127, FIGURE 30, OVERHEAD CRANE TROLLEY
a. Describe the construction and operation of the crane trolley.
b. An, overhead crane like that shown is to have a hoisting speed of
22 ft/min. when lifting its rated capacity of 20 tons. Maximum lift
is to be 45 feet.
The direct current hoist motor has operating characteristics as shown
by the curve of Fieure 31. The motor should run at aDbroximatelv rated
speed when the crane is lifting its rated capacity. A current control
62

MACHINE DESIGN WIRE ROPES
limits the maximum torque which the motor can develop to 130% of rated
motor torque. Crane motors having ratings of 25 HP at 575 rpm, 35 HP
at 525 rpm, and 50 HP at 500 rpm are available. Establish a satisfactory
combination of:
1. rope diameter and pattern
2. rope material
3. drum and sheave diameters
c.. Select a suitable motor and establish the total reduction gear ratio for
the crane.
XVIII - SPUR GEARS
PROBLEM 128
a. Explain why "conjugate" curves must be used for tooth profiles, rather
than just any curved surfaces which might be arbitrarily selected.
b. Definean.involute curve, and show on a neat sketch how the curve is
developed.
c. State the two most important xeasons why involute curves are used
instead of any other conjugate curves for gear tooth Profiles.
PROBLEM 129
a. By means of a neat sketch and brief explanation, show that when one
involute drives another, the angular velocity ratio is constant. Do
not refer to the pitch point, nor to the "law of gearing", in the
explanat ion.
b. Describe the hobbing operation for cutting gear teeth, and state the
property of the involute curve which makes this possible.
c. What is the purpose of having standard. pitches, pressure angles, and
tooth proportions?
63

MACHINE DESIGN SPUR GEARS
PROBLEM 130, -FIGURE 2, TRANSPORT MACHINE
a. Describe the construction and operation of- the transport machine.
b. The final drive pinions and gears of a transport machine have 20 and
42 teeth respectively. The diametral pitch is 4, the pressure angle is.20~, and the teeth have full depth proportions. Using a compass and
straight edge, make a full scale. sketch showing the following for the
gear and pinion.
11. pitch> circles 5. pressure angle
2. roo*;rcles 6.. length of the path of contact
3, base circles
4. addendum circles
c. Prove on your sketch that if the 20 tooth pinion is cut with a hob, the
teeth will not be undercut.
PROBLEM 131, FIGURE 13, 2 SPEED DIFFERENTIAL
a. Describe the construction and operation of the two speed differential.
b.- A spur pinion and gear in the differential-are to have 14 and 24 teeth
respectively. The, teeth are to be cut with a 5 pitch 200 full depth
hob. The two gears. are to opetate with the theoretically correct center
distance with- 0.007" back1-ash. Neither the pinion nor the gear are to
be undercut. Determine the following for the pinion and gear:
1. outside diameter
2. addendum
3. whole depth
4. circular tooth thickness at the pitch diameter
PROBLEM 132. FIGURE 2. TRANSPORT MACHINE
a. Describe the construction and operation ot tne transport machine.
b.. The final drive pinions-and gears of a transport machine have 20 and-42
teeth respectively. The diametral pitch is 4, the pressure angle is
20~, and the teeth have full depth proportions. The teeth are in contact
64

MACHINE DES IGN SPUR GEARS
at the pitch point, and the pinion torque is 2000 lb-inches. Using a
compass and straight edge, make a full scale sketch showing:
1. pitch and base circles
2. the total force exerted on the driven gear
3. the components of the total force
PROBLEM 133
a. Apply the beam stress equation:
M c
S = to a gear tooth, and derive the Lewis equation:
PP
S
f Y
b. What is the significance of the parabola commonly used in the derivation
of the Lewis equation?
c. Discuss the probable accuracy of the Lewis equation as a means of
determining the stress which actually occurs in a gear tooth.
PROBLEM 134
a What is the visual evidence of gear tooth failure by bending fatigue and
of failure by surface fatigue?
b. What surface treatments could be used to increase the bending fatigue
life and surface fatigue life of gear teeth?
PROBLEM 135, FIGURE 30, OVERHEAD CRANE TROLLEY
a. Describe the construction and operation of the crane.
b. An overhead crane has a rated capacity of 20 tons, which it hoists at
22 ft/min. when the DC motor is developing its rated horsepower. The
motor characteristics are shown on the curve of Figure 31. A current
relay limits the maximum motor torque to 130% of its rated torque.
The rope drum diameter is 30", and the sheave diameters are 20". The
rope drum is driven, by the DC motor through several sets of enclosed
65

MACH INE DES IGN.SPUR GEARS
spur gears, The final pair of spur gears are to provide a 3:1 ratio,
with the gear keyed to the 5" diameter shaft of the rope drum, and the
pinion keyed to a 3.5" diameter shaft.
Design the teeth for the final pair of spur gears, tabulating a
satisfactory combination of:
1. pitch diameters 5. pressure angle
2. diametral pitch 6. depth of teeth
3. numbers of teeth 7. required accuracy of manufacture
4. face width 8. material and hardness
c. Make a neatly dimensioned sketch, to scale, showing'the cross section
of your gear and pinion.
PROBLEM 136, FIGURE 28* STRAIGHT PRESS
a. Describe the construction and operation of the press.
b. In a press like that shown, maximum crank torque occurs when the crank
is 20~ before bottom center, and a force of 10 tons is being exerted.
The crank requires 1.5 seconds to make one complete revolution. The
stroke of the press is 12", and the length of the Pitman rod is 28".
The bull gear and pinion are to provide an 8:1 ratio. Design the teeth
for these gears, stating a satisfactory combination of1. pitch diameters 5. pressure angle
2. diametral pitch 6. depth of teeth
3. numbers of teeth 7. required accuracy of manufacture
4. face width 8. material -and hardness
c. Make a neatly dimensioned sketch, to scale, showing the cross section
of your gear and pinion.
PROBLEM 137, FIGURE 9, SCRAPER HOIST
a. Describe the construction and operation of the scraper hoist.
b. A scraper hoist is to be powered by a 20 HP, 1800 rpm AC induction motor
with characteristics as shown by the curve of Figure 31 for design D
66

MACHINE DES IGN SPUR GEARS
motors. The double reduction gears next to the motor provide a total
ratio of 5:1. The shorter rope drum has a 15" diameter, and is to be
capable of pulling a 4" wire rope at approximately 193 ft/min. when
the motor is developing its rated horsepower.
Considering the motor to operate at its rated horsepower most of the time,
design the teeth for the planetary gears which drive the shorter drum.
Use the Buckingham equations to check the load carrying capacity, and
tabulate a satisfactory combination of:
1. number of planets
2. pitch diameters of sun, planet, and ring gears
3. diametral pitch
4. numbers of teeth
5. pressure angle and tooth depth
6. face width
7. required accuracy of manufacture
8. material and hardness
XIX - HELICAL GEARS
PROBLEM 138
a. State the comparative advantages and dis-advantages of helical gears
and straight spur gears.
b. Show that for helical gears cut with a standard pitch hob the following
relationship is correct:
NO teeth = (pitch diameter) x (diametral pitch) x (cosine of helix angle)
c. Using a 3 dimension sketch, derive an equation relating the pressure
angle in a plane normal to the teeth, the pressure angle in the plane
of rotation, and the helix angle.
67

MACHIN:E DES IGN HELICAL GEARS
PROBLEM: 139, FIGURE 9, SCRAPER HOIST
a. Describe the construction and operation of the scraper hoist.
b. The planetary spur gears which drive thi short rope drum are to be
replaced with helical gears. The original planetary gear speed ratio
of 5:1: is to be maintained, and the helical sun and planet gears are
to be cut with the. same hob with which the spur gears were cut. The
carrier, ring gear mountings, etc., are to be unchanged, The spur sun
gear has 22 teeth, 6 pitch, 200 pressure angle.
Determine a satisfactory combination of the following for the new suh,
planet, and ring gears:
1. pitch diameters
2. numbers of teeth
3. helix angle and hand
PROBLEM 140, FIGURE 7. HELICAL GEAR.SPEED REDUCER
a. Describe the construction and use of the speed reducer.
b. A helical gear speed reducer similar to that shown is to be capable of
transmitting 50 HP continuously from a 1750 rpm driving motor, and is
to provide a 3.5:1 reduction.
Using the Buckingham equations to calculate the load carrying capacity,
design the helical gear teeth. Tabulate a satisfactory combination of:
1. pitch diameters 6. tooth depth
2. diametral pitch 7. face width
3. numbers of teeth 8. required accuracy of manufacture
4.- helix angle and hand 9. material and hardness
5. pressure angle
PROBLEM 141, FIGURE 10,. MARINE REDUCTION AND REVERSE GEAR
a. Describe the construction and operation of the reverse gear.
b. A reduction and reverse gear similar to that shown is to be used with
a Diesel engine which performs as shown by the curve of Figure 31, and

MACHINE DESIGN HELICAL GEARS:
is to provide a 1.5:1 ratio both forward and reverse. Using the
Buckingham equations to calculate the load carrying capacity, design
the helical teeth for the forward ratio only. Tabulate a satisfactory
combination of:
1. pitch diameters 6. tooth depth
2. diametral pitch 7.- face width
3. numbers of teeth 8. required accuracy of manufacture
4. helix angle and hand 9. material and hardness
5. pressure angle
c. If the gears in the reverse ratio are to have the same pitch and helix
angle as those in the forward ratio, would it be satisfactory to use
the same numbers of teeth in the reverse gears as in the forward gears?
Explain br iefly.
PROBLEM 142. FIGURE 7. HELICAL GEAR SPEED REDUCER
a. Describe the construction and use of the speed reducer.
b. A speed reducer which is exactly 5 times the size shown, has tee th
a 200 pressure angle and a -250 helix angle. The motor rotates at 1160
rpm and develoos - 20 HP.
Determine the total force -which the pinion teeth exert on the gear
teeth, the 3 components of this force, and the bearing reactions due
to these components. Show the forces, components, and reactions for
both the gear and- pinion on neatly labelled 3 dimension sketches.
PROBLEM- 143, FIGURE 8, CLUTCH AND TRANSMISSION
a. Make a schematic sketch of the transmission and describe with reasonable
detail how it operates to provide a neutral. 3 sDeeds forward. and a
reverse.
b. The sliding gear has 28 teeth, 7 pitch, and 230 helix angle. The pitch
diameter of the spline on-which it slides is 15". Determine the helix
angle required for the- spline teeth so that the thrust on the helical
69

MACHINE DES IGN HELICAL GEARS
gear teeth will not move the sliding gear axially along the spline
teeth, and whether the gear teeth and spline teeth should have the same
or opposite hand helices.
PROBLEM 144, FIGURE 8, CLUTCH AND TRANSMISSION
a. Make a schematic sketch and describe the operation of the transmission.
b. The transmission is to provide a total ratio of 1.61:1 when in second
gear. The. countershaft gears used when the transmission is in second
gear are to be designed so that the resulting axial thrust on the
countershaft bearings is as near to zero as reasonably possible. Using
a pitch of 7, and a 3.00" center distance, determine a satisfactory
combination of pitch diameters and helix angles for the 4 gears used
when in second gear. State whether the 2 gears on the countershaft
should have the same or opposite hand helices.
c. To obtain lengthwise dimensions, such as the distances from a gear to
its bearings, consider the drawing shown to be 2/3 of the actual size
of the transmission. The engine develops a torque of 200 lb-ft at
2100 rpm when the transmission is in second gear. Using the numbers
of teeth, helix angles, and diameters found in part b, make a complete
force analysis of the countershaft assembly when in second gear. Make
a 3 dimension sketch showing the normal forces at the teeth, the components of the normal forces, and the housing reactions due to each of
these components. Label each vector and show magnitude and direction.
XX - BEVEL GEARS
PROBLEM 145
a. A straight tooth bevel gear and pinion provide a 4:1 ratio and have
perpendicular axes. Could this same pinion be used with a smaller gear
in another installation with perpendicular axes to provide a 3:1 ratio?
Explain briefly.
b. Why must bevel gear assemblies be constructed so that the pdsition of the
gear and pinion can be adjusted lengthwise along their shafts at assembly?
70

MACHINE DESIGN BEVEL GEARS
PROBLEM 146, FIGURE 12, BEVEL GEAR SPEED REDUCER
D. Describe, the construction and use- of the speed reducer.
b. Explain how the position of the gear and pinion are adjusted axially,
and why this is necessary.
c. A reducer similar to that shown is to be capable of transmitting 20 HP
continuously from a 900 rpm motor, and is to provide a 4:1 reduction.
Design the straight bevel gear teeth for the speed reducer, stating a
satisfactory combination of:
1. pitch diameters 5.. aaaenaum and dedendum
2. diametral pitch 6. face width
3. numbers of teeth 7. material andi- hardness
4. pressure: angle
PROBLEM 147. FIGURE 12, BEVEL GEAR SPEED,REDUCER.
ai Describe the construction and use of the speed reducer.
b. Straight tooth bevel gears with a 200 pressure angle are to be used in
a speed reducer similar to that shown. The gears are to transmit 20 HP
at 1160 rpm of the bevel pinion. The figure shown is exactly ~S of the
actual size of the speed reducer.
Determine the magnitude - of the normal force on the teeth, the three
components of this nortmal force, and the reactions due to each of these
components on the bearings of the gear and pinion. Make a neat, 3
dimension sketch showuing -the location and direction of the for-ces,
components, and reactions.
PROBLEM 148. FIGURE 12. BEVEL GEAR SPEED REDUCER
a. Describe the construction and use of the speed reducer.
b. Spiral tooth bevel gears with a 150 spiral angle and a 20~ pressure
angle are to be used in a speed reducer similar to that shown. The
pinion has a right hand spiral, and the gears are to transmit 20 HP at
1160 rpm of the pinion. The figure shown is exactlyj of the actual
71

MACHIN DES IGN BEVEL GEARS
size of the speed reducer.
Determine the magnitude of the normal force; on the teeth,: the three
components of this normal force, and the reactions due to each of these
components on the-bearings of the gear and pinion. Make a neat, 3
dimension sketch showing the location and direction of the forces,
components, and- reactions.
PROBLEM 149, FIGURE 4., REAR AXLE
a. Describe the construction and oDeration of the rear axle assembly,
including the action of the differential when the automobile is traveling straight ahead, and when the automobile is turning a corner.
b. Explain why, when the automobile is stuck with one rear wheel on ice
and the other wheel on -dry pavement, the wheel on the ice spins while
the wheel on the pavement does not turn. Show any analysis necessary
to prove your answer is correct.
PROBLEM 150, FIGURE 4, REAR AXLE
a. Describe the construction and operation of the rear axle assembly,
including the action of the differential when the automobile is traveling straight ahead, and when the automobile is turning a corner.
~A rear axle simiilar to thatt shown is to be Used with the V-8 engine
of Figure 11,- and a clutch- a:nd —'transm ission of Figure 8, in a minodern
American passenger automobile. The horsepower developed by the engine
is shown on the ourve-of FPigure 31, while the'horsepower required to
drive the automobile on level ground -and up a 35% grade are shown by
the curves of Figure 32. Estimating the overall efficiency of the
transmission, differential, etc.. to be about 85%, determine the
following:
I, the reduction ratio needed at the rear axle to obtain the maximum
possible speed' of the vehicle on level ground.
2. the transmission ratio needed to -obtain the maximum possible speed
of the vehicle when climbing a 35% grade in low gear.
72

MACHINE DES IGN BEVEL GEARS:
c. The above -automobile is stuck with one rear wheel on ice, the other on
pavement. The coefficient of tire friction on ice is about 0.10, while
on:-pavement it is apr-oximately 0.70. With the transmission in low
gear, and the engine throttle partially open, the engine turns at 2000
rpm. The wheel on the ice slips as it rotates, but the automobile does
not move-. Approximately what horsepower is the engine developing?
PROBLEM 151, FIGURE 13, TWO SPEED DIFFERENTIAL
a. Describe the construction and operation of the two speed differential.
b. Discuss the relative advantages and dis-advantages of spiral bevel gears
and hypoid bevel gears, when used in the rear axle of passenger automobiles and trucks.
xxI - W(RM GEARS
PROBLEM- 152
a.- State — the most important advantages and dis-advantages of worm gearing
compared to other common types of gearing.
b. Considering the worm and gear to be a simple inclined plane, show that
if a worm and gear are self locking, the efficiency or the worm and
gear can be no more than 50o%.
c. Explain why bronze gears are commonly used with hardened steel worms,
rather than having both thne worm and gear made of hardened steel.
d.' Explain how the position of the gear is adjusted axially in the Worm
Gear Speed Reducer, Pigure 29, and why this adjustment is necessary,
PROBLEM 153. FIGURE 23. CAPSTAN WINCH
a. Describe-the construction and'use of the capstan winch.
b. The- capstan: winch shown is to be capable of pulling 1500 lbs at40 ft/min. with either or both drums. Service will be intermittent.
73

MACHINE DESIGN WORM GEARS
The rope drums are to. have 8" diameters, and, are to have' clockwise
rotation when viewed from- the right hand end. The winch is to be
poweredby an 875 rpm-AC motor having clockwise rotation when viewed
from its shaft; end.
Design the worm and gear stating a satisfactory combination of:
1. pitch diameters 6. lead angle and hand
2. linear pitch 7. helix angle and hand
3. number of threads in worm,8. face width of gear
4. number of teeth in gear 9. material and hardness of worm and gear
5.- pressure angle
c. Determine the horsepower rating of the motor required to drive the winch.
PROBLEM 154, FIGURE 23, CAPSTAN WINCH
a. Describe the construction and use of the capstan winch.
b. A winch similar to that shown is to be capable of pulling 2500 lbs at
20 ft/min. with either or both drums. The worm has 2 threads, and the
gear has -60 teeth. The winch is ten times the size shown on the drawing. Determine the normal forte and friction force at the teeth, the
components of these forces, and the bearing reactions due to each of
these components. Make a neat, 3 dimension sketch showing these forces,
components, and reactions.
c. Are the worm and gear self-locking? Explain briefly and show calculations.
PROBLEM 155, FIGURE 29, WORM GEAR SPEED REDUCER
a. Describe the -construction and use of the worm gear speed reducer.
b. A speed reducer similar to that shown is to be capable of transmitting
25 HP continuously from a 1750 rpm driving motor, and is to provide a
15:1 reduction. The input and output shafts must both rotate clockwise
as viewed from their outer ends. Determine a satisfactory combination
of:
74

MACHZINE- DES-IGN WORM GEARS
1. pitch diameters 6. lead angle and hand
2, linear pitch 7. helix angle and hand
3. number of treads in worm 8. face width of gear
4. number of teeth -in gear 9. material and hardness of worm and gear
5. pressure angle
c.* Estimate the external surface area which will be present on the housing
which encloses the above worm and gear, approximate the temperature rise
above ambient with continuous operation, and state whether or not this
temperature rise would be permissible.
PROBLEM 156, FIGURE 13, TWO SPEED DIFFERENTIAL
a. Describe the construction and operation of-the two speed differential.
b. The differential is to be re-designed to replace the spiral bevel pinior
and gear with a worm and gear. Make 2 neat, complete sketches of the
differential with the worm and gear, sectioned to show the method of
supporting both the' worm and the gear.
c. If a worm and gear were to be used in a differential, would it be best
to have a worm with a rather large number of threads, say 6 or 8, or
with a smaller number of threads, such as 2 or 3? Discuss briefly
and explain clearly.
XX I I COUPLINGS AND CLUTCHES
PROBLEM 157
a. Why are flexible couplings more commonly used than rigid couplings?
b. A flanged coupling is to be designed to fit a 40 HP, 1770 rpm AC motor.
The motor shaft diameter is 2". Show your design on a neat sketch,
drawn to scale and completely dimensioned,.and specify the necessary
mater ials.
75

MACHINE DESIGN COUPLINGS AND CLUTCHES
PROBLEM 158, FIGURE —14, AUTOMATIC TRANSMISSION
a. Describe the operation of the over-running clutch in the torque converter
of the- -transmission,
b.' A torque converter similar to that shown has an outside fluid diameter
of 12". The engine delivers a maximum torque of 150 lb-ft and the
converter provides a 2.3:1 torque ratio at stall. Design a roller type
of over-running clutch for the stator of this torque converter, showing
the following on a neat sketch, drawn to scale:
1. roller diameter
2. number of -rollers
3 —. inner and outer: race dimensions
4. ramp angle
5. material and heat treatment
PROBLEM - 159. FIGURE 5, BEVEL:GEAR -REVERSING UNIT
a. Describe the construction and operation of the bevel gear reversing unit.
b. Make a neat sketch of the clutch engaging mechanism, and explain how it,
operates.
c. Explain why such an elaborate mechanism is required with the disk clutch.
PROBLEM 160, FIGURE 5, BEVEL GEAR REVERSING UNIT
a. Describe the construction and operation of the bevel gear reversing unit.
b. The reversing unit is to be supplied with a 10 HP,' 1200 rpm AC induction
motor, which pertormsa as snown ty the curve of Figure 31 for B design
motors. The bevel gears provide a 3:1- reduction, and it is anticipated
-that the clutches will be engaged and dis-engaged frequently. Design
the disk clutch, stating a satisfactory combination of:
1. inside and outside diameters of the disks
-2. disk sturface materials
3. number of inner and outer disks
4. force required at the disks to engage the clutch
76

MACHKINE DES IGN COUPLINGS AND CLUTCHES
c. Design an engaging mechanism so this clutch -cazr-be operated manually.
Make a neat sketch showing the handle,r fork, rocker linkage,- etc., with
all important dimensions. Show force:and motion analysis clearly.
PROBLEM 161, FIGURE 28, STRAIGHT PRESS
a. Describe the construction and operation of' the press.
b. A press is 10 times the size shown in the drawing. Maximum crank torque
occurs when the crank is 300 oerore ceaa center, and is exerting a
force of 25 tons. The motor and flywheel run continuously, and a
triction disk clutch at the flywheel engages and dis-engages the jackshaft as the operator wishes. The motor runs at approximately 1170 rpm
when the clutch is disengaged.
Design a friction clutch for the press, stating a'satisfactory combination. of.
1. inside and outside diameters of the disks
2. disk sur-face materials
3-. number of inner:; and- outer disks
4. force required at the disks to engage the clutch
PROBLEM 162. FIGURE 8-, CLUTCH AND TRANSMISSION
a-. Describe the constr-uction and operation of this clutch,: including the
means of engaging and disengaging.
b. Describe the features commonly found in.an automobile clutch which would
not be commonly found in clutches used with industrial machinery.
c. A' clutch and transmission similar to that shown are to be used with the
engine of Figure 11, which performs as shown by the curve of Figure 31.
Design the clutch. stating a satisfactory combination of:
1. inside and outside -diameters ot- the disks
2, disk sur face mater ials
3. sp'gringfo0rce -required

MACHINE DES IGN COUPLINGS- AND CLUTCHES
PROBLEM 163, FIGURE 14, AJTC4ATIC -TRANSMISSION
- a. Describe the operation of the transmission during three speeds forward
— and one speed in reverse, including the method' of applying and releasing the disk clutches.
b. The transmission is to be used with an-engine which pertorms as shown
by the curve of Figure 31. The torque converter provides a maximum.
torque ratio of 2:1. To provide sufficient space for other parts of
the transmission, the inside diameter of the disks of the front clutch
can be no smaller'than 3L". Design the front clutch,, stating a satisfactory combination' of:
1. inside and outside diameters of the disks
2. number of inner and outer disks
3. disk mater ials
4. force required to apply clutch
PROBLEM 164. FIGURE 10, MARYNE REDUCTION AND REVERSE GEAR
a. Describe the operation of the marine reduction and reverse gear.
b. The marine gear is to be used:.with a Diesel engine which performs as
shown by the curve of Figure 31. Available space limits the outside
diameter of: the clutch disks -to 10: maximum. Design the disk clutch,
stating a satisfactory combination of:
1. inside and outside diameters of the disks
2, number of inner and outer disks
3. disk material
4.1 force required to apply the clutch.
PROBLEM 165, FIGURE 16, CONE CLUTCH
a. S1?ate the relative advantages and dis-advantages of cone and disk
clutches.
b. A cone clutch is to be engaged with both parts stationary. Derive the
equation for the force required to engage the clutch in terms of the
normal force, the friction coefficient, and the cone angle.
78

MACHINE DESIGN COUPLINGS AND CLUTCHES
c. Is the engaging force found by the equation derived above satisfactory
if the clutch is engaged when one part is rotating and the other part
stationary? Explain briefly.
PROBLEM 166, FIGURE 16, CONE CLUTCH
a. Show that a cone clutch will hold itself in engagement if the tangent of
the cone angle is less than the coefficient of friction.
b. A cone clutch is to transmit 200 lb-ft of torque at 200 rpm, and is to
hold itself in engagement. Design the clutch, stating a satisfactorycombination of:
1. mean diameter of cone
2. cone face width
3. cone angle
4. friction surface materials
5. force required to apply cl'utch
XXIII - HYDRAULIC COUPLINGS AND TORQUE CONVERTERS
PROBLEM 167
a. Explain in words, not -equations, the principle of operation of a
hydr aul ic coupl ing.
b. Establish the relationship of the input torque to the output torque of
a hydraulic coupling, and derive an equation for the efficiency of the
coupling in terms of the speed ratio.
c. Discuss the advantages and dis-advantages of a hydraulic coupling as
a means of transmitting power.
PROBLEM 168, FIGURE 10, MARINE REDUCTION AND REVERSE GEAR
a. Describe the operation and use of the marine gear,
b. The marine gear is to be used with a Diesel engine similar to that
shown in Figure 1, except with more cylinders. Typical engine
79

MACHINE DES IGN HYDRAULIC COUPLINGS AND TCRQUE CONVERTERS
performance with wide open throttle is shown by the curve of Figure
31. Engines capable of developing horsepowers of 200, 250, 300, and
350, all at 1800 rpm, are available.
The curves of Figure 32 show the performance of a 15" hydraulic coupling
of the type used with the marine gear. Figure 32 also shows the power
required to drive the propeller of a boat.
A boat is to be built to cruise with a propeller speed of 300 rpm when
the engine develops 80% of its horsepower rating as mentioned above,
and coupling slip is 3%.
Determine a satisfactory combination of:
1. size of Diesel engine to be used
2. diameter of geometrically similar coupling to be used
3. gear ratio required
c. Would it be more economical to obtain the 80% of rated horsepower by
operating the engine at part throttle or by operating at full throttle
at a lower speed? Explain briefly.
PROBLEM 169
a. Explain the fundamental difference in construction of the hydraulic
coupling and the hydraulic torque converter, and prove that this difference is necessary.
b. By means of a neat sketch and brief explanation, show how the converter
increases torque, and why the efficiency decreases rapidly as the speed
of the turbine approaches the speed of the pump.
c. Discuss the desirability of mounting the stator on a one-way clutch in
a converter to be used in a passenger automobile, a converter to be used
in a crawler tractor, and a converter to be used in a city bus.
PROBLEM 170, FIGURE 14, AUTOMATIC TRANSMISSION
a. Describe the construction and operation of the torque converter.
b. The 12" converter used with the automatic transmission performs as
80

MACHINE DESIGN HYDRAULIC COUPLINGS AND TORQUE CONVERTERS
shown by the curves of Figure 32. Using 8-" x 11" graph paper, neatly
plot the following curves for this same converter:
1. input torque to- converter, lb-ft (ordinate), vs. input speed of
converter, rpm (abscissa), for a 1.5:1 torque ratio.:2. output speed of converter, rpm (ordinate), vs. input speed of
converter, rpm (abscissa), for a 1.5:1 torque ratio.
Both curves are to be plotted on' the same sheet with a common abscissa.
The torque scale is to go to 300 lb-f t, the speed scales to 3000 rpm.
c. Under certain operating conditions of a modern American automobile, the
engine runs at 2000 rpm and the above converter develops a 1.5:1 torque
ratio. Determine the horsepower the engine is developing, and the
approximate speed of the vehicle in miles per hour.
XXIV - BRAKES
PROBLEM 171,'FIGURE 15, THRUSTOR BRAKE
a. Describe the construction and operation of the brake.
b. A brake similar to that shown is to hold a torque of 200 lb-ft. Design
this brake, stating a Satisfactory combination of-the following, and
make a neat sketch, drawn to scale, of your design.
1. drum diameter and width
2. drum material
3. shoe lining mater ial
4. shoe angle
5. lengths of levers and position of all pivots (show dimensions on
sketch)
6. spring force required to applv brake
7.- thrustor force required to-release brake
8i

MACHINE DES IGN; BRAKES
PROBLEM 172, FIGURE 30, OVERHEAD CRANE TROLLEY
a. Describe the construction and operation of the crane.
b. A crane similar to that shown is to have a capacity of 15 tons, a rope
drum diameter of 20", and a 40:1 gear reduction between the DC motor and
the rope drum. The lowering speed of the 15 ton load is 20 ft/min.,
held constant by regenerative braking of the DC motor.
The external shoe brake, which is applied by a spring and released
electrically, is -to be capable of bringing the load to a stop in 6
inches in case of motor failure while lowering. Design the shoe brake,
stating a satisfactory combination of the following, and make a neat
sketch, drawn to scale, of your design:
1. drum diameter and width
2. dr um mat erial
3. shoe lining material
4. shoe angle
5. lengths of levers and position of all pivots (show dimension son
sketch)
6. spring force required to apply brake
7. thrustor force required to release brake
PROBLEM 173, FIGURE 19, EXTERNAL SHOE BRAKE
a. Describe the construction and operation of the brake.
b. A brake similar to that shown is to be designed for use on a passenger
elevator. Because of the safety problem involved, the brake drum and
elevator rope drum are to be fastened together and rotate on the same
shaft. The maximum gross load of the elevator is to be'3000 lbs., and
the lowering speed is to be 240 ft/min. The brake is to be capable of
stopping the elevator in the shortest distance possible without causing
discomfort to the passengers. Make a neat sketch, drawn to scale, of
your brake design, and tabulate the following:
1. drum diameter and width
2. drum material
82

MACHINE DESIGN BRAKES
3. shoe lining material
4. shoe angle
5. shoe pivot location for minimum wear (show on sketch)
6. spring force required to apply brake
7. lever lengths and pivot locations (show on sketch)
PROBLEM 174, FIGURE 17, INTERNAL SHOE BRAKE
a. Describe the construction and operation of the brake.
b. The brake shown is used on the front wheels of a passenger automobile.
Would it be desirable to have brakes of this same construction on all
4 wheels? Explain briefly.
c. Explain briefly how the construction of the brake shown differs from.
that of the most popular brake construction in use today.
PROBLEM 175, FIGURE 17, INTERNAL SHOE BRAKE
a. Describe the construction and operation of the brake.
b. A modern American automobile is to have front wheel brakes like that
shown. For calculating purposes, it can be considered that during a
fast stop, approximately 60% of the total weight of the loaded vehicle
will be equally divided between the 2 front wheels. The brakes are to
be capable of stopping the vehicle from 60 mph in the shortest possible
distance without skidding the wheels.
Design the front wheel brakes, stating a satsifactory combination of
the following, and make a neat sketch, drawn to scale, of your design:
1. drum diameter and material
2. shoe lining material
3. shoe angle and shoe width
4. force required to apply brake
5. location of pivots (show on sketch)
83

MACHINE DES IGN BRAKES
PROBLEM 176,'FIGURE 9. SCRAPER HOIST
a. Describe the construction and operation of the scraper hoist.
-b. A scraper hoist.is to- be driven by an 1800 rpm AC induction motor,
design D with characteristics as shown in Figure 31. The hoist is to
be capable of pulling 4000 lbs at 140 ft/min. when the motor is developing its rated horsepower. The rope drum diameter is 15", the planetary
gear provides a 5:1 speed reduction, and the pitch diameter of'the
planetary ring gear is 20"'. The band brake which holds the ring gearis to be designed so that it can be manually operated at an average rate
of about- once per minute by an operator- standing at the hoist.
Make a neat sketch, drawn to scale, of your brake design, using the
construction shown in the figure. State a satisfactory combination of
-the following:
1. brake drum diameter
2. material, thickness, and width of band
3. material, thickness, and width of band lining
4. angle of contact (show on sketch)
5. lever and handle lengths, pivot locations, etc., (show on sketch)
6. force required on handle- to apply the brake
c. With the brake construction shown, should the pulling rope come onto
the drum at the top -of the drum or at the bottom of the drum?
Explain briefly.
PROBLEM 177, FIGURE 14, AUTOMATIC TRANSMISSION
a. Describe the operation of- the transmission during 3 speeds forward and
one reverse, including the methods of applying and releasing the band
brake s.
b. The planetary gears of the transmission shown provide the following
ratios:
first gear ratio = 2.4444
second gear ratio = 1.4815
84

MACHINE DESIGN BRAKES
third gear ratio-= 1.0000
reverse ratio = 2.0000
The torque converter provides a 2:1 torque ratio at stall. The transmission is used with an engine having the performance shown in Figure 31.
Space available limits the rear brake drum diameter to 5-1-" minimum and
6~2" maximum. Design the rear brake, stating a satisfactory combination
of:
1. druni diameter 5. band lining material
2. drum material 6. band width
3. band material 7. force required at band to apply brake
4. contact angle
c. Considering this transmission to be used in a conventional American
automobile, is the proper end of the band anchored and the proper end
actuated? Explain briefly.
PROBLEM 178
a. List the comparative advantages and dis-advantages of external shoe
brakes, internal shoe brakes, band brakes, and disk brakes.
b. The scraper hoist of Figure 9. uses a planetary gear with a band brake
as a means of engaging-and disengaging the rope drums. List the
advantages and dis-advantages of planetary gearing as an engaging
device as compared to disk or Cone clutches.
PROBLEM 179, FIGURE 18, DISK'BRAKE
a. Describe the construction and operation of the disk brake.
b. A brake of the type shown is to be used to control the speed of a
processing machine. To do this, the brake will operate on a regular
cycle in which the brake is applied for 4 seconds of every minute.
During this 4 seconds the brake must absorb 10,000 ft-lbs of energy
with an average speed of 200 rpm for the rotating disks.
Design the brake to perform as described without over heating. Tabulate
a satisfactory combination otf
85

MACHINE DESIGN BRAKES
1. number of inner and outer disks
2.' thickness of inner and outer disks
3. inside and outside diameters of disks
4. disk surface materials
5. force required to apply brake
6. approximate operating temperature of disks
XXV - SHAFTS
PROBLEM 180
a. Explain why machine shafts are seldom made with a constant diameter from
end- to end.
b. State the reason for each change of diameter on the output shaft of the
Bevel Gear Speed Reducer, -Figure 12.
c. What range of carbon content and Brinell hardness are best suited for
steel shafts which carry heavy loads?
IROBLEM 181, FIGURE 7, HELICAL GEAR SPEED REDUCER
a. Discuss the problem of accurately determining the loads which the input
shaft and output shaft must carry if the reducer shown is to be sold
on the open market.
b. Discuss the effects of combined torsion and bending on the strength of
a shaft which has shoulders and keyways.
c. Considering shaft strength, smooth operation of the gear teeth, and the
problems of manufacturing, discuss the desirability of having the.gear
be either a press fit or a clearance fit on the output shaft. What
type of fit would you recommend?
PROBLEM 182
Describe the type of loading, such as bending, torsion, etc., which the
following shafts carry, neglecting the weight of the parts:
86

MACHINE DESIGN. SHAFTS
1. The shaft which connects the torque converter turbine to the front
clutch in the Automatic Transmission, Figure 14.
2. The shaft which holds the 4 rope sheaves at the hook on the Overhead
Crane Trolley, Figure 30.
3. The countershaft which supports the cluster gear of the Transmission,
Figure 8.
4. The countershaft of the Marine Reduction and Reverse Gear, Figure 10.
5. The input shaft of the Bevel Gear Speed Reducer, Figure 12.
6. The shaft of the -rear sun gear in the Automatic Transmission,
Figure 14.
PROBLEM 183, FIGURE 14, AUTOMATIC TRANSMISSION
a. Describe the construction and operation of the transmission.
b. The transmission shown is to be used with an engine having the performance shown in Figure 31. The performance of the torque converter is
shown in Figure 32.
Design the shaft which connects the turbine of the torque converter to
the first disk clutch, stating a satisfactory combination of:
1. outside and inside shaft diameters
2. shaft material and heat treatment
3. length of spline at the converter turbine
PROBLEM 184, FIGURE 14, AUTOMATIC TRANSMISSION
a. Describe the construction and operation of the transmission.
b. The transmission shown is to be used with an engine having the performance shown in Figure 31. The performance of the torque converter is
shown in Figure 32. The rear sun gear has 27 teeth, a normal pitch of
14, with a 200 pressure angle and a 200 helix angle.
Design the shaft for the rear sun gear, stating a satisfactory combination of:
1. inside and outside diameters
2. material and heat treatment
87

MACHINE DESIGN SHAFTS
PROBLEM 185, FIGURE 30,'OVERHEAD CRANE TROLLEY
a. Describe the iconstruction and use of the crane.
b. The shaft which holds the 4 rope sheaves at the hook is to be designed
for a crane having a rated capacity of 10 tons. The crane is to be
driven by a DC motor having the performance shown in Figure 31, A
controller limits the motor torque to the maximum shown. Dimensions
along the shaft can be found by considering the actual crane to be
8 times the size shown. Needle bearings inside each sheave, with the
needles rolling directly on the shaft, allow the sheaves to rotate on
the shaft. Determin-e a satisfactory combination of:
i. shaft diameter
2. shaft material and heat treatment
PROBLEM 186, FIGURE 7, HELICAL GEAR SPEED REDUCER
A speed reducer is to be driven by a 25 HP, AC induction motor having a
synchronous speed of 1800 rpm. The performance of the motor corresponds
to that of design B shown in Figure 31.
The reducer is to provide a 3:1 reduction. The pinion has 20 teeth, a
normal pitch of 8, a 200 pressure6 angle and a 230 right hand helix angle.
The output shaft is to be capable of carrying a 2000 lb overhung load to
allow for possible belt loads, chain pull, etc. To obtain trouble free
operation of the gears, it is desirable that the output shaft deflect no
more than about 0.002" at the center of the gear when operating at rated
capacity. Linear dimensions can be obtained by considering the actual
machine to be- 6 times the size shown in the figure.
Design the output shaft, and make a neat sketch, to scale, of your design.
Show all diameters, fillet radii, and keyway dimensions. State the material
and heat treatment to be, used.
PROBLEM 187, FIGURE 12, BEVEL GEAR SPEED REDUCER
A speed reducer 4 times the size shown is to be used with a 50 HP, AC
induction motor having a synchronous speed of 1800 rpm. The performance of
the motor corresponds to that of design B shown in Figure 31.
88

MACHINE DESIGN; SHAFTS
The output shaft of the reducer is to be capable of holding a 4000 lb
overhung-load to allow for belt tensions, chain pull, etc. To obtain
smooth operation of the bevel gears, the shaft deflection at the bevel
gear should be no more than about 0.002" when operating at its rated
capacity.
Design the output shaft, and make a neat sketch, to scale, of your design.
Show all diameters, fill-et radii, and keyway dimensions, and state the
material and heat treatment to be used.
PROBLEM 188, FIGURE 5, BEVEL GEAR REVERSING UN-IT
a. Describe the construction and operation of the reversing unit.
b. A reversing unit 3 times the size of that shown is to be driven by a
20 HP, AC induction motor having a synchronous speed of 1200 rpm. The
performance of the motor corresponds to that of design B shown in
Figur e 31.
The bevel pinion has a 200 pressure angle and a 150 right hand spiral
angle. This unit is to be produced and sold on the open market.
Design the output shaft, establishing a satisfactory combination of
diameters, fillet radii, thread dimensions, and keyway dimensions.
Make a neat sketch, to scale, of your design, show all dimensions, and
specify a material and heat treatment.
XXVI - SLIDING BEARINGS
PROBLEM 189
a. Briefly describe the mechanics of thick film lubrication.
b. What is the most important property of the lubricating oil so far as
thick film lubrication is concerned?
c. Make a neat sketch showing typical pressure distribution in a bearing
with thick film lubrication.
89

MACH INE DES IGN SLID ING BEAR INGS
d. What 4 -factors most influence the formation and maintenance of the
thick film?
PROBLEM 190
a. What are the. most important physical characteristics of a good bearing
material?
b. Why is the material from which the bearing is made of any concern when
the lubrication is such that a film of oil separates the shaft from the
bearing?
c. Sketch.and describe -how grooves might be put-in the bearing surface to
improve a bearing with thick film lubrication, and a bearing with
grease lubrication.
PROBLEM 191, FIGURE 2, TRANSPORT MACHINE
a. Briefly describe the operation and use of the transport machine.
b. An actual machine is exactly 5 times the size shown, and is driven by
a 3 HP, 900 rpm AC induction motor. The idler shaft which carries the
large chain sprocket and the small pinion, rotates at 75 rpm and is
mounted in 2 sliding. bearings as shown. Design these bearings, stating
a satisfactory combination of:
-1. bearing diameter and length
2. bearing mater ial3. lubricant to be used
4. desired clearance between shaft and bearings
PROBLEM 192, FIGURE 28, STRAIGHT PRESS
a. Describe the operation and use of the press.
b. A press similar to that shown is to be capable of exerting a force of
20 tons when the crank is 20~ before-bottom center. The press is
exactly 10 times the'size shown, and the crank requires 1.5 seconds to
complete one revolution. Design the crankshaft main bearings, stating
a satisfactory combination of:
90

MACHINE DES IGN SLIDING BEARINGS
1. bearing- diameter and length
2. bearing material
3. lubricant to be used
4. desired clearance between shaft and bearing
PROBLEM 193, FIGURE 11, V-8 ENGINE
a. Describe the operation of the engine -and its lubricating system.
b. A main crankshaft bearing is to be designed for an engine similar to
that shown. At 380u rpm the maximum load on the bearing during each
cycle is about 4200 lbs., while the average load is 2800 lbs. Lubricating oil entering the bearing will have a temperature of approximately
205~ P., and should leave the bearing with a temperature of- about 2200 P.
Determine- a satisfactory combination of:
1. Bearing diameter and length
2. bearing material
3. SAE lubricating oil
4. desired clearance between shaft and bearing
5. surface finish of shaft and bearing.
c. Determine the amount of; oil, in gallons/min., that must flow through
the bearing to have the oil leave with the temperature mentioned above.
PROBLEM 194, FIGURE 1, DIESEL ENGINE
a. Describe the operation of the engine and its lubrication system.b. A connecting rod bearing is to be designed for an engine similar to
that shown. At 1800 rpm the maximum load on the bearing during eacn
cycle is 12000 lbs., while the average load is 6000 lbs. Temperature
of the lubricating oil entering and leaving the bearing is to be approximately 205 F and 2300 F respectively. Determine a satisfactory
combination of:
1. bearing diameter and length
2. bearing material
3. SAE lubricating oil
91

MACHINE DESIGN SLIDING BEARINGS
4. desired clearance between shaft and bearing
5. surface finish of shaft and bearing
c. Determine the amount of oil, in gallons/min., that must flow through
the bearing to have the oil leave with the temperature mentioned above.
XXVII - ROLLING BEARINGS
PROBLEM 195
a. Discuss the relative advantages and dis-advantages of ball and roller
bearings as compared to sliding bearings.
b.e Discuss the relative advantages and dis-advantages of ball bearings,
straight roller bearings, needle roller bearings, and tapered roller
bear ings.
c. Describe the means by which the tapered roller bearings of the Bevel'
Gear Speed Reducer, Figure 12, are adjusted axially, and explain why
such adjustment is necessary.
d. Describe- the construction of the tapered roller bearings which support
the worm gear in the Screw Jack, Figure 6, compared to those used in
the Bevel Gear Speed-Reducer, Figure 12. Discuss the reasons for the
two different bearing constructions.
PROBLEM 196
a. Describe the way in which the countershaft assemblies are held axially
in the Transmission,- Figure 8, and the Marine Reduction and Reverse
Gear, Figure 10.
b. Sketch and describe a method of pre-loading a pair of angular contact
ball bearings, and discuss the use of such a construction.
c. Discuss the problems involved when supporting a shaft in 3 bearings
as shown in the Bevel Gear Reversing Unit, Figure 5.
92

MACHINE DES IGN ROLLING BEAR INGS
PROBLEM 197, FIGURE 28, STAIGHT PRESS
The shaft of the motor which drives the press is to be mounted in one ball
bearing and one straight roller bearing. Both bearings are to have exactly
the same inside diameter, outside diameter and width. Make a neat sketch
showing the shaft mounted in these bearings, with the necessary shoulders,
seals, the rotor, and the belt sheave.
PROBLEM 198
a. Describe the mechanics of failure of a ball or roller bearing, and
discuss the effects-of speed and desired life on the load carrying
capacity of the bearing.
b. Approximately what relationship exists between the BL-10 life and the
average life for a group of ball or roller bearings? Illustrate this
by sketching and neatly labelling a typical normal distribution curve.
c. Describe the phenomena, of "stress corrosion' and how it affects ball
or roller bearings subjected to vibratory loads with no rotation.
PROBLEM 199, FIGURE 9, SCRAPER HOIST
a. Describe the operation and use of the scraper hoist.
b. An actual scraper hoist is 5 times the size shown on the drawing. The
double reduction helical gears next to the motor have 20~ pressure
angles and 24~ helix angles. Both gears on the countershaft have right
hand helices.; The motor rating is 20 HP at 1725 rpm. Considering the
motor to operate at its rated capacity most of the time, select a pair
of ball bearings for the countershaft which will provide an average
life of 8,000 hours per bearing.
PROBLEM 200, FIGURE 9, SCRAPER HOIST
a. Describe the operation and use of the scraper hoist.
b. An actual scraper hoist is 5 times the size shown. The shorter rope
drum is to be able to exert a pull of 4000 lbs at 175 ft/min., when the
motor is developing its rated horsepower. The bearings which support
93

MACHINE DESIGN ROLLING BEARINGS
the planet pinions are to have an average life of 10,000 hours at this
rated load condition. - Select a pair of ball bearings for the planet
-pinions.
XXVII - MISCELLANEOUS PROBLEMS
PROBLEM 201, FIGURE 14, AUTOMATIC TRANSMISSION
a. Describe the operation of the transmission to provide 3 speeds forward,
a neutral, and a reverse.
b. The low and intermediate gear ratios of the transmission are 2.4444
and 1,4815 respectively. Determine the numbers of teeth for each
gear in the transmission, and the resulting reverse ratio, if none of
the gears have less than 16 teeth.'PROBLEM 202, FIGURE 14, AUTOMATIC TRANSMISSION
a. Describe the hydraulic actuating system of the transmission, including
the location and function of the 2 oil pumps, the means of driving these
pumps, and the way in which oil gets into and out of the torque converter.
b. An internal gear type of oil pump, as used in,the transmission, is to
be designed to deliver approximately 4 gallons/min., at 2000 rpm of the
pump driving shaft. Make a neat sketch-, to scale, showing the following
for your design:
1. location and size of gears
2. number of teeth in gears
3. face width
4. location of inlet and outlet ports
C.- The discharge pressure of the pump is held at 95 psi by a relief valve
in the hydraulic circuit. The transmission is used with an engine which
performs as shown by the curve of Figure 31. How much horsepower is
required to drive the pump designed above when the engine is developing
its maximum horsepower?
94

MACHINE DESIGN MISCELLANEOUS PROBLEMS
PROBLEM 203, FIGURE 23, CAPSTAN WINCH
A winch similar to that shown is to be used with a fiber rope to handle
cargo. By wrapping the fiber rope around the drum a number of turns, and
then pulling on the free end, an operator standing at the winch is to be
capable of hoisting a 500 lb load at a uniform rate of about 25 ft/min.
It is anticipated that the efficiency-of the worm drive will be about 40%.
Determine a satisfactory combination of:
1. rope drum diameter
2. size and material of rope
3. number of turns needed on drum
4. pounds pull to be exerted on rope by operator
5. size and speed of AC induction motor to drive winch
6. worm gear ratio needed
PROBLEM 204, FIGURE 20, CRUSHER
a. Describe the construction and use of the crusher.
b. A crusher which is 10 times the size shown has jaws which are 2 ft.
wide. The toggle linkage must exert a maximum force of 10 tons on the
crusher jaw, at an average rate of 100 times/min.
Determine a satisfactory combination of thickness, width, and material
for the toggle links, and the torque required to turn the crank when in
the position where this maximum force is exerted on the jaw.
PROBLEM 205, FIGURE 26, HYDRAULIC CYLINDER
a. Describe the construction and use of the cylinder, including the
purpose of the protrusions on the piston and the receptacles in the
cylinder ends.
b. A hydraulic cylinder similar to that shown-is to have a 12" stroke and
be capable of exerting a force of approximately 3 tons when using oil
at 500 psi pressure. Determine a satisfactory combination of:
1. cylinder diameter and wallthickness
2. cylinder mater ial
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MACHINE -DISIGN 3 9015 02493 8055 MISCELIANEOUS PROBLEMS
PROBLEM 206, FP IGURE 21, C FRAME PRESS
a. Describe the construction of the press.
b. The following data is given for a press similar to that shown:
1. stroke = 8"
2. Pitman rod length = 20"
3. maximum force exerted = 25 tons
4. crank position at maximum force = 20~ before dead center
5. maximum press opening = 15"'
6. throat depth = 15" from centerline of punch
Design the vertical, straight section of the press frame, and make a
neat sketch, drawn to scale and completely dimensioned, showing a cross
section of the frame where vertical, and the material to be used for
the frame.
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