Machine design bits

Machine Design
1. Design of Joints:
Cotters
Keys
Splines
Welded joints
Threaded fasteners
Joints formed by interference fits
2. Design of friction drives
Couplings
Clutches
Introduction Friction clutches
Torque transmitting capacity
Uniform pressure theory
Uniform wear theory
Multi-disk clutches
Cone clutches
Centrifugal clutches
Friction materials for clutches
Belt and Chain drives
Length of the belt
Belt tension
Centrifugal tension
Condition for maximum power
Selection of V-belt drive
Initial tension in the belt
Chain drive
Rope drive
Power screw
Types of power screw
Self locking screw
Efficiency of screw
Collar friction
3. Design of power transmission system
Spur gear
Classification of Gears
Mitres gear
Pitch point
Pressure angle
Backlash
Minimum Number of Teeth
Forms of teeth
Cycloidal teeth
Involute teeth
Contact ratio
Interference
Face Width
Beam Strength of Gear Tooth
Wear Strength of Gear Tooth
Gear Lubrication
Simple Gear train
Compound gear train
Reverted gear train
Epicyclic gear train

Helical Gears
Terminology of Helical Gears
Virtual Number of Teeth
Bevel Gears
Worm Gears
Worm Gears 600
Friction in Worm Gears 6JJ
Selection of Materials 618
Strength Rating of Worm Gears 618
Wear Rating of Worm Gears 622
Thermal Considerations 6
4. Design of bearings
Rolling Contact Bearings
Types of Rolling Contact Bearings 417
Dynamic Load Carrying Capacity 422
Equivalent Bearing Load 423
Load-life Relationship 423
Selection of Taper Roller Bearings 437
Lubrication of Rolling Contact Bearings 453
Sliding Contact Bearings
Basic Modes of Lubrication 456
Hydrostatic Step Bearing 464
Energy Losses in Hydrostatic Bearing 466
Temperature Rise 483
Bearing Materials 495
Lubricating Oils 497
Greases 502
Comparison of Rolling and Sliding Contact bearings 503
5. Fluctuating Load Consideration for Design
Stress Concentration 117
Fluctuating Stresses 127
Endurance Limit 128
Notch Sensitivity 130
Soderberg and Goodman Diagrams 146
Gyroscopic motion
6. Miscellaneous

1. Design of Joint
Objective Questions (IES, IAS, GATE)
Cotters
1. Match List I with List II and select the correct answer using the code given below
the Lists:
List I List II
(Application) (Joint)
A. Boiler shell 1. Cotter joint
B. Marine shaft coupling 2. Knuckle joint
C. Crosshead and piston road 3. Riveted joint
D. Automobile gear box 4. Splines
(gears to shaft) 5. Bolted Joint
Code: [IES 2007]
A B C D A B C D
(a) 1 4 2 5 (b) 3 5 1 4
(c) 1 5 2 4 (d) 3 4 1 5
1. Ans. (b)
2. Match List-I (Parts to be joined) with List-II (Type of Joint) and select the correct
answer using the code given below: [IES-2006]
List-I List -II
A. Two rods having relative axial 1. Pin Joint motion
B. Strap end of the connecting rod 2. Knuckle Joint
C. Piston rod and cross head 3. Gib and Cotter Joint
D. Links of four-bar chain 4. Cotter Joint
A B C D A B C D
(a) 1 3 4 2 (b) 2 4 3 1
(c) 1 4 3 2 (d) 2 3 4 1
2. Ans. (d)
3. Match List I with List II and select the correct answer. [IES-1994]
List I (Types of joints) List II (An element of the joint)
A. Riveted joint 1. Pin
B. Welded joint 2. Strap
C. Bolted joint 3. Lock washer
D. Knuckle joint 4. Fillet
Codes: A B C D A B C D
(a) 4 3 2 1 (b) 2 3 4 1
(c) 2 4 3 1 (d) 2 4 1 3
3. Ans. (c)
4. In a gib and cotter joint, the gib and cotter are subjected to [IES-2006]
(a) single shear only (b) double shear only
(c) single shear and crushing (d) double shear and crushing
4. Ans. (b)
5. Match List I (Items in joints) with List II (Type of failure) and select the correct
answer using the codes given below the Lists: [IES-2004]
List I List II

A. Bolts in bolted joints of engine cylinder cover plate 1. Double transverse shear
B. Cotters in cotter joint 2. Torsional shear
C Rivets in lap joints 3 Single transverse shear
D. Bolts holding two flanges in a flange coupling 4. Tension
A B C D A B C D
(a) 4 1 3 2 (b) 4 2 3 1
(c) 3 1 4 2 (d) 3 2 4 1
5. Ans. (a)
6. In a cotter joint, the width of the cotter at the centre is 50 mm and its thickness is
12 mm. The load acting on the cotter is 60 kN. What is the shearing stress developed
in the cotter? [IES-2004]
(a) 120 N/mm2
(b) 100 N/mm2
(c) 75 N/mm2
(d) 50 N/mm2
6. Ans. (d) It is a case of double shear.
Shear stress
3
2Load 60 10
50N / mm
2 Area 2 50 12
×
= = =
× × ×
7. The spigot of a cotter joint has a diameter D and carries a slot for cotter. The
permissible crushing stress is x times the permissible tensile stress for the material of
spigot where x > 1. The joint carries an axial load P. Which one of the following
equations will give the diameter of the spigot? [IES-2001]
(a)
1
2
t
P x
D
xπσ
−
= (b)
1
2
t
P x
D
xπσ
+
= (c)
2 1
t
P x
D
xπ σ
+
= (d)
2
1
t
P
D x
πσ
= +
7. Ans. (b)
8. Match List-l (Machine element) with List-II (Cause of failure) and select the correct
answer using the codes given below the lists: [IES-1998]
List-I List-II
A. Axle 1. Shear stress
B. Cotter 2. Tensile/compressive stress
C. Connecting rod 3. Wear
D. Journal bearing 4. Bending stress
Code: A B C D A B C D
(a) 1 4 2 3 (b) 4 1 2 3
(c) 4 1 3 2 (d) 1 4 3 2
8. Ans. (a)
9. The piston rod and the crosshead in a steam engine are usually connected by
means of
(a) Cotter joint (b) Knuckle joint (c) Ball joint (d) Universal joint [IES-2003]
9. Ans. (a)
10. A cotter joint is used when no relative motion is permitted between the rods
joined by the cotter. It is capable of transmitting [IES-2002]
(a) twisting moment (b) an axial tensile as well as compressive load
(c) the bending moment (d) only compressive axial load
10. Ans. (b)
11. Match List I with List II and select the correct answer using the codes given below
the lists:
List I List II [IES-1995]
(Different types of detachable joints) (Specific use of these detachable joints)
A. Cotter joint 1. Tie rod of a wall crane

B. Knuckle joint 2. Suspension bridges
C. Suspension link joint 3. Diagonal stays in boiler
D. Turn buckle (adjustable joint) 4. Cross-head of a steam engine.
(a) 4 2 3 1 (b) 4 3 2 1
(c) 3 2 1 4 (d) 2 1 4 3
11. Ans. (b)
the lists:
List I (Type of joint) List II (Mode of jointing members) [IES-1993]
A. Cotter joint 1. Connects two rods or bars permitting small amount of flexibility
B. Knuckle joint 2. Rigidly connects two members
C. Turn buckle 3. Connects two rods having threaded ends
D. Riveted joint 4. Permanent fluid-tight joint between two flat pieces
5. Connects two shafts and transmits torque
(a) 5 1 3 2 (b) 2 1 3 4
(c) 5 3 2 4 (d) 2 3 1 4
12. Ans. (b)
13. Assertion (A): When the coupler of a turn buckle is turned in one direction both
the connecting rods either move closer or move away from each other depending
upon the direction of rotation of the coupler. [IES-1996]
Reason (R): A turn buckle is used to connect two round rods subjected to tensile
loading and requiring subsequent adjustment for tightening or loosening.
13. Ans. (a)
Keys
14. In the assembly design of shaft, pulley and key, the weakest member is
(a) pulley (b) key (c) shaft (d) none [IES-1998]
14. Ans. (b)
15. Match List-I (Type of keys) with List-II (Characteristic) and select the correct
List-I List-II
A. Woodruff key 1. Loose fitting, light duty
B. Kennedy key 2. Heavy duty
C. Feather key 3. Self-aligning
D. Flat key 4. Normal industrial use
(a) 2 3 1 4 (b) 3 2 1 4
(c) 2 3 4 1 (d) 3 2 4 1
15. Ans. (d)
16. A spur gear transmitting power is connected to the shaft with a key of rectangular
section. The type (s) of stresses developed in the key is fare. [IES-1995]
(a) shear stress alone (b) bearing stress alone
(c) both shear and bearing stresses (d) shearing, bearing and bending stresses.
16. Ans. (c) Key develops both shear and bearing stresses.
17. Assertion (A): The effect of keyways on a shaft is to reduce its load carrying
capacity and to increase its torsional rigidity. [IES-1994]

Reason (R): Highly localized stresses occur at or near the corners of keyways.
17. Ans. (a) Both A and R are true, and R provides correct explanation, for A.
18. In the assembly of pulley, key and shaft [IES-1993]
(a) pulley is made the weakest (b) key is made the weakest
(c) key is made the strongest (d) all the three are designed for equal strength
18. Ans. (b) Key is made the weakest so that it is cheap and easy to replace in case
of failure.
19. Which key is preferred for the condition where a large amount of impact torque is
to be transmitted in both direction of rotation? [IES-1992]
(a) Woodruff key (b) Feather key (c) Gib-head key (d) Tangent key
19. Ans. (d)
20. Square key of side "d/4" each and length I is used to transmit torque "T" from the
shaft of diameter "d" to the hub of a pulley. Assuming the length of the key to be
equal to the thickness of the pulley, the average shear stress developed in the key is
given by [GATE-2003]
2 2 3
4 16 8 16
( ) ( ) ( ) ( )
T T T T
a b c d
ld ld ld dπ
20. Ans. (c)
21. A key connecting a flange coupling to a shaft is likely to fail in [GATE-1995]
(a) shear (b) tension (c) torsion (d) bending
21. Ans. (a) Shear is the dominant stress on the key
22. What is sunk key made in the form of a segment of a circular disc of uniform
thickness, known as? [IES-2006]
(a) Feather key (b) Kennedy key (c) Woodruff key (d) Saddle key
22. Ans. (c)

23. What are the key functions of a master schedule? [IES-2005]
1. To generate material and capacity requirements
2. To maintain valid priorities
3. An effective capacity utilization
4. Planning the quantity and timing of output over the intermediate time horizons
Select the correct answer using the code given below:
(a) 1, 2 and 3 (b) 2, 3 and 4 (c) 1, 3 and 4 (d) 1, 2 and 4
23. Ans. (b)
24. A square key of side d/4 is to be fitted on a shaft of diameter d and in the hub of a
pulley. If the material of the key and shaft is same and the two are to be equally
strong in shear, what is the length of the key? [IES-2005]
(a)
2
dπ
(b)
2
3
dπ
(c)
3
4
dπ
(d)
4
5
dπ
24. Ans. (a)
25. Which one of the following statements is correct? [IES-2004]
While designing a parallel sunk key it is assumed that the distribution of force along
the length of the key
(a) varies linearly (b) is uniform throughout
(c) varies exponentially, being more at the torque input end
(d) varies exponentially, being less at torque output end
25. Ans. (c)
26. Match List-I (Device) with List-II (Component/Accessory) and select the correct
List-I List-II
(Device) (Component/Accessory)
A. Lifting machine 1. Idler of Jockey pulley
B. Fibre rope drive 2. Sun wheel
C. Differential gear 3. Sheave
D. Belt drive 4. Power screw
Codes:A B C D A B C D
(a) 4 3 1 2 (b) 3 4 1 2
(c) 4 3 2 1 (d) 3 4 2 1
26. Ans. (c)
27. A pulley is connected to a power transmission shaft of diameter d by means of a
rectangular sunk key of width wand length ‘l’. The width of the key is taken as d/4.
For full power transmission, the shearing strength of the key is equal to the torsional
shearing strength of the shaft. The ratio of the length of the key to the diameter of the
shaft (l/d) is [IES-2003]
(a)
4
π
(b)
2
π
(c)
2
π
(d) π
27. Ans. (c)

4
3
3
Shearingstrength of key: . .
4
Torque(T) = . . . .
2 4 2
Torsionalshearing,
232
16
For same strength
. . .
4 2 16
2
d
F l
d d d
F l
T
dd
orT d
d d
l d
l
or
d
τ
τ
τ
π
τ
π
τ
τ π
π
⎛ ⎞
= ⎜ ⎟
⎝ ⎠
⎛ ⎞
= ⎜ ⎟
⎝ ⎠
=
= ×
⎛ ⎞
= ×⎜ ⎟
⎝ ⎠
=
28. Assertion (A): A Woodruff key is an easily adjustable key.
Reason (R): The Woodruff key accommodates itself to any taper in the hub or boss
of the mating piece. [IES-2003]
28. Ans. (c)
29. The key shown in the above figure
is a
(a) Barth key
(b) Kennedy key
(c) Lewis key
(d) Woodruff key
[IES-2000]
29. Ans. (a)
30. Match List I (Keys) with List II (Characteristics) and select the correct answer
using the codes given below the Lists: [IES-2000]
List I List II
A. Saddle key 1. Strong in shear and crushing
B. Woodruff key 2. Withstands tension in one direction
C. Tangent key 3. Transmission of power through frictional resistance
D. Kennedy key 4. Semicircular in shape
(a) 3 4 1 2 (b) 4 3 2 1
(c) 4 3 1 2 (d) 3 4 2 1
30. Ans. (d)
31. The shearing area of a key of length 'L', breadth 'b' and depth 'h' is equal to
(a) b x h (b) Lx h (c) Lx b (d) Lx (h/2) [IES-1998]
31. Ans. (c)

Splines
32. Consider the following statements: [IES-1998]
A splined shaft is used for
1. transmitting power
2. holding a flywheel rigidly in position
3. moving axially the gear wheels mounted on it 4. mounting V-belt pulleys on it.
Of these statements
(a) 2 and 3 are correct (b) 1 and 4 are correct
(c) 2 and 4 are correct (d) 1 and 3 are correct
32. Ans. (d)
Welded joints
33. In a fillet welded joint, the weakest area of the weld is [IES-2002]
(a) toe (b) root (c) throat (d) face
33. Ans. (c)
34. A single parallel fillet weld of total length L and weld size h subjected to a tensile
load P, will have what design stress? [IES 2007]
(a) Tensile and equal to
Lh
P
707.0
(b) Tensile and equal to
Lh
P
(c) Shear and equal to
Lh
P
707.0
(d) Shear and equal to
Lh
P
34. Ans. (c)
Throat, t = h cos450
= h
v2
1
= 0.707h
T =
Lt
P
=
Lh
P
707.0
35. Two metal
plates of thickness
’t’ and width 'w' are
joined by a fillet
weld of 45° as
shown in given
figure.
[IES-1998]
When subjected to a pulling force 'F', the stress induced in the weld will be
(a)
sin 45o
F
wt
(b)
F
wt
(c)
sin 45o
F
wt
(d)
2F
wt
35. Ans. (a)

36. A butt welded joint,
subjected to tensile force P is
shown in the given figure, l =
length of the weld (in mm) h =
throat of the butt weld (in mm)
and H is the total height of weld
including reinforcement. The
average tensile stress σt, in the
weld is given by
[IES-1997]
( ) ( ) ( ) ( )
2
a b c d
2
t t t t
P P P P
Hl hl hl Hl
σ σ σ σ= = = =
36. Ans. (b)
37. In the welded joint shown in the given figure,
if the weld at B has thicker fillets than that at A,
then the load carrying capacity P, of the joint will
(a) increase (b) decrease
(c) remain unaffected (d) exactly get doubled
[IES-1997]
37. Ans. (c)
38. A double fillet welded joint with parallel fillet weld of length L and leg B is
subjected to a tensile force P. Assuming uniform stress distribution, the shear stress
in the weld is given by [IES-1996]
(a)
2
.
P
B L
(b)
2. .
P
B L
(c)
2. .
P
B L
(d)
2
.
P
B L
38. Ans. (c)
39. The following two figures show welded joints (x x x x x indicates welds), for the
same load and same dimensions of plate and weld. [IES-1994]
The joint shown in
(a) fig. I is better because the weld is in shear and the principal stress in the weld is
not in line with P
(b) fig. I is better because the load transfer from the tie bar to the plate is not direct
(c) fig. II is better because the weld is in tension and safe stress of weld in tension is
greater than that in shear
(d) fig. II is better because it has less stress concentration.
39. Ans. (c) Figure II is better because the weld is in tension and safe stress of weld
in tension is greater than shear.

40. Two plates are joined together by means of single
transverse and double parallel fillet welds as shown
in figure given above. If the size of fillet is 5 mm and
allowable shear load per mm is 300 N, what is the
approximate length of each parallel fillet?
(a) 150 mm (b) 200 mm
(c) 250 mm (d) 300 mm
[IES-2005]
40. Ans. (b) ( )300 100 2l 15000 or l 200× + = =
41. A circular rod of diameter d is welded to a flat plate along its circumference by
fillet weld of thickness t. Assuming τw as the allowable shear stress for the weld
material, what is the value of the safe torque that can be transmitted? [IES-2004]
(a) 2
. . wd tπ τ (b)
2
. .
2
w
d
t
π
τ (c)
2
. .
2 2
w
d
t
π
τ (d)
2
. .
2
w
d
t
π
τ
41. Ans. (b)
( )
W
W
2
W W
Shear stress
Shear fore dt
d d
Torque T dt .t
2 2
τ
τ π
π
τ π τ
=
= ×
= × × =
42. A circular solid rod of diameter d welded to a rigid flat plate by a circular fillet weld
of throat thickness t is subjected to a twisting moment T. The maximum shear stress
induced in the weld is [IES-2003]
(a) 2
T
tdπ
(b) 2
2T
tdπ
(c) 2
4T
tdπ
(d) 3
2T
tdπ
42. Ans. (b) 3 2
.
. 22
4
d
T
T r T
tdJ td
τ
π π
⎛ ⎞
⎜ ⎟
⎝ ⎠= = =
43. The permissible stress in a filled weld is 100 N/mm2
. The fillet weld has equal leg
lengths of 15 mm each. The allowable shearing load on weldment per cm length of
the weld is [IES-1995]
(a) 22.5 kN (b) 15.0 kN (c) 10.6 kN (d) 7.5 kN.
43. Ans. (c) Load allowed = 100 x 0.707 x 10 x15 = 10.6 kN
44. A 60 mm long and 6 mm thick fillet weld carries a steady load of 15 kN along the
weld. The shear strength of the weld material is equal to 200 MPa. The factor of
safety is [GATE-2006]
(a) 2.4 (b) 3.4 (c) 4.8 (d) 6.8
44. Ans. (b)

Threaded fasteners
45. A force ‘F’ is to be transmitted through a square-threaded power screw into a nut.
If ‘t’ is the height of the nut and‘d’ is the minor diameter, then which one of the
following is the average shear stress over the screw thread? [IES 2007]
(a)
dt
f
π
2
(b)
dt
F
π
(c)
dt
F
π2
(d)
dt
F
π
4
45. Ans. (b)
46. Consider the case of a square-
threaded screw loaded by a nut as shown
in the given figure. The value of the
average shearing stress of the screw is
given by (symbols have the usual
meaning)
( )
2
( ) ( )
2
( )
r r
F F
a b
d h d h
F F
c d
dh dh
π π
π π
[IES-1997]
46. Ans. (b)
47. Assertion (A): Uniform-strength bolts are used for resisting impact loads.
Reason (R): The area of cross-section of the threaded and unthreaded parts is made
equal. [IES-1994]
47. Ans. (c) A is true and R is false.
48. How can shock absorbing capacity of a bolt be increased? [IES 2007]
(a) By tightening it property (b) By increasing the shank diameter
(c) By grinding the shank
(d) By making the shank diameter equal to the core diameter of thread
48. Ans. (d)
49. The number of slots is a 25 mm castle nut is [IES-1992]
(a) 2 (b) 4 (c) 6 (d) 8
49. Ans. (c)

50. A threaded nut of M16, ISO metric type, having 2 mm pitch with a pitch diameter
of 14.701 mm is to be checked for its pitch diameter using two or three numbers of
balls or rollers of the following sizes [GATE-2003]
(a) Rollers of 2 mm ϕ (b) Rollers of 1.155 mm ϕ
(c) Balls of 2 mm ϕ (d) Balls of 1.155 mm ϕ
50. Ans. (b)
Joints formed by interference fits
Answers with Explanation (Objective)

2. Design of friction drives
Couplings
1. Consider the following statements in respect of flexible couplings: [IES-2006]
1. The flanges of flexible coupling are usually made of grey cast iron FG200.
2. In the analysis of flexible coupling, it is assumed that the power is transmitted by
the shear resistance of the pins.
3. Rubber bushes with brass lining are provided to absorb misalignment between the
two shafts.
Which of the statements given above are correct?
(a) 1, 2 and 3 (b) Only 1 and 2 (c) Only 2 and 3 (d) Only 1 and 3
1. Ans. (a) Note: It is flexible coupling not fluid coupling.
2. Which of the following stresses are associated with the design of pins in bushed
pin-type flexible coupling? [IES-1998]
1. Bearing stress 2. Bending stress
3. Axial tensile stress 4. Transverse shear stress
Select the correct answer using the codes given below
Codes:(a) 1, 3 and 4 (b) 2, 3 and 4 (c) 1, 2 and 3 (d) 1, 2 and 4
2. Ans. (d)
the lists:
A. Crank shaft 1. Supports the revolving parts and transmits torque.
B. Wire shaft 2. Transmits motion between shafts where it is not possible to
effect a rigid coupling between them
C. Axle 3. Converts linear motion into rotary motion
D. Plain shaft 4. Supports only the revolving parts.
(a) 3 2 1 4 (b) 4 2 3 1
(c) 3 2 4 1 (d) 1 4 2 3
3. Ans. (a)
4 The bolts in a rigid flanged coupling connecting two shafts transmitting power are
subjected to
(a) shear force and bending moment (b) axial force [GATE-1996]
(c) torsion (d) torsion and bending moment.
4. Ans. (a)
Clutches
Introduction Friction clutches
5. Which one of the following is not a friction clutch? [IES-2003]
(a) Disc or plate clutch (b) Cone clutch (c) Centrifugal clutch (d) Jaw clutch
5. Ans. (d)

6. Which one of the following pairs of parameters and effects is not correctly
matched?
(a) Large wheel diameter ………………..Reduced wheel wear [IES-1998]
(b) Large depth of cut …………………...Increased wheel wear
(c) Large work diameter ………………...Increased wheel wear
(d) Large wheel speed …………………..Reduced wheel wear
6. Ans. (d)
7. Two co-axial rotors having moments of inertia I1, I2 and angular speeds ω1 and ω2
respectively are engaged together. The loss of energy during engagement is equal to
[IES-1994]
(a)
( )
( )
2
1 2 1 2
1 22
I I
I I
ω ω−
+
(b)
( )
( )
2
1 2 1 2
1 22
I I
I I
ω ω−
−
(c)
( )
( )
2
1 2 1 2
1 2
2I I
I I
ω ω−
+
(d)
( )
2 2
1 1 2 2
1 2
I I
I I
ω ω−
+
7. Ans. (a)
8. Which of the following statements hold good for a multi-collar thrust bearing
carrying an axial thrust of W units? [IES-1996]
1. Friction moment is independent of the number of collars.
2. The intensity of pressure is affected by the number of collars.
3. Co-efficient of friction of the bearing surface is affected by the number of collars.
(a) 1 and 2 (b) 1 and 3 (c) 2 and 3 (d) 1, 2 and 3
8. Ans. (a)
9. Which of the following statements regarding laws governing the friction between
dry surfaces are correct? [IES-1996]
1. The friction force is dependent on the velocity of sliding.
2. The friction force is directly proportional to the normal force.
3. The friction force is dependent on the materials of the contact surfaces.
4. The frictional force is independent of the area of contact
(a) 2, 3 and 4 (b) 1 and 3 (c) 2 and 4 (d) 1, 2, 3 and 4
9. Ans. (a)
Torque transmitting capacity
Uniform pressure theory
10. Assertion (A): In case of friction clutches, uniform wear theory should be
considered for power transmission calculation rather than the uniform pressure
theory.
Reason (R): The uniform pressure theory gives a higher friction torque than the
uniform wear theory. [IES-2003]
10. Ans. (a)
11.A clutch has outer and inner diameters 100 mm and 40 mm respectively.
Assuming a uniform pressure of 2 MPa and coefficient of friction of liner material 0.4,
the torque carrying capacity of the clutch is [GATE-2008]
(a) 148 Nm (b) 196 Nm (c) 372 Nm (d) 490 Nm
11. Ans. (b) Force(P)= ( )22
4
dD
p
−
π

T=
( )
( )22
33
.
3 dD
dDP
−
−μ
= ( ) ( )33
6
33
04.01.0
12
1024.0
..
12
−
×××
=−
πμπ
dDp =196Nm
12. Which one of the following is the correct expression for the torque transmitted by
a conical clutch of outer radius R, Inner radius r and semi-cone angle α assuming
uniform pressure? (Where W = total axial load and μ = coefficient of friction)
(a)
( )
2sin
W R rμ
α
+
(b)
( )
3sin
W R rμ
α
+
[IES-2004]
(c)
3 3
2 2
2 ( )
3sin ( )
W R r
R r
μ
α
−
−
(d)
3 3
2 2
3 ( )
4sin ( )
W R r
R r
μ
α
−
−
12. Ans. (c)
13. A disk clutch is required to transmit 5 kW at 2000 rpm. The disk has a friction
lining with coefficient of friction equal to 0.25. Bore radius of friction lining is equal to
25 mm. Assume uniform contact pressure of 1 MPa. The value of outside radius of
the friction lining is
(a) 39.4 mm (b) 49.5 mm (c) 97.9 mm (d) 142.9 mm
13. Ans. (a) [GATE-2006]
14. When the intensity of pressure is uniform in a flat pivot bearing of radius r, the
friction force is assumed to act at
(a) r (b) r/2 (c) 2r/3 (d) r/3 [IES-2001]
14. Ans. (c)
15. In a flat collar pivot bearing, the moment due to friction is proportional to (r1 and r2
are the outer and inner radii respectively) [IES-1993]
2 2 2 2 3 3 3 3
1 2 1 2 1 2 1 2
2 2
1 2 1 2 1 2 1 2
( ) ( ) ( ) ( )
r r r r r r r r
a b c d
r r r r r r r r
− − − −
− + − −
15. Ans. (c)
Uniform wear theory
73. In designing a plate clutch, assumption of uniform wear conditions is made
because
(a) it is closer to real life situation (b) it leads to a safer design. [IES-
1996]

(c) it leads to cost effective design (d) no other assumption is possible.
73. Ans. (a)
105. The frictional torque transmitted in a flat pivot bearing, assuming uniform wear,
is [IAS-2002]
(a) WRμ (b)
3
4
WRμ (c)
2
3
WRμ (d)
1
2
WRμ
(Where μ = Coefficient of friction; W = Load over the bearing; R = Radius of bearing)
105. Ans. (d) Use frictional clutch formula.
( ), 0 2
4 2
W R
T D d d and D R gives T
μ μπ
= + = = =
Multi-disk clutches
30. In a multiple disc clutch if n1 and n2 are the number of discs on the driving and
driven shafts, respectively, the number of pairs of contact surfaces will be [IES-
2001; IES-2003]
(a) 1 2n n+ (b) 1 2 1n n+ − (c) 1 2 1n n+ + (d) 1 2
2
n n+
30. Ans. (b)
98. In the multiple disc clutch, if there are 6 discs on the driving shaft and 5 discs on
the driven shaft, then the number of pairs of contact surfaces will be equal to
[IES-1997]
(a) 11 (b) 12 (c) 10 (d) 22
98. Ans. (a) No. of active plates = 6 x 2 - 1 = 11.
Cone clutches
Centrifugal clutches
35. On the motors with low starting torque, the type of the clutch to be used is
(a) Multiple-plate clutch (b) Cone clutch [IES-2003]
(c) Centrifugal clutch (d) Single-plate clutch with both sides effective
35. Ans. (c)
114. Consider the following statements regarding a centrifugal clutch: [IES-2000]
1. It need not be unloaded before engagement.
2. It enables the prime mover to start up under no-load conditions.
3. It picks up the load gradually with the increase in speed
4. It will not slip to the point of destruction
5. It is very useful when the power unit has a low starting torque
Which of these are the advantages of centrifugal clutch?
(a) 1, 2 and 4 (b) 1, 3 and 5 (c) 2, 3 and 5 (d) 1, 3, 4 and 5
114. Ans. (a)
104. Match List-I with List-II and select the correct answer using the codes given
below the lists:

List-I List-II
A. Single-plate friction clutch 1. Scooters [IES-1998]
B. Multi-plate friction clutch 2. Rolling mills
C. Centrifugal clutch 3. Trucks
D. Jaw clutch 4. Mopeds
(a) 1 3 4 2 (b) 1 3 2 4
(c) 3 1 2 4 (d) 3 1 4 2
104. Ans. (c)
Friction materials for clutches
Belt and Chain drives
12. The creep in a belt drive is due to the [IES-2001]
(a) material of the pulleys (b) material of the belt
(c) unequal size of the pulleys (d) unequal tension on tight and slack sides of the
belt
12. Ans. (d)
39. Assertion (A): In design of arms of a pulley, in belt drive, the cross-section of the
arm is, elliptical with minor axis placed along the plane of rotation. [IES-2001]
Reason (R): Arms of a pulley in belt drive are subjected to complete reversal of
stresses and is designed for bending in the plane of rotation.
39. Ans. (d)
84. Assertion (A): In pulley design of flat belt drive, the cross-sections of arms are
made elliptical with major axis lying in the plane of rotation. [IES-1999]
Reason (R): Arms of a pulley in belt drive are subjected to torsional shear stresses
and are designed for torsion.
84. Ans. (c)
89. Which one of the following belts should not be used above 40°C? [IES-1999]
(a) Balata belt (b) Rubber belt (c) Fabric belt (d)
Synthetic belt
89. Ans. (b)
69. In μ is the actual coefficient of friction in a belt moving in grooved pulley, the
groove angle being 2α, the virtual coefficient of friction will be [IES-1997]
(a) / sinμ α (b) / cosμ α (c) sinμ α (d) cosμ α
69. Ans. (a)
67. In flat belt drive, if the slip between the driver and the belt is 1%, that between
belt and follower is 3% and driver and follower pulley diameters are equal, then the
velocity ratio of the drive will be [IES-1996]
(a) 0.99 (b) 0.98 (c) 0.97 (d) 0.96.
67. Ans. (d)
1. A pulley and belt in a belt drive from a [IAS-2001]
(a) cylindrical pair (b) turning pair(c) rolling pair (d) sliding pair
1. Ans. (c)

20. Crushed ore is dropped on a conveyor belt at the rate of 300 kg/s. The belt
moves at speed of 2 m/s. The net force acting on the belt that keeps it moving at the
same speed is [IAS-2001]
(a) 30 N (b) 60 N (c) 300 N (d) 600 N
20. Ans. (d) Force = ( ) 300 2 600
d dm
mv v N
dt dt
= × = × =
1.16 Total slip will Occur in a belt drive when [GATE-1997]
(a) angle of rest is zero (b) angle of creep is zero
(c) angle of rest is greater than angle of creep (d) angle of creep is greater than
angle of rest
1.16 Ans. (a)
54. Assertion (A): Crowning is provided on the surface of a flat pulley to prevent
slipping of the belt sideways. [IES-2006]
Reason (R): Bell creep, which is the reason for slip of the belt sideways, is fully
compensated by providing crowning on the pulley.
54. Ans. (c) Belt creep has no effect on sideways.
106. The bolts in a rigid flanged coupling connecting two shafts transmitting power
are subjected to [IES-2002]
(a) shear force and bending moment (b) axial force.
(c) torsion and bending moment (d) torsion
106. Ans. (a)
Length of the belt
102. The length of the belt in the case of a cross-belt drive is given in terms of centre
distance between pulleys (C), diameters of the pulleys D and d as [IES-2002]
(a) ( )
( )
2
2
2 4
D d
C D d
C
π +
+ + + (b) ( )
( )
2
2
2 4
D d
C D d
C
π +
+ − +
(c) ( )
( )
2
2
2 4
D d
C D d
C
π −
+ + + (d) ( )
( )
2
2
2 4
D d
C D d
C
π −
+ − +
102. Ans. (a)
69. Which one of the following statements relating to belt drives is correct?
(a) The rotational speeds of the pulleys are directly proportional to their diameters
(b) The length of the crossed belt increases as the sum of the diameters of the
pulleys increases
(c) The crowning of the pulleys is done to make the drive sturdy
(d) The slip increases the velocity ratio [IES 2007]
Ans. L = ( 21 rr +π ) + 2C +
(
C
rr 2
21 )+
where C = centre distance of shafts.
Belt tension
61. Assertion (A): In a short centre open-belt drive, an idler pulley is used to maintain
the belt tension and to increase the angle of contact on the smaller pulley.
[IES-1994]

Reason (R): An idler pulley is free to rotate on its axis and is put on the slack side of
the belt.
61. Ans. (a) Both A and R are true, and R provides correct explanation for A.
97. In a dell drive, if the pulley diameter is doubled keeping the tension and belt width
constant, then it will be necessary to [IES-1993]
(a) increase the key length (b) increase the key depth
(c) increase the key width (d) decrease the key length
97. Ans. (c) Due to twice increase in diameter of pulley, torque on key is double and
has to be resisted by key width. Length can't be increased as belt width is same.
99. The following data refers to an open belt drive: [IES-1993]
Pulley A Pulley B
Purpose …………………. Driving Driven
Diameter………………… 450 mm 750 mm
Angle of contact………… θA = 150o
θA = 210o
Coefficient of friction between 0.36Af = 0.22Af =
belt and pulley
The ratio of tensions may be calculated using the relation (T1/T2) = exp (z) where z is
( )( ) ( )( ) ( ) ( ) / 4 ( ) / 2A A B B A B A B A A B Ba f b f c f f d f fθ θ θ θ θ θ+ + +
99. Ans. (a) 1
2
A AfT
e
T
θ
= where f and θ are taken for smaller pulley.
1.14 The ratio of tension on the tight side to that on the slack side in a flat belt drive is
(a) proportional to the product of coefficient of friction and lap angle [GATE-2000]
(b) an exponential function of the product of coefficient of friction and lap angle.
(d proportional to the lap angle
(d) proportional to the coefficient of friction
1.14 Ans. (b)
2.16 The difference between tensions on the tight and slack sides of a belt drive is
3000 N. If the belt speed is 15 m/s, the transmitted power in k W is [GATE-1998]
(a) 45 (b) 22.5 (c) 90 (d) 100
2.16 Ans. (a)
2.14 The percentage improvement in power capacity of a flat belt drive, when the
wrap angle at the driving pulley is increased from 150° to 210° by an idler
arrangement for a friction coefficient of 0.3, is [GATE-1997]
(a) 25.21 (b) 33.92 (c) 40.17 (d) 67.85
2.14 Ans. (d) We know that Power transmitted (P) = ( )1 2 .T T v W−
Case-I: 1
2
T
e
T
μθ
= or
5
0.3
61
1 2 1 2
2
2.193 1.193
T
e or T T P T V W
T
π⎛ ⎞
×⎜ ⎟
⎝ ⎠
= = ⇒ =

Case-II: 1
2
T
e
T
μθ
= or
7
0.3
61
1 2 1 2
2
3.003 2.003
T
e or T T P T V W
T
π⎛ ⎞
×⎜ ⎟
⎝ ⎠
= = ⇒ =
Therefore improvement in power capacity = 2 1
1
100% 67.88%
P P
P
−
× =
5. A Differential pulley is subjected to
belt tensions as shown in the diagram.
The resulting force and moment when
transferred to the centre of the pulley
are, respectively
(a) 400 N and 0 Nm
(b) 400 N and 100 Nm
(c) 500 N and 0 Nm
(d) 500 N and 100 Nm
[IAS-2003]
Centrifugal tension
87. Centrifugal tension in belts is [IES-1999]
(a) useful because it maintains some tension even when no power is transmitted
(b) not harmful because it does not take part in power transmission
(c) harmful because it increases belt tension and reduces the power transmitted
(d) a hypothetical phenomenon and does not actually exist in belts
87. Ans. (c)
92. In the case of a vertical belt pulley drive with Tc as centrifugal tension and To as
the initial tension, the belt would tend to hang clear of the tower pulley when
[IES-1997]
( ) ( ) ( ) ( )a b / 3 c d / 2c o c o c o c oT T T T T T T T< < > <
92. Ans. (c)
2.11 With regard to belt drives with given pulley diameters, centre distance and
coefficient of friction between the pulley and the belt materials, which of the
statement below are FALSE?

(a) A crossed flat belt configuration can transmit more power than an open flat belt
configuration
(b) A "V" belt has greater power transmission capacity than an open flat belt
[GATE-1999]
(c) Power transmission is greater when belt tension is higher due to centrifugal
effects than the same belt drive when centrifugal effects are absent.
(d) Power transmission is the greatest just before the point of slipping is reached
2.11 Ans. (c)
53. Consider the following statements in case of belt drives: [IES 2007]
1. Centrifugal tension in the belt increases the transmitted power.
2. Centrifugal tension does not affect the driving tension
3. Maximum tension in the belt is always three times the centrifugal tension.
Which of the statements given above is/are correct?
(a) 1, 2 and 3 (b) 2 and 3 only
(c) 1 and 3 only (d) 1 only
Ans. (b)
64. In case of belt drives, the effect of the centrifugal tension is to: [IES-2006]
(a) cause the belt to leave the pulley and increase the power to be transmitted
(b) cause the belts to stay on the pulley and increase the power to be transmitted
(c) reduce the driving power of the belt
(d) stretch the belt in longitudinal direction
64. Ans. (d) Centrifugal tension has no effect on the power to be transmitted.
Condition for maximum power
101. Which one of the following statements with regard to belt drives is NOT correct?
(a) Increase in the angle of wrap of the belt enables more power transmission
(b) Maximum power is transmitted when the centrifugal tension is three times the
tight side tension [IES-2000]
(c) Wide and thin belt is preferable for better life than a thick and narrow one
(d) Crown is provided on the pulley to make the belt run centrally on the pulley
101. Ans. (b)
71. When a belt drive is transmitting maximum power [IES-1996]
(a) effective tension is equal to centrifugal tension.
(b) effective tension is half of centrifugal tension.
(c) driving tension on slack side is equal to the centrifugal tension.
(d) driving tension on tight side is twice the centrifugal tension.
71. Ans. (d)
101. The power transmitted by a belt is dependent on the centrifugal effect in the
belt. The maximum power can be transmitted when the centrifugal tension is [IES-
2002]
(a) 1/3 of tension (T1) on the tight side
(b) 1/3 of total tension (Tt) on the tight side
(c) 1/3 of tension (T2) on the slack side
(d) 1/3 of sum of tensions T1 and T2 i.e. 1/3 (T1 + T2)
101. Ans. (b)

Selection of V-belt drive
38. Assertion (A): For similar materials having the same maximum permissible
tension V-belt transmits more power than flat belt with same velocity ratio and centre
distance. [IES-2001]
Reason (R): As two sides of V-belt are in contact with side faces of pulley groove,
larger contact area gives greater effective frictional force.
38. Ans. (a)
100. In a multiple V belt drive, when a single belt is damaged, it is preferable to
change the complete set to [IES-1993]
(a) reduce vibration (b) reduce slip (c) ensure uniform loading (d) ensure proper
alignment
100. Ans. (c) If a single belt breaks, all belts arc replaced to ensure uniform loading.
114. A 50 kW motor using six V belts is used in a pulp mill. If one of the belts breaks
after a month of continuous running, then
[IAS 1994]
(a) the broken belt is to be replaced by a similar belt
(b) all the belt are to be replaced
(c) the broken belt and two adjacent belts are to be replaced
(d) the broken belt and one adjacent belt are to be replaced
Ans. (b)
Initial tension in the belt
93. Given that T1 and T2 are the tensions on the tight and slack sides of the belt
respectively, the initial tension of the belt taking into account centrifugal tension Tc, is
equal to [IES-1997]
(a) 1 2
3
cT T T+ +
(b) 1 2 2
2
cT T T+ +
(c) 1 2 3
3
cT T T+ +
(d)
1 2 3
3
cT T T− +
93. Ans. (b)
Chain drive
65. Which one of the following drives is used for a constant velocity ratio, positive
drive with large centre distance between the driver and driven shafts? [IES-2004]
(a) Gear drive (b) Flat belt drive (c) Chain drive (d) V-belt drive
65. Ans. (c)
110. Assertion (A): Slider-crank chain is an inversion of the four-bar mechanism.
Reason(R): Slider-crank chain often finds applications in most of the reciprocating
machinery. [IES-2003]
110. Ans. (b)
119. Match List I (Applications) with List II (Drive element) and select the correct
List I List II
A. Automobile differential 1. Flat belt
B. Bicycle 2. V-belt
C. Planning machine 3. Chain drive

D. Radiator fan of automobile 4. Gear drive
(a) 4 3 1 2 (b) 1 3 4 2
(c) 4 2 1 3 (d) 1 2 4 3
119. Ans. (a)
59. Sources of power loss in a chain drive are given below: [IES-1995]
1. Friction between chain and sprocket teeth. 2. Overcoming the chain
stiffness.
3. Overcoming the friction in shaft bearing.
4. Frictional resistance to the motion of the chain in air or lubricant.
The correct sequence of descending order of power loss due to these sources is
(a) 1,2,3,4 (b) 1,2,4,3 (c) 2,1,3,4 (d) 2,1,4,3
59. Ans. (a) Power loss in descending order takes place as 1, 2 3 and 4.
23. Given that P = chain pitch, c = centre distance, [IES-1994]
N, n = number of teeth on large and small sprocket respectively
the length of chain in terms of pitches can be approximated by
(a)
2c
P
(b)
2
) / 2
c
N n
P
+ +
(c) 22
[( ) / 2 ]
c P
N n P
P c
+ − (d) 22
( ) / 2 [( ) / 2 ]
c P
N n P N n P
P c
+ + + −
23. Ans. (d)
Rope drive
68. In a 6×20 wire rope, No.6 indicates the [IES- 2001; 2003; 2007 GATE-2003]
(a) diameter of the wire rope in mm (b) number of strands in the wire
rope
(c) number of wires (d) gauge number of the wire
Ans. (b) 6×20 wire rope: 6 indicates number of strands in the wire rope and 20
indicates no of wire in a strand.
113. Consider the following types of stresses in respect of a hoisting rope during
acceleration of load:
1. Direct stress due to weight hoisted and weight of the rope [IES-2000]
2. Bending stresses due to bending of rope over the sheave
3. Stresses due to initial tightening.
4. Acceleration stresses
Which of these are the correct types of stresses induced in a hoisting rope during
acceleration of load?
(a)1, 2 and 3 (b) 2, 3 and 4 (c)1, 2 and 4 (d) 1, 3 and 4
113. Ans. (c)
85. Assertion (A): In lifts, wire ropes are preferred over solid steel rods of same
diameter. [IES-1999]
Reason (R): Wire ropes are more flexible than steel rods and also provide plenty of
time for remedial action before failure.
85. Ans. (a)
94. Given that W = weight of load handled, Wr = weight of rope and f = acceleration,
the additional load in ropes of a hoist during starting is given by [IES-1997]

( ) ( ) ( ) ( )a b c dr r r
a a a a
W W W W WW
F f F f F f F f
g g g g
⎛ ⎞ ⎛ ⎞− +
= = = =⎜ ⎟ ⎜ ⎟
⎝ ⎠ ⎝ ⎠
94. Ans. (b)
68. Effective stress in wire ropes during normal working is equal to the stress due to
(a) axial load plus stress due to bending.
(b) acceleration / retardation of masses plus stress due to bending.
(c) axial load plus stress due to acceleration / retardation.
(d) bending plus stress due to acceleration/retardation. [IES-1996]
68. Ans. (a)
24. When compared to a rod of the same diameter and material, a wire rope
[IES-1994]
(a) is less flexible (b) has a much smaller load carrying capacity.
(c) does not provide much warning before failure.
(d) provides much greater time for remedial action before failure.
24. Ans. (d) A wire rope provides much greater time for remedial action before
failure.
Power screw
Types of power screw
76. Power screws are used to produce uniform, slow and powerful motion such as
required in presses, jacks and other machinery. 'V' threads are usually not used for
this application due to low efficiency. This is because: [IES-2005]
(a) Profile angle is zero (b) Profile angle is moderate
(c) Profile angle is large (d) There is difficulty in manufacturing the profile
76. Ans. (c)
21. Consider the following statements regarding power screws: [IES-1994]
1. The efficiency of a self-locking screw cannot be more than 50%.
2. If the friction angle is less than the helix angle of the screw, then the efficiency will
be more than 50%.
3. The efficiency of ACME (trapezoidal thread is less than that of a square thread.
Of these statements
(a) 1, 2 and 3 are correct (b) 2 and 3 are correct
(c) I and 3 are correct (d) 1 and 2 are correct
21. Ans. (a)
43. Assertion (A): Buttress thread is a modified square thread profile which is
employed on the lead screw of machine tools. [IES-2001]
Reason (R): Frequent engagement and disengagement of lead screw for automatic
feed is not possible with perfect square threads, therefore, the square profile has to
be modified.
43. Ans. (a)
112. The following parameters are to be calculated while designing screw jack.
1. Core diameter of screw 2. Torque required to rotate the screw [IES-2000]
3. Principal stresses 4. Height of the nut
The correct sequence of the calculation of these parameters is

(a) 1, 2, 4, 3 (b) 1, 2, 3, 4 (c) 2, 1, 3, 4 (d) 2, 1, 4, 3
112. Ans. (c)
55. While designing a screw in a screw jack against buckling failure, the end
conditions for the screw are taken as[IES-1995]
(a) both the ends fixed (b) both the ends hinged
(c) one end fixed and other end hinged (d) one end fixed and the other end free.
55. Ans. (d)
57. Assertion (A): The load placed at the top of the screw in a mechanical screw jack
is prevented from rotation by providing a swivelling mechanism. [IES-1993]
Reason (R): When the screw in a mechanical screw jack rotates, the load kept on top
of it moves axially up or down.
57. Ans. (d) In this case A is false but R is true.
the Lists:
List I List II [IAS-2007]
(Type of Thread) (Use)
A. Square thread 1. Used in vice
B. Acme thread 2. Used in lead screw
C. Buttress thread 3. Used in screw jack
D. Trapezoidal thread 4. Used in power transmission devices in machine tool
(a) 2 3 4 1 (b) 2 3 1 4
(c) 3 2 1 4 (d) 3 2 4 1
30. Ans. (c)
86. The diameter of tommy bar for a screw jack is designed for [IES-1999]
(a) bending moment due to effort applied
(b) torque on the tommy bar due to effort applied
(c) a percentage of axial loads
(d) some axial loads coupled with transverse loads
86. Ans. (a)
53. The load cup of a screw jack is made separate from the head of the spindle to
(a) enhance the load carrying capacity of the jack [IES-1995]
(b) reduce the effort needed for lifting the working load
(c) reduce the value of frictional torque required to be countered for lifting the load
(d) prevent the rotation of load being lifted.
53. Ans. (d) Load cup prevents the rotating of load.
72. Under service conditions involving jarring, vibration and pulsation of the working
load, the bolt of choice would
(a) short bolt with high rigidity (b) long bolt with increased elasticity
(c) bolt with a dished washer (d) bolt with castle nut [IES 2007]
Ans. (d)
97. If P is the pitch of a square thread, then the depth of thread d is given by
(a) 0.5 P (b) P (c) 1.5 P (d) 2.0 P
97. Ans. (a)
96. The frictional torque for square thread at mean radius while raising load is given
by [IES-1993]

(W = load; Ro = Mean Radius; ϕ = Angle of friction; α = Helix angle)
( ) tan( ) ( ) tan( ) ( ) tan ( ) tano o o oa WR b WR c WR d WRφ α φ α α φ− +
96. Ans. (b)
Self locking screw
91. What is the efficiency of a self-locking power screw?
[IES-2006; 1997; GATE-1994]
(a) 70% (b) 60% (c) 55% (d) < 50 %
91. Ans. (d)
65. To ensure self-locking in a screw jack it is essential that helix angle is
(a) larger than friction angle (b) smaller than friction angle. [IES-1996]
(c) equal to friction angle (d) such as to give maximum efficiency in lifting.
65. Ans. (b)
96. A screw jack is said to be self-locking if its efficiency is [IES-2002]
(a) less than 50% (b) equal to 50% (c) more than 50% (d) 100%
96. Ans. (a)
3.8 Self locking in power screw is better achieved by decreasing the helix angle and
increasing the coefficient of friction. [GATE-1995]
3.8 Ans. True
For self locking, angle of friction should be greater than helix angle of screw.
Efficiency of screw
54. The maximum efficiency of a screw jack having square threads with friction
angle φ is
[IES 2007]
(a)
)2/tan(1
)2/tan(1
ϕ
ϕ
+
−
(b)
ϕ
ϕ
tan1
tan1
+
−
(c)
ϕ
ϕ
sin1
sin1
+
−
(d)
)2/sin(1
)2/sin(1
ϕ
ϕ
+
−
Ans. (c)
111. Assertion (A): The maximum efficiency
1 sin
1 sin
φ
η
φ
⎛ ⎞−
=⎜ ⎟
+⎝ ⎠
of a screw jack is same,
where ɸ is the friction angle, for both motion up and motion down the plane. [IES-
2003]
Reason (R): The condition for the maximum efficiency for motion up and motion
down the plane is same, given by
4 2
π φ
α = − where α = helix angle.
111. Ans. (a)
9. Which one of the following is the value of helix angle for maximum efficiency of a
square threaded screw? [ 1
tanφ μ−
= ] [IES-2004]
(a) 45o
+ ɸ (b) 45o
- ɸ (c) 45o
- ɸ/2 (d) 45o
+ ɸ/2
9. Ans. (c)

1.14 The efficiency of a power screw is maximum when the lead angle is [GATE-
1997]
( ) ( ) ( ) ( )
2 2 2 2
r r
a b r c d r
π π
π π− − −
1.14 Ans. (a)
Collar friction
66. Stresses in a screw thread are estimated by considering the thread to be:
(a) long cantilever beam projecting from the pitch cylinder [IES-2006]
(b) long cantilever beam projecting from the root cylinder
(c) short cantilever beam projecting from the root cylinder
(d) short cantilever beam projecting from the pitch cylinder
66. Ans. (c)
108. For a composite consisting of a bar enclosed inside a tube of another material
when compressed under a load 'w' as a whole through rigid collars at the end of the
bar. The equation of compatibility is given by (suffixes 1 and 2) refer to bar and tube
respectively [IES-1998]
1 2 1 2
1 2 1 2
1 1 2 2 1 2 2 1
( ) ( ) . ( ) ( )
W W W W
a W W W b W W Const c d
A E A E A E A E
+ = + = = =
108. Ans. (a)

Design of power transmission system
Spur gear
1. The velocity ratio between pinion and gear in a gear drive is 2.3, the module of
teeth is 2.0 mm and sum of number of teeth on pinion and gear is 99.What is the
centre distance between pinion and the gear? [IES 2007]
(a) 49.5 mm (b) 99 mm (c) 148.5 mm (d) 198 mm
1. Ans. (b) Centre distance =
2
21 DD +
=
2
21 mTmT +
=
2
m
(T1+ T2) =
2
2
× 99 = 99mm
When two gears are meshing, the clearance is given by the
1. difference between dedendum of one gear and addendum of the mating gear.
2. difference between total and the working depth of a gear tooth.
3. distance between the bottom land of one gear and the top land of the mating gear.
4. difference between the radii of the base circle and the dedendum circle.
Which of these statements are correct?
(a) 1, 2 and 3 (b) 2, 3 and 4 (c) l. 3 and 4 (d) l. 2 and 4
2. Ans. (d)
3. The working surface above the pitch surface of the gear tooth is termed as
[IES-1998]
(a) addendum (b) dedendum (c) flank (d) face
3. Ans. (a)
4. Match the following
1
14
2
o
composite system gears [IES-1992]
List I List II
A. Dedendum 1.
2
pd
B. Clearance 2.
0.157
pd
C. Working depth 3.
1.157
pd
D. Addendum 4.
1
pd
(a) 1 2 3 4 (b) 4 3 2 1

(c) 3 2 1 4 (d) 3 1 2 4
4. Ans. (c)
the lists:
List I (Standard tooth/arms) List II (Advantages or disadvantages)
A. 20° and 25° systems 1. Results in lower loads on bearing
B. 14.5o
stub-tooth system 2. Broadest at the base and strongest in
bending
C. 25° Full depth system 3. Obsolete
D. 20° Full depth system 4. Standards for new applications [IES-1993]
(a) 4 3 2 1 (b) 3 1 2 4
(c) 3 2 1 4 (d) 4 2 3 1
5. Ans. (a)
6. Match List I (Terms) with List II (Definition) and select the correct answer using the
codes given below the lists: [IAS-2001]
List I List II
A. Module 1. Radial distance of a tooth from the pitch circle to the
top of the tooth
B. Addendum 2. Radial distance of a tooth from the pitch circle to the
bottom of the tooth
C. Circular pitch 3. Distance on the circumference of the pitch circle from a
point of one tooth to the corresponding point on the next tooth
4. Ratio of a pitch circle diameter in mm to the number of teeth
Codes: A B C A B C
(a) 4 1 3 (b) 4 2 3
(c) 3 1 2 (d) 3 2 4
7. Ans. (a)
8. Consider the following specifications of gears A, B, C and D: [IAS-2001]
Gears A B C D
Number of teeth 20 60 20 60
Pressure angle 114
2
o
114
2
o 20o
114
2
o
Module 1 3 3 1
Material Steel Brass Brass Steel
Which of these gears form the pair of spur gears to achieve a gear ratio of 3?
(a) A and B (b) A and D (c) B and C (d) C and D
8. Ans. (b)
For a gear pair i) module must be same
ii) pressure angle must be same.
9. If the number of teeth on the wheel rotating at 300 r.p.m. is 90, then the number of
teeth on the mating pinion rotating at 1500 r.p.m. is [IAS-2000]
(a) 15 (b) 18 (c) 20 (d) 60
9. Ans. (b)
Peripheral velocity (πDN) = constant. 1 1 2 2πD N = πD N and D= mT
1
1 1 1 1 2 1
2
300
90 18
1500
N
or mT N mT N or T T
N
π π= = × = × =

Or you may say speed ratio, 1 2
2 1
N T
N T
=
10. Match the type of gears with their most appropriate description. [GATE-2008]
Type of gear Description
P Helical 1. Axes non parallel and intersecting
Q Spiral 2. Axes parallel and teeth are inclined to the axis
R Hypoid 3. Axes parallel and teeth are parallel to the axis
S Rack and pinion 4. Axes are perpendicular and intersecting, and
teeth are inclined to the axis
5. Axes are perpendicular and used for large speed
reduction
6. Axes parallel and one of the gears has infinite radius
(A) P-2, Q- 4, R- I, S- 6 (C) P-2, Q- 6, R- 4, S- 2
(B) P-l, Q- 4, R- 5, S- 6 (D) P-6, Q- 3, R- I, S- 5
10. Ans. (A)
11. One tooth of a gear having 4 module and 32 teeth is shown in the figure. Assume
that the gear tooth and the corresponding tooth space make equal intercepts on the
pitch circumference. The dimensions 'a' and 'b', respectively, are closest to
[GATE-2008]
(A) 6.08 mm,4mm (B) 6.48mm,4.2mm (C) 6.28mm,4.3mm (d) 6.28mm, 4.1
11. Ans.(D)a= m.π =
12. Assertion (A): When one body drives another by direct contact, their contact
points must have equal components of velocity normal to the surfaces at the point of
contact.
Reason (R): Two points in the same body must have the same component of velocity
relative to the third body, in the direction of the line joining the two points.
[IES-1993]
12. Ans. (a)
13. A rack is a gear of [IAS-1998]
(a) infinite diameter (b) infinite module (c) zero pressure angle (d) large pitch
13. Ans. (a)
Classification of Gears
14. Match List I with List II and select the correct answer [IES-1996]
List I List II
A. Helical gears 1. Non-interchangeable
B. Herring bone gears 2. Zero axial thrust
C. Worm gears 3. Quiet motion

D. Hypoid Gears 4. Extreme speed reduction
(a) 1 2 3 4 (b) 3 2 1 4
(c) 3 1 4 2 (d) 3 2 4 1
14. Ans. (d)
15. Match List-l (Type of Gears) with List-II (Characteristics) and select the correct
answer using the code given below the Lists: [IES-2006]
List-I List -II
A. Helical gearing 1. Zero axial thrust
B. Herringbone gearing 2. Non-inter-changeable
C. Worm gearing 3. Skew shafts
D. Hypoid gearing 4. Parallel shafts
A B C D A B C D
(a) 4 1 3 2 (b) 3 2 4 1
(c) 4 2 3 1 (d) 3 1 4 2
15. Ans. (a)
the Lists:
List I List II
A. Worm gear 1. Imposes no thrust load on the shaft
B. Spur gear 2. To transmit power between two non-inter-
Secting shafts which are perpendicular to
each other
C. Herringbone gear 3. To transmit power when the shafts are
parallel
D. Spring level gear 4. To transmit power when the shafts are at
right
Angles to one another
Code: [IES 2007]
A B C D A B C D
(a) 1 2 3 4 (b) 2 3 1 4
(c) 1 2 4 3 (d) 2 3 4 1
16. Ans. (b)
17. Match List I (Type of Gear/Gear Train) with List II (Different Usage and Drive) and
select the correct answer using the code given below the Lists: [IES-2005]
List I List II
A Epicyclic gear train 1. Reduces end thrust
B. Bevel Gear 2. Low gear ratio
C. Worm-worm Gear 3. Drives non-parallel nonintersecting shafts
D. Herringbone Gear 4. Drives non-parallel intersecting shafts
5. High gear ratio
A B C D A B C D
(a) 5 4 3 1 (b) 2 3 4 5
(c) 5 3 4 1 (d) 2 4 3 5
17. Ans. (a)
18. Which type of gear is used for shaft axes having an offset? [IES-2004]
(a) Mitre gears (b) Spiral bevel gears (c) Hypoid gears (d) Zerol gears
18. Ans. (c)

19. The gears employed for connecting two non-intersecting and non-parallel, i.e.,
non-coplanar shafts are [IES-2003]
(a) Bevel gears (b) Spiral gears (c) Helical gears (d) Mitre gears
19. Ans. (b)
20. In a single reduction, a large velocity ratio is required. The best transmission is
[IES-1999]
(a) spur gear drive (b) helical gear drive
(c) bevel gear drive (d) worm gear drive
20. Ans. (a)
21. Which one of the following pairs is not correctly matched? [IES-1995]
(a) Positive drive .... Belt drive
(b) High velocity ratio .... Worm gearing
(c) To connect non-parallel and non- intersecting shafts .... Spiral gearing.
(d) Diminished noise and smooth operation .... Helical gears.
21. Ans. (a)
22. List I List II [GATE-1995]
(Gear types) (Applications)
(A) Worm gears 1. Parallel shafts
(B) Cross helical gears 2. Non-parallel, intersecting shafts
(C) Bevel gears 3. Non-parallel, non-intersecting shafts
(D) Spur gears 4. Large speed ratios
22. Ans. (A) - 4, (B) - 3, (C) - 2, (D) -1
23. Match the following
Type of gears Arrangement of shafts [GATE-2004]
P. Bevel gears 1. Non-parallel off-set shafts
Q. Worm gears 2. Non-parallel intersecting shafts
R. Herringbone gears 3. Non-parallel non-intersecting shafts
S. Hypoid gears 4. Parallel shafts
(a) P-4 Q-2 R-1 S-3 (b) P-2 Q-3 R-4 S-1
(c) P-3 Q-2 R-1 S-4 (d) P-1 Q-3 R-4 S-2
23. Ans. (b)
24. Assertion (A): While transmitting power between two parallel shafts, the noise
generated by a pair of helical gears is less than that of an equivalent pair of spur
gears. [IAS-2000]
Reason(R): A pair of helical gears has fewer teeth in contact as compared to an
equivalent pair of spur gears.
24. Ans. (c) In spur gears, the contact between meshing teeth occurs along the entire
face width of the tooth, resulting in a sudden application of the load which, in turn,
results in impact conditions and generates noise.
In helical gears, the contact between meshing teeth begins with a point on the
leading edge of the tooth and gradually extends along the diagonal line across the
tooth. There is a gradual pick-up of load by the tooth, resulting in smooth
engagement and silence operation.
25. Consider the following expressions for a spur gear: [IES-1995]
1. Addendum = 1/pd 2. Clearance = pc/20

3. Centre distance for internal gears = T1 + T2/2Pd 4. Dedendum = 1.157 pc/π
Of these correct expressions are
(a) 1, 2, 3 and 4 (b) 1 and 2 (c) 1, 2 and 3 (d) 1, 2 and 4
25. Ans. (*)
26. Spiral gears are used to connect: [IES-2005]
(a) Two parallel shafts (b) Two intersecting shafts
(c) Two non-parallel and non-intersecting shafts (d) None of the above
26. Ans. (c)
27. The motion transmitted between the teeth of two spur gears in mesh is generally
(a) sliding (b) rolling (c) rotary (d) party sliding and partly rolling
[IES-1999]
27. Ans. (a)
Mitres gear
28. Mitre gears [IES-1992]
(a) spur-gears with gear ratio 1: 1
(b) Skew gears connecting non-parallel and nonintersecting shafts
(c) Bevel gears transmitting power at more than or less than 90°
(d) Bevel gears in which the angle between the axes is and the speed ratio of the
gears is 90°
28. Ans. (d)
29. Match List-I (Gears) with List-II (Configurations) and select the correct answer
using the codes given below the Lists: [IES-2003]
List-I List-II
(Gears) (Configurations)
A Spur 1. Connecting two non-parallel or intersecting but coplanar shafts
B. Bevel 2. Connecting two parallel and coplanar shafts with teeth parallel to the
axis of the gear wheel
C. Helical 3. Connecting two parallel and coplanar shafts with teeth inclined to the
axis of the gear wheel
D. Mitre 4. Connecting two shafts whose axes are mutually perpendicular to each
other
(a) 2 4 3 1 (b) 3 1 2 4
(c) 2 1 3 4 (d) 3 4 2 1
29. Ans. (c)
Pitch point
30. Gearing contact is which one of the following? [IES 2007]
(a) Sliding contact (b) Sliding contact, only rolling at pitch point
(c) Rolling contact (d) Rolling and sliding at each point of contact
30. Ans. (d)
31. When two spur gears having involute profiles on, their teeth engage, the line of
action is tangential to the [IES-2003]
(a) Pitch circles (b) Dedendum circles
(c) Addendum circles (d) Base circles
31. Ans. (a)

Pressure angle
32. The pressure angle of a spur gear normally varies from [IAS-2000]
(a) 14° to 20° (b) 20° to 25° (c) 30° to 36° (d) 40° to 50°
32. Ans. (a)
33. What is the value of pressure angle generally used for involute gears? [IES-2006]
(a) 35° (b) 30° (c) 25 ° (d) 20°
33. Ans. (d)
34. For involute gear, the ratio, patch circle radius/base radius is (φ is the pressure
angle)
(a) sinφ (b) cos φ (c) secφ (d) cosecφ
34. Ans. (c)
35. For a spring-loaded roller-follower driven with a disc earn, [GATE-2001]
(a) the pressure angle should be larger during rise than that during return for ease of
transmitting motion.
(b) the pressure angle should be smaller during rise than that during return for ease
of transmitting motion.
(c) the pressure angle should be large during rise as well as during return for ease of
transmitting motion.
(d) the pressure angle does not affect the ease of transmitting motion.
35 Ans. (c)
36. Consider the following, modifications regarding avoiding the interference between
gears:
1. The centre distance between meshing gears be increased [IES-2003]
2. Addendum of the gear be modified
3. Teeth should be undercut slightly at the root
4. Pressure angle should be increased
5. Circular pitch be increased
Which of these are effective in avoiding interference?
(a) 1, 2 and 3 (b) 2, 3, 4 and 5 (c) 1, 4 and 5 (d) 3, 4
and 5
36. Ans. (b)
37. Assertion (A): An involute rack with 20° pressure angle meshes with a pinion of
14.5° pressure angle. [IES-2002]
Reason (R): Such a matching is impossible.
37. Ans. (d)
38. Compared to gears with 200
pressure angle involute full depth teeth, those with
200
pressure angle and stub teeth have
[IES 2007]
1. smaller addendum. 2. smaller dedendum.
3. smaller tooth thickness. 4. greater bending strength.
(a) 1, 2 and 3 (b) 1, 2 and 4

(c) 1, 3 and 4 (d) 2, 3 and 4
38. Ans. (c)
A pinion of
1
14
2
o
pressure angle and 48 involute teeth has a pitch circle diameter of
28.8 cm. It has
1. module of 6 mm 2. circular pitch of 18 mm
3. addendum of 6 mm4. diametral pitch of
11
113
(a) 2 and 3 (b) 1 and 3 (c) 1 and 4 (d) 2 and 4
39. Ans. (b) Module =
d 288
= =6mm
T 48
Circular pitch = 6 = 18.84 mm ; addendum 1 module 6 mm
1
diametral pitch =
6
d
T
T
d
π
π= × = =
=
Circular pitch = - = 1t X 6 = 18.84 mm
40. Which of the following statements are correct? [IES-1996]
1. For constant velocity ratio transmission between two gears, the common normal at
the point of contact must always pass through a fixed point on the line joining the
centres of rotation of the gears.
2. For involute gears the pressure angle changes with change in centre distance
between gears.
3. The velocity ratio of compound gear train depends upon the number of teeth of the
input and output gems only.
4. Epicyclic gear trains involve rotation of at least one gear axis about some other
gear axis.
(a) 1, 2 and 3 (b) 1, 3and 4 (c) 1, 2 and 4 (d) 2, 3 and 4
40. Ans. (c)
41. Which one of the following is true for involute gears? [IES-1995]
(a) Interference is inherently absent
(b) Variation in centre distance of shafts increases radial force
(c) A convex flank is always in contact with concave flank
(d) Pressure angle is constant throughout the teeth engagement.
41. Ans. (d) For involute gears, the pressure angle is constant throughout the teeth
engagement.
42. In involute gears the pressure angle is [IES-1993]
(a) dependent on the size of teeth (b) dependent on the size of gears
(c) always constant (d) always variable
42. Ans. (c) The pressure angle is always constant in involute gears.

Backlash
Minimum Number of Teeth
Certain minimum number of teeth on the involute pinion is necessary in order to
(a) provide an economical design (b) avoid Interference
(c) reduce noise in operation (d) overcome fatigue failure of the teeth
43. Ans. (b)
44. A certain minimum number of teeth is to be kept for a gear wheel [IES-1999]
(a) so that the gear is of a good size (b) for better durability
(c) to avoid interference and undercutting (d) for better strength
44. Ans. (c)
45. Minimum number of teeth for involute rack and pinion arrangement for pressure
angle of 20° is [IAS-2001]
(a) 18 (b) 20 (c) 30 (d) 34
45. Ans. (a) min min2 2
2 2 1
17.1 17 So 18
sin sin 20
f
o
h
T as T
θ
×
= = = > =
46. The minimum number of teeth on the pinion to operate without interference in
standard full height involute teeth gear mechanism with 20° pressure angle is
[GATE-2002]
(a) 14 (b) 12 (c) 18 (d) 32
46. Ans. (c)
the lists:
List I (Terminology) List II (Relevant terms) [IES-1995]
A. Interference 1. Arc of approach, arc of recess, circular pitch
B. Dynamic load on tooth 2. Lewis equation
C. Static load 3. Minimum number of teeth on pinion
D. Contract ratio 4. Inaccuracies in tooth profile
(a) 3 4 1 2 (b) 1 2 3 4
(c) 4 3 2 1 (d) 3 4 2 1
47. Ans. (d)
48. In full depth
1
14
2
o
degree involute system, the smallest number of teeth in a
pinion which meshes with rack with out interference is [IES-1992]
(a) 12 (b) 16 (c) 25 (d) 32
48. Ans. (d)
49. Assertion (A): When a pair of spur gears of the same material is in mesh, the
design analysis is based on the smaller wheel.
[IES-1993]
Reason (R): For a pair of gears of the same material in mesh "the strength factor" of
the smaller wheel is less than that of the larger wheel.

49. Ans. (c) A is true but R is false because strength factor is function of module and
is same for gear and pinion. It is due to more wear of pinion that-design analysis is
based on the smaller wheel.
Forms of teeth
Cycloidal teeth
50. The curve traced by a point on the circumference of a circle which rolls along the
inside of affixed circle, is known as [IES-1992]
(a) epicycloid (b) hypocycloid (c) cardiod (d) involute
50. Ans. (b)
51. The tooth profile most commonly used in gear drives for power transmission is
[IAS-1996]
(a) A cycloid (b) An involute (c) An ellipse (d) A parabola
51. Ans. (b) It is due to easy manufacturing.
52.
In the mechanism shown above, link 3 has [IES-2004]
(a) curvilinear translation and all points in it trace out identical cycloids
(b) curvilinear translation and all points in it trace out identical involutes
(c) linear translation & all points in it trace out identical helices
(d) linear translation & all points in it trace out identical ellipses
52. Ans. (a)
53. A thin circular disc is rolling with a uniform linear speed, along a straight path on
a plane surface. [IES-1994]
Consider the following statements in this regard:
1. All points on the disc have the same velocity.
2. The centre of the disc has zero acceleration.
3. The centre of the disc has centrifugal acceleration.
4. The point on the disc making contact with the plane surface has zero
acceleration.
Of these statements
(a) 1 and 4 are correct (b) 3 and 4 are correct (c) 3 alone is correct (d)
2 alone is correct.
53. Ans. (d)

Involute teeth
54. In spur gears having involute teeth, the product of circular pitch and diametral
pitch is……. [GATE-1994]
54. Ans. π
55. In the case of an involute toothed gear, involute starts from [IES-1997]
(a) addendum circle (b) dedendum circle (c) pitch circle (d) base circle
55. Ans. (d) Involute can't exist below base circle.
56. An involute pinion and gear are in mesh. If both have the same size of
addendum, then there will be an interference between the [IES-1996]
(a) tip of the gear tooth and flank of pinion. (b) tip of the pinion and flank of gear.
(c) flanks of both gear and pinion. (d) tips of both gear and pinion.
56. Ans. (a)
1. A stub tooth has a working depth larger than that of a full-depth tooth.
2. The path of contact for involute gears is an arc of a circle.
(a) Only 1 (b) Only 2 (c) Both 1 and 2 (d) Neither 1 nor 2
57. Ans. (d) 1. A stub tooth has a working depth lower than that of a full-depth tooth.
2. The path of contact for involute gears is a line.
58. Consider the following statements regarding the choice of conjugate teeth for the
profile of mating gears: [IES-1999]
1. They will transmit the desired motion 2. They are difficult to manufacture.
3. Standardisation is not possible 4. The cost of production is low.
58. Ans. (a) Cost of production of conjugate teeth, being difficult to manufacture is
high.
Contact ratio
59. Which one of the following is the correct statement?
In meshing gears with involute gears teeth, the contact begins at the intersection of
the
(a) Line of action and the addendum circle of the driven gear
(b) Line of action and the pitch circle of the driven gear [IES 2007]
(c) Dedendum circle of the driver gear and the addendum circle of the driven gear
(d) Addendum circle of the driver gear and the pitch circle of the driven gear
59. Ans. (c)
60. Which one of the following statements is correct? [IAS-2007]
(a) Increasing the addendum results in a larger value of contact ratio
(b) Decreasing the addendum results in a larger value of contact ratio
(c) Addendum has no effect on contact ratio
(d) Both addendum and base circle diameter have effect on contact ratio
60. Ans. (d) contact ratio=
tanlengthof areof con t
circular pitch

=
2 2
2 2 2 2
cos cos ( )sin
(cos )
A A
c
R R r r R r
P
θ θ θ
θ
− + − − +
61. The contact ratio of the contacting tooth is [GATE-2007]
(a) 1.21 (b) 1.25 (c) 1.29 (d) 1.33
61. Ans. (d)
62. The velocity of sliding of meshing gear teeth is [IAS-2002]
(a)( )1 2 xω ω× (b) 1
2
x
ω
ω
(c) ( )1 2 xω ω+ (d)
( )1 2
x
ω ω+
(Where ω1 and ω2 = angular velocities of meshing gears
x = distance between point of contact and the pitch point)
62. Ans. (c)
Interference
63. In gears, interference takes place when [IES-1993]
(a) the tip of a tooth of a mating gear digs into the portion between base and root
circles
(b) gears do not move smoothly in the absence of lubrication
(c) pitch of the gear is not same (d) gear teeth are undercut
63. Ans. (a) In gears, interference takes place when the tip of a tooth of a mating
gear digs into the portion between base .and root circle.
64. For spur with gear ratio greater than one, the interference is most likely to occur
near the
(a) pitch point (b) point of beginning of contact [IAS-1997]
(c) point of end of contact (d) root of the tooth
64. Ans. (d)
65. Interference in a pair of gears is avoided, if the addendum circles of both the
gears intersect common tangent to the base circles within the points of tangency.
[GATE-1995]
65. Ans. True
66. Interference between the teeth of two meshing involute gears can be reduced or
eliminated by
1. Increasing the addendum of the gear teeth and correspondingly reducing
the
addendum of the pinion.
2. Reducing the pressure angle of the teeth of the meshing gears.
3. Increasing the centre distance
[IES 2007]
(a) 1 and 2 (b) 2 and 3
(c) 1 only (d) 3 only
66. Ans. (b)
A 20o
stub tooth system is generally preferred in spur gears as it results in
1. stronger teeth 2. lesser number of teeth on the pinion

3. lesser changes of surface fatigue failure 4. reduction of interference
Which of the above statements are correct?
(a) 1, 2 and 4 (b) 3 and 4 (c) 1 and 3 (d) 1, 2, 3 and 4
67. Ans. (a)
below the lists:
List-I List-II [IES-2001]
A. Undercutting 1. Beam strength
B. Addendum 2. Interference
C. Lewis equation 3. Large speed reduction
D. Worm and wheel 4. Intersecting axes
5. Module
(a) 2 5 1 3 (b) 1 5 4 3
(c) 1 3 4 5 (d) 2 3 1 5
68. Ans. (a)
69. Which one of the following pairs is correctly matched? [IES-1999]
(a) Governors ... Interference (b) Gears …….Hunting
(c) Klein's construction .... Acceleration of piston (d) Cam …….Pinion
69. Ans. (c)
70. Consider the following characteristics: [IES-1998]
1. Small interference 2. Strong tooth.
3. Low production cost 4. Gear with small number of teeth.
Those characteristics which are applicable to Stub 20° involute system would include
(a) 1 alone (b) 2, 3 and 4 (c) 1, 2 and 3 (d) 1, 2, 3 and 4
70. Ans. (d)
71. How can interference in involute gears be avoided? [IAS-2007]
(a) Varying the centre distance by changing the pressure angle only
(b) Using modified involute or composite system only
(c) Increasing the addendum of small wheel and reducing it for the larger wheel only
(d) Any of the above
71. Ans. (d)
72. Which one of the following statements in respect of involute profiles for gear teeth
is not correct?
(a) Interference occurs in involute profiles,
(b) Involute tooth form is sensitive to change in centre distance between the base
circles.
(c) Basic rack for involute profile has straight line form
(d) Pitch circle diameters of two mating involute gears are directly proportional to the
base circle diameter [IAS-2003]
72. Ans. (b)
73. Assertion (A): In the case of spur gears, the mating teeth execute pure rolling
motion with respect to each other from the commencement of engagement to its
termination. [IAS-2003]
Reason (R): The involute profiles of the mating teeth are conjugate profiles which
obey the law of gearing.
73. Ans. (a)

74. Assertion (A): Gears with involute tooth profile transmit constant velocity ratios
between shafts connected by them. [IAS-1997]
Reason (R): For involute gears, the common normal at the point of contact between
pairs of teeth always passes through the pictch point.
74. Ans. (a)
75. Twenty degree full depth involute profiled 19-tooth pinion and 37-tooth gear are in
mesh. If the module is 5 mm, the centre distance between the gear pair will be
[GATE-2006]
(a) 140 mm (b) 150 mm (c) 280 mm (d) 300 mm
75. Ans. (a)
Face Width
Beam Strength of Gear Tooth
76. In heavy-duty gear drives, proper heat treatment of gears is necessary in order
to:
(a) avoid interference (b) prevent noisy operation [IES-2006]
(c) minimize wear of gear teeth
(d) provide resistance against impact loading on gear teeth
76. Ans. (d)
77. Consider the following statements pertaining to the basic Lewis equation for the
strength design of spur gear teeth: [IES-2005]
1. Single pair of teeth participates in power transmission at any instant.
2. The tooth is considered as a cantilever beam of uniform strength.
3. Loading on the teeth is static in nature.
4. Lewis equation takes into account the inaccuracies of the tooth profile.
5. Meshing teeth come in contract suddenly.
(a) 1, 3, 4 and 5 b) 1,2, 3 and 4(c) 1, 2 and 3 (d) 2, 4 and 5
77. Ans. (c)
78. In the formulation of Lewis equation for toothed gearing, it is assumed that
tangential tooth load Ft, acts on the [IES-1998]
(a) pitch point (b) tip of the tooth (c) root of the tooth (d) whole face of the tooth
78. Ans. (b)
79. Assertion (A): The Lewis equation for gear tooth with involute profile predicts the
static load capacity of cantilever beam of uniform strength. [IES-1994]
Reason (R): For a pair of meshing gears with involute tooth profile, the pressure
angle and module must be the same to satisfy the condition of interchangeability.
79. Ans. (b) Both A and R are true, but R is not right explanation for A.
80. Assertion (A): When a pair of spur gears of the same material is in mesh, the
design is based on pinion. [IES-2002]

Reason (R): For a pair of gears of the same material in mesh, the 'strength factor' of
the pinion is less than that of the gear.
80. Ans. (a)
81. The dynamic load on a gear is due to [IES-2002]
1. inaccuracies of tooth spacing 2. irregularities in tooth profile
3. deflection of the teeth under load
4. type of service (i.e. intermittent, one shift per day, continuous per day).
Which of the above statements are correct?
(a) 1. 2 and 3 (b) 2, 3 and 4 (c) 1, 3 and 4 (d) 1, 2 and 4
81. Ans. (a)
82. Consider the following statements:
The form factor of a spur gear tooth depends upon the [IES-1996]
1. number of teeth 2. pressure angle
3. addendum modification coefficient 4. circular pitch
Of these correct statements are
(a) 1 and 3 (b) 2 and 4 (c) 1, 2 and 3 (d) 1 and 4
82. Ans. (c)
83. Assertion (A): If the helix angle of a helical gear is increased, the load carrying
capacity of the tooth increases. [IES-1996]
Reason (R): The form factor of a helical gear increases with the increasing in the
helix angle.
83. Ans. (a)
the Lists:
A. Unwin's formula 1. Bearings
B. Wahl factor 2. Rivets
C. Reynolds’s equation 3. Gears
D. Lewis form factor 4. Springs
(a) 1 4 2 3 (b) 2 3 1 4
(c) 1 3 2 4 (d) 2 4 1 3
84. Ans. (d)
85. A spur gear has a module of 3 mm, number of teeth 16, a face width of 36 mm
and a pressure angle of 20°. It is transmitting a power of 3 kW at 20 rev/s. Taking a
velocity factor of 1.5, and a form factor of 0.3, the stress in the gear tooth is about
[GATE-2008]
(A) 32 MPa (B) 46 MPa (C) 58 MPa (D) 70MPa
85. Ans. (C)
Wear Strength of Gear Tooth
86. The limiting wear load of spur gear is proportional to (where Ep = Young's
modulus of pinion material; Eg = Young's modulus of gear material) [IES-1997]
( )( ) ( ) ( ) ( )
1
a b c 1 d 1
p g p g
p g
p g g p
E E E E
E E
E E E E
− ⎛ ⎞ ⎛ ⎞ ⎛ ⎞+
+ + +⎜ ⎟ ⎜ ⎟ ⎜ ⎟⎜ ⎟ ⎜ ⎟ ⎜ ⎟
⎝ ⎠ ⎝ ⎠ ⎝ ⎠
86. Ans. (b)

Gear Lubrication
87. Match List I (Types of gear failure) with List II (Reasons) and select the correct
answer using the codes given below the Lists [IES-2004]
List I List II
A. Scoring 1. Oil film breakage
B. Pitting 2.Yielding of surface under heavy loads
C. Scuffing 3. Cyclic loads causing high surface stress
D. Plastic flow 4. Insufficient lubrication
A B C D A B C D
(a) 2 1 3 4 (b) 2 3 1 4
(c) 4 3 1 2 (d) 4 1 3 2
87. Ans. (c)
Simple Gear train
88. In a simple gear train, if the number of idler gears is odd, then the direction or
motion of driven gear will
(a) be same as that of the driving gear [IES-2001]
(b) be opposite to that of the driving gear
(c) depend upon the number of teeth on the driving gear
(d) depend upon the total number of teeth on all gears of the train
88. Ans. (a)
89. The gear train usually employed in clocks is a [IES-1995]
(a) reverted gear train (b) simple gear train
(c) sun and planet gear (d) differential gear.
89. Ans. (b) Reverted gear train is used in clocks.
90. In the figure shown above, if the
speed of the input shaft of the spur gear
train is 2400 rpm and the speed of the
output shaft is 100 rpm, what is the
module of the gear 4?
(a) 1.2 (b) 1.4
(c) 2 (d) 2.5
[IES-2005]
90. Ans. (b)
( )
2 1
2
2
1 i 3
1
3 3 32
4 i 4
4 1 4 4
3 4
mT mT
35
2
or T 10
T
N N N
T
N T TT 10 10
N N or 100 2400 or T 40
T T T 60 T
m T m T 70
35 or m 1.4
2 40 10
+
=
=
= − × =
−
= = + × × = × × =
′ ′+
′= = =
+
91. In a machine tool gear box, the smallest and largest spindles are 100 rpm and
1120 rpm respectively. If there are 8 speeds in all, the fourth speed will be[IES-2002]
(a) 400 rpm (b) 280 rpm (c) 800 rpm (d) 535 rpm
91. Ans. (b)

92. A fixed gear having 200 teeth is in mesh with another gear having 50 teeth. The
two gears are connected by an arm. The number of turns made by the smaller gear
for one revolution of arm about the centre of the bigger gear is [IES-1996]
(a)
2
4
(b) 3 (c) 4 (d) 5
92. Ans. 1 + 200/50 = 1 + 4 = 5
Note: - Common Data for Questions 93 - 94.
A gear set has a opinion with 20 teeth and a gear with 40 teeth. The pinion runs at 30
rev/s and transmits a power of 20 kW. The teeth are on the 20° full –depth system
and have module of 5 mm. The length of the line of action is 19 mm.
93. The center distance for the above gear set in mm is [GATE-2007]
(a) 140 (b) 150 (c) 160 (d) 170.
93. Ans. (b)
94. The resultant force on the contacting gear tooth in N is: [GATE-2007]
(a) 77.23 (b) 212.20 (c) 225.80 (d) 289.43
94. Ans. (c)
Compound gear train
95. The velocity ratio in the case of the compound train of wheels is equal to
[IES-2000]
No.of teeth on first driver No.of teeth on last follower
(a) (b)
No.of teeth on last follower No.of teeth on first driver
Productof teeth on the drivers Productof te
(c) (d)
Productof teeth on the followers
eth on the followers
Productof teeth on the drivers
95. Ans. (c)
96. Consider the gear train
shown in the given figure
and table of gears and their
number of teeth.
Gear :A B C D E
F
No of teeth:20 50 25 75
26 65
[IES-1999]
Gears BC and DE are moulded on parallel shaft rotating together. If the speed of A is
975 r.p.m., the speed of F will be
(a) 39 r.p.m. (b) 52 r.p.m. (c) 75 r.p.m. (d) 75 r.p.m
96. Ans. (b)
Speed ratio
20 25 26 4 4
975 52
50 75 65 75 75
A C EF
F
A B D F
T T TN
or N rpm
N T T T
× × × ×
= = = = × =
× × × ×

97. A compound train consisting of spur, bevel
and spiral gears are shown in the given figure
along with the teeth numbers marked against the
wheels. Over-all speed ratio of the train is
(a) 8 (b) 2
(c)
1
2
(d)
1
8
[IES-1996]
97. Ans. (a)
98. There are six gears A, B, C, D, E, F in a compound train. The numbers of teeth in
the gears are 20, 60, 30, 80, 25 and 75 respectively. The ratio of the angular speeds
of the driven (F) to the driver (A) of the drive is
(a)
1
24
(b)
1
8
(c)
4
15
(d) 12[IAS-1995]
98. Ans. (a)
99. In the compound gear train shown in
the above figure, gears A and C have
equal numbers of teeth and gears B and D
have equal numbers of teeth. When A
rotates at 800 rpm, D rotates at 200
rpm.The rotational speed of compound
gears BC would then be
(a) 300 rpm (b) 400rpm
(c) 500 rpm (d) 600rpm
[IES 2007]
99. Ans. (b) From the figure rA+ rB = rC +rD or TA +TB =TC+TD and as NB+NC it must
be TB =TD & TA=TC
Or
A
B
N
N
=
C
D
N
N
or NC = DA NN = 200800× = 400rpm [ BN∵ = ]cN
Data for Q 100-101 are given below. Solve the problems and choose correct
answers.

A compacting machine shown in the
figure below is used to create a desired
thrust force by using a rack and pinion
arrangement. The input gear is
mounted on tile motor shaft. The gears
have involute teeth of 2 mm module.
[GATE-2004]
100. If the drive efficiency is 80%, then torque required on the input shaft to create
1000 N output thrust is [GATE-2004]
(a) 20 Nm (b) 25 Nm (c) 32 Nm (d) 50 Nm
100. Ans. (b)
101. If the pressure angle of the rack is 20°, then force acting along the line of action
between the rack and the gear teeth is [GATE-2004]
(a) 250 N (b) 342 N (c) 532 N (d) 600 N
101. Ans. (c)
Reverted gear train
102. Consider the following statements in case of reverted gear train: [IES-2002]
1. The direction of rotation of the first and the last gear is the same.
2. The direction of rotation of the first and the last gear is opposite.
3. The first and the last gears are on the same shaft.
4. The first and the last gears are on separate but co-axial shafts.
Which of these statements is/are correct?

102. Ans. (d)
103. A reverted gear train is one in which the output shaft and input shaft [IES-1997]
(a) rotate in opposite directions (b) are co-axial
(c) are at right angles to each other (d) are at an angle to each other
103. Ans. (b)
104. In a reverted gear train, two gears P and Q are meshing, Q - R is a compound
gear, and R and S are meshing. The modules of P and R are 4mm and 5mm
respectively. The numbers of teeth in P, Q and R are 20, 40 and 25 respectively. The
number of teeth in S is [IES-2003]
(a) 23 (b) 35 (c) 50 (d) 53
104. Ans. (b)
P Q R G
P Q R S
1 P Q 2 R S
S
S
Summation of radius will be constant
R +R =R +R
or D + D = D + D
or m (T + T ) = m (T + T )
or 4 (20 + 40) = 5 (25 + T )
or T =23
105. Two shafts A and B, in the same straight line are geared together through an
intermediate parallel shaft. The parameters relating to the gears and pinions are
given in the table: [IES-2003]
Item Speed Teeth PCD Module
Driving wheel A
Driven wheel B
Driven wheel C on the intermediate shaft
Driving wheel D on the intermediate shaft, in mesh
with B
NA
NB
NC
ND
TA
TB
TC
TD
DA
DB
DC
DD
m
m
m
m
(a) CA B
B A D
TN T
N T T
= × (b) A A D
B C B
N T T
N T T
= ×
(c) A C B DD D D D+ = + (d) A C B DT T T T+ = +
105. Ans. (b)
A C B D
A C B D
(i) D + D = D + D
(ii) mT + mT = mT + mT
(iii) C CA A B
B C B A D
N TN N T
N N N T N
= × = ×
Data for Q. 106 - 107 are given below. Solve the problems and choose correct
answers.
The overall gear ratio in a 2 stage speed reduction gear box (with all spur gears) is
12. The input and output shafts of the gear box are collinear. The countershaft which
is parallel to the input and output shafts has a gear (Z2 teeth) and pinion (Z3 = 15

teeth) to mesh with pinion (Z1 = 16 teeth) on the input shaft and gear (Z4 teeth) on the
output shaft respectively. It was decided to use a gear ratio of 4 with 3 module in the
first stage and 4 module in the second stage.
106. Z2 and Z4 are [GATE-2003]
106. Ans. (a)
107. The centre distance in the second stage is [GATE-2003]
(a) 90 mm (b) 120 mm (c) 160 mm (d) 240mm
107. Ans. (b)
Epicyclic gear train
108. If the annular wheel of an epicyclic gear train has 100 teeth and the planet
wheel has 20 teeth, the number of teeth on the sun wheel is [IES-2003]
(a) 80 (b) 60 (c) 40 (d) 20
108. Ans. (b) From geometry
2
2
2 100 2 20 60
p s A
p s A
s A p
d d d
or T T T
orT T T
+ =
+ =
= − = − × =

109. In the epicyclic gear train shown in the given figure, A
is fixed. A has 100 teeth and B has 20 teeth. If the arm C
makes three revolutions, the number of revolutions made
by B will be
(a) 12
(b) 15
(c) 18
(d) 24
[IES-1997]
109. Ans. (c) For 1 revolution of C,
100
1 1 6 for3revolution, 6 3 18
20
A
B D
B
T
N N
T
= + = + = ∴ = × =
110. A fixed gear having 100 teeth meshes with another gear having 25 teeth, the
centre lines of both the gears being joined by an arm so as to form an epicyclic gear
train. The number of rotations made by the smaller gear for one rotation of the arm
is[IAS-1995]
(a) 3 (b) 4 (b) 5 (d) 6
110. Ans. (c)
111. The arm OA of an epicyclic gear train shown in figure revolves counter
clockwise about O with an angular velocity of 4 rad/s. Both gears are of same size.
Tire angular velocity of gear C, if the sun gear B is fixed, is [GATE-1995]
111. Ans. (b)
112. An epicyclic gear train has 3 shafts A, Band C, A is an input shaft running at 100
rpm clockwise. B is an output shaft running at 250 rpm clockwise. Torque on A is 50
kNm (clockwise). C is a fixed shaft. The torque to fix C [IES-2002]
(a) is 20 kNm anticlockwise (b) is 30 kNm anticlockwise
(c) is 30 kNm clockwise (d) cannot be determined as the data is
insufficient
112. Ans. (b)

113. The sun gear in the figure is driven clockwise at 100
rpm. The ring gear is held stationary.
For the number of teeth shown on the gears, the arm
rotates at
(a) 0 rpm (b) 20 rpm
(c) 33.33 rpm (d) 66.67 rpm [GATE-2001]
113. Ans. (b)
.
114. A single epicyclic gear train is shown in the given figure.
Wheel A is stationary. If the number of teeth on A and Bare 120
and 45 respectively, then when B rotates about its own axis at
100 rpm, the speed of C would be
(a) 20 rpm (b) 27
3
11
rpm
(c) 19
7
11
rpm (d) 100 rpm [IES-1994]
114. Ans. (b)
115. Two mating spur gears have 40 and 120 teeth respectively. The pinion rotates
at 1200 rpm and transmits a torque of 20 Nm. The torque transmitted by the gear is
[GATE-2004]
(a) 6.6 Nm (b) 20 Nm (c) 40 Nm (d) 60Nm
115. Ans. (d)

116. For an epicyclic gear train, the input torque = 100 Nm. RPM of the input gear is
1000 (clockwise), while that of the output gear is 50 RPM (anticlockwise). What is the
magnitude of the holding torque for the gear train? [IAS-2007]
(a) Zero (b) 500 Nm (c) 2100 Nm (d) None of the above
116. Ans. (c) Ti+To+Tarm=0 and 0i i o o arm armT T Tω ω ω+ + = Gives
Tarm=Ti
1000
1 1 100 1 2100
50
i i
i
o o
N
T Nm
N
ω
ω
⎛ ⎞ ⎛ ⎞ −⎛ ⎞
− = − = × − =−⎜ ⎟ ⎜ ⎟ ⎜ ⎟
⎝ ⎠⎝ ⎠ ⎝ ⎠
117. In the figure shown, the sun wheel has 48 teeth
and the planet has 24 teeth. If the sun wheel is
fixed, what is the angular velocity ratio between the
internal wheel and arm?
(a) 3.0
(b) 1.5
(c) 2.0
(d) 4.0
[IAS-2004]
117. Ans. (a) 0B C A
A
A C B
N N T
N
N N T
−
= − =
−
∵
48
1 2 2 1 3
24
B C B B
C C C
N N N N
or or
N N N
−
= − − + = − = + =
−
118. 100 kW power is supplied to the machine through a gear box which uses an
epicyclic gear train. The power is supplied at 100 rad/s. The speed of the output shaft
of the gear box is 10 rad/s in a sense opposite to the input speed. What is the holding
torque on the fixed gear of the train? [IAS-2004]
(a) 8 kNm (b) 9 kNm (c) 10 kNm (d) 11 kNm
118. Ans. (b) T1+T2+T3=0
T1W1+T2W2+T3W3=0
W3=0
T1W1=100kW, W1=100rad/s
∵ T1=1 k Nm
Or T2=
( )
1 1
2
100
10
10
TW
kNm
W
−
− = = −
( )3 2 1 10 1 9T T T kNm= − − = − − − =

119. In the epicyclic gear train shown in
the figure, TA = 40, TB = 20. For three
revolutions of the arm, the gear B will
rotate through
(a) 6 revolutions
(b) 2.5 revolutions
(c) 3 revolutions
(d) 9 revolutions
[IAS-2003]
Common Data for Questions 120, 121:
A planetary gear train has four gears and one carrier. Angular velocities of the gears
are ω1, ω2, ω3, and ω4 respectively. The carrier rotates with angular velocity ω5,
120. What is the relation between the angular velocities of Gear 1 and Gear 4?

[GATE-2006]
120. Ans. (a)
121. For (ω1 = 60 rpm clockwise (cw) when looked from the left, what is the angular
velocity of the carrier and its direction so that Gear 4 rotates in counter clockwise
(ccw) direction at twice the angular velocity of Gear 1 when looked from the left?
[GATE-2006]
(a) 130 rpm, cw (b) 223 rpm, ccw (c) 256 rpm, cw (d) 156
rpm, ccw
121. Ans. (d)
Helical Gears
Terminology of Helical Gears
122. If α = helix angle, and pc = circular pitch; then which one of the following
correctly expresses the axial pitch of a helical gear?
(a) pc cosα (b)
αcos
cp
(c)
αtan
cp
(d) pc sin α [IES 2007]
122. Ans. (c)
123. A helical gear has the active face width equal to b, pitch p and helix angle α.
What should be the minimum value of b in order that contact IS maintained across
the entire active face of the gear? [IES-2004]
(a) cosp α (b) secp α (c) tanp α (d) cotp α

123. Ans. (d)
P
b
tanα
≥
124. Assertion (A): Helical gears are used for transmitting motion and power between
intersecting shafts, whereas straight bevel gears arc used for transmitting motion and
power between two shafts intersecting each other at 90o
. [IES-2000]
Reason (R): In helical gears teeth are inclined to axis of the shaft and arc in the form
or a helix.
Whereas in bevel gears, teeth arc tapered both in thickness and height form one end
to the other.
124. Ans. (b)
125. Assertion (A): Shafts supporting helical gears must have only deep groove ball-
bearings.
Reason (R): Helical gears produce axial thrusts. [IES-1999]
125. Ans. (a)
126. Assertion (A): Crossed helical gears for skew shafts are not used to transmit
heavy loads.
Reason (R) The gears have a point contact, and hence are not considered strong.
[IES-1995]
126. Ans. (a) Crossed helical gears for skew shafts are not used to transmit heavy
loads because gears have point contact and are not strong.
Virtual Number of Teeth
Bevel Gears
127. In a differential mechanism, two equal sized bevel wheels A and B are keyed to
the two halves of the rear axle of a motor car. The car follows a curved path. Which
one of the following statements is correct? [IES-2004]
The wheels A and B will revolve at different speeds and the casing will revolve at a
speed which is equal to the
(a) difference of speeds of A and B (b) arithmetic mean of speeds of A and
B
(c) geometric mean of speeds of A and B (d) harmonic mean of speeds of A and B
127. Ans. (b)
128. Assertion (A): Spiral bevel gears designed to be used with an offset in their
shafts are called ‘hypoid gears’ [IAS-2004]
Reason (R): The pitch surfaces of such gears are hyperboloids of revolution.
128. Ans. (a)
Worm Gears
Worm Gears 600
129. If reduction ratio of about 50 is required in a gear drive, then the most
appropriate gearing would be [IAS-1999]
(a) spur gears (b) bevel gears (c) double helical gears (d) worm and worm
wheel
129. Ans. (d)

130. Large speed reductions (greater than 20) in one stage of a gear train are
possible through
(a) Spur gearing (b) Worm gearing (c) Bevel gearing (d) Helical gearing
[GATE-2002]
130. Ans. (b)
131. A 1.5 kW motor is running at 1440 rev/min. It is to be connected to a stirrer
running at 36 rev /min. The gearing arrangement suitable for this application is
[GATE-2000]
(a) differential gear (b) helical gear (c) spur gear (d)
worm gear
131. Ans. (d)
132. Assertion (A): Tapered roller bearings must be used in heavy duty worm gear
speed reducers. [IES-2005]
Reason (R): Tapered roller bearings are suitable for large radial as well as axial
loads.
132. Ans. (a)
133. Consider the following statements in respect of worm gears: [IES-2005]
1. l. They are used for very high speed reductions.
2. The velocity ratio does not depend on the helix angle of the worm.
3. The axes of worm and gear are generally perpendicular and non-intersecting.
(a) 1 and 2 (b) 1 and 3 (c) 2 and 3 (d) 1, 2 and 3
133. Ans. (d)
134. Consider the following statements regarding improvement of efficiency of worm
gear drive: [IES-2004]
1. Efficiency can be improved by increasing the spiral angle of worm thread to
45o
or more
2. Efficiency can be improved by adopting proper lubrication
3. Efficiency can be improved by adopting worm diameter as small as
practicable to reduce sliding between worm-threads and wheel teeth
4. Efficiency can be improved by adopting convex tooth profile both for worm
and wheel
134. Ans. (c) 1 is wrong
135. Speed reduction in a gear box is achieved using a worm and worm wheel. The
worm wheel has 30 teeth and a pitch diameter of 210 mm. If the pressure angle of
the worm is 20o
, what is the axial pitch of the worm? [IAS-2004]
(a) 7 mm (b) 22 mm (c) 14 mm (d) 63 mm
135. Ans. (b)
210 22
7 7 22
30 7
xm and P m mmπ= = = = × =
Axial pitch = circular pitch of the worm wheel= mπ
136. A speed reducer unit consists of a double-threaded worm of pitch = 11 mm and
a worm wheel of pitch diameter = 84 mm. The ratio of the output torque to the input
torque is [IAS-2002]
(a) 7·6 (b) 12 (c) 24 (d) 42

136. Ans. (a)
Output torque pitch diameterof worm wheel 84
7.6
Input torque pitch of worm 11
= = =
137. To make a worm drive reversible, it is necessary to increase [GATE-1997]
(a) centre distance (b) worm diameter factor (c) number of starts (d) reduction
ratio
137. Ans. (c)
138. The lead angle of a worm is 22.5 deg. C. Its helix angle will be [IES-1994]
(a) 22. 5 deg. (b) 45 deg. (c) 67.5 deg. (d) 90°C.
138. Ans. (c) α = Pressure angle ≅ lead angle; α + β = 90°; β = helix angle = 90° -
22.5° = 67.5°
139. The maximum efficiency for spiral gears in mesh is given by (Where (θ = shaft
angle and φ , = friction angle) [IAS-1998]
(a)
1 cos( )
1 cos( )
θ φ
θ φ
+ −
+ +
(b)
1 cos( )
1 cos( )
θ φ
θ φ
+ +
+ −
(c)
1 cos( )
1 cos( )
θ φ
θ φ
− −
+ +
(d)
1 cos( )
1 cos( )
θ φ
θ φ
− +
+ −
139. Ans. (b)
140. Assertion (A): A pair of gears forms a rolling pair. [IAS-1996]
Reason (R): The gear drive is a positive drive.
140. Ans. (d) In rolling pair one link rolls over another fixed link.
141. In spur gears, the circle on which the involute is generated is called the
[GATE-1996]
(a) pitch circle (b) clearance circle (c) base circle (d) addendum circle
141. Ans. (a)
Friction in Worm Gears 6JJ
Selection of Materials 618
Strength Rating of Worm Gears 618
Wear Rating of Worm Gears 622
Thermal Considerations 6

4. Design of bearings
Rolling Contact Bearings
1. A circular disc having a mass of
30 kg is mounted asymmetrically
between two bearings A and B as
shown above in the figure. It is
used as an eccentric cam with an
eccentricity of 0.01 m. If the
shaking force on each of the
bearings is not to exceed 1500 N,
the speed of rotation of the cam
should not exceed
(a) 10 rad/s (b) 100
rad/s
(c) 70.7 rad/s (d) 140
rad/s
[IES-2003]
1. Ans. (b)
max
2
1/2
R = 1500 N
F = 2 x R = 2 x 1500 N
m r = 2 x 1500
2 1500
or = = 100 rad / see
30 0.01
c
ω
ω
×⎛ ⎞
⎜ ⎟
×⎝ ⎠
Types of Rolling Contact Bearings 417
2. Average values of effective coefficients of friction for bearings are described
below:
1. Spherical ball bearing - f1 2. Cylindrical roller bearing -f2
3. Taper roller bearing - f3 4. Stable (thick film)
Sliding contact bearing - f4
Which one of the following sequences is correct? [IES 2007]
(a) f1 < f2 < f3 < f4 (b) f1 < f2 < f4 < f3
(c) f2 < f1 < f3 < f4 (d) f1 < f4 < f2 < f3
2. Ans. (a)
3. The rating life of a group of apparently identical ball bearings is defined as the
number of revolutions or exceeded before the first evidence of fatigue crack by:
[IES-2005]
(a) 100% of the bearings of the group (b) 95% of the bearings of the group
(c) 90% of the bearings of the group (d) 66.66% of the bearings of the group
3. Ans. (c)

4. In sliding contact bearings, a positive pressure can be built up and a load
supported by a fluid only by the use of a: [IES-2005]
(a) Diverging film (b) Converging-diverging film
(c) Converging film (d) Flat film
4. Ans. (c)
5. Match List I (Type of Bearings) with List II (Type of Load) and select the correct
answer using the code given below the Lists: [IES-2005]
List I List II
A Deep groove bearing 1. Radial load
B. Tapered roller bearing 2. Radial and axial load
C. Self aligning being 3. Mainly radial load with shaft misalignment
D. Thrust bearing 4. Mainly axial load
A B C D A B C D
(a) 1 2 3 4 (b) 3 4 1 2
(c) 1 4 3 2 (d) 3 2 1 4
5. Ans. (a)
Antifriction bearings are
(a) sleeve bearings (b) gas lubricated bearings
(c) ball and roller bearings (d) journal bearings
6. Ans. (c)
7. The rolling element bearings are [IES-2003]
(a) Hydrostatic bearings (b) Squeeze film bearings
(c) Antifriction bearings (d) Grease lubrication bearings
7. Ans. (c)
8. A ball-bearing is characterized by basic static capacity = 11000 N and dynamic
capacity = 18000 N. This bearing is subjected to equivalent static load = 5500 N. The
bearing loading ratio and life in million revolutions respectively are [IES-2001]
(a) 3.27 and 52.0 (b) 3.27 and 35.0 (c) 2.00 and 10.1 (c) 1.60 and 4.1
8. Ans. (c)
9. In a single row deep groove ball-bearing, cages are needed to [IES-1999]
(a) separate the two races (b) separate the balls from the inner race
(c) separate the outer race from the balls
(d) ensure that the balls do not cluster at one point and maintain proper relative
angular positions.
9. Ans. (d)
10. Spherical roller bearings are normally used [GATE-1992]
(a) for increased radial load (b) for increased thrust load
(c) when there is less radial space (d) to compensate for angular misalignment
10. Ans. (a, d)
11. Which one of the following statements is NOT true of rolling contact bearing?
(a) The bearing characteristic number is given by ZN/p where Z is the absolute
viscosity of the lubricant, N is the shaft speed and p is the bearing pressure.
[IES-1997]
(b) Inner race of a radial ball bearing has an interference fit with the shaft and rotates
along with it

(c) Outer race of the bearing has an interference fit with bearing housing and does
not rotate
(d) In some cases, the inner race is stationary and outer race rotates
11. Ans. (d)
12. Assertion (A): It is desirable to increase the length of arc over which the oil film
has to be maintained in a journal bearing. [IES-1996]
Reason (R): The oil pressure becomes negative in the divergent part and the partial
vacuum created will cause air to leak in from the ends of bearing.
12. Ans. (c)
13. Consider the following statements about anti-friction bearings: [IES-1994]
1. They have low starting and low running friction at moderate speeds.
2. They have high resistance to shock loading. 3. They can carry both radial and
thrust loads.
4. Their initial cost is high. 5. They can accommodate some amount of misalignments
of shaft.
Of these statements
(a) 1, 2, 3 and 4 are correct (b) 1,3 and 4 are correct
(c) 1, 4 and 5 are correct (d) 1, 2, 3 and 5 are correct.
13. Ans. (a)
14. Ball bearings are provided with a cage [IES-1992]
(a) to reduce friction (b) to maintain the balls at a fixed
distance apart
(c) to prevent the lubricant from flowing out (d) to facilitate slipping of balls
14. Ans. (b)
15. Removal of metal particles from the raceway of a rolling contact bearing is a kind
of failure of bearing known as [IES-1995]
(a) pitting (b) wearing (c) spalling (d) scuffing
15. Ans. (a)
16. To carry a large axial load in a flat collar bearing, a number of collars is provided
to
(a) reduce frictional torque (b) increase frictional torque [IAS-2000]
(c) decrease intensity of pressure (d) increase intensity of pressure
16. Ans. (c) Total load is distributed among collars.
17. Deep groove ball bearings are used for [IAS-1995]
(a) heavy thrust load only (b) small angular displacement of shafts
(c) radial load at high speed (d) combined thrust and radial loads at high speed.
17. Ans. (d) Deep groove ball bearings are primarily designed to support radial loads
at high speeds. However, this type of construction permits the bearing also to support
relatively high thrust loads in either direction.

Dynamic Load Carrying Capacity 422
Equivalent Bearing Load 423
Load-life Relationship 423
18. The rated life of a ball bearing varies inversely as which one of the following?
(a) load (b) (load)2
(c) (load)3
(d) (load)3.33
[IES-2004]
18. Ans. (c)
P
d
L ,
R
⎛ ⎞
= ⎜ ⎟
⎝ ⎠
d = dynamic load capacity
R = Equivalent bearing load
P=3 for ball bearing
=
10
3
for roller bearing.
19. If the load on a ball bearing is halved, its life: [IES-2005]
(a) Remains unchanged (b) Increases two times
(c) Increases four times (d) Increases eight times
19. Ans. (d)
3
d
L
R
⎛ ⎞
= ⎜ ⎟
⎝ ⎠
d is dynamic load carrying capacity. R is actual load applied if
R halved L will increased by 23
= 8 times
20. If k = 3 for ball bearings and k = 3.33 for roller bearings, which one of the
following correctly states the load (P) - Life (L) relationship for rolling contact
bearings? [IAS-2004]
(a) 1 1
2 2
k
L P
L P
⎛ ⎞
= ⎜ ⎟
⎝ ⎠
(b)
( )
1
1
2 1
1 2
k
L P
L P
−⎛ ⎞
= ⎜ ⎟
⎝ ⎠
(c) 2 1
1 2
k
L P
L P
⎛ ⎞
= ⎜ ⎟
⎝ ⎠
(d)
1
2 1
1 2
k
L P
L P
−
⎛ ⎞
= ⎜ ⎟
⎝ ⎠
20. Ans. (c)
[d=dynamic load carrying capacity and R= Equivalent load]
K
d
L
R
⎛ ⎞
= ⎜ ⎟
⎝ ⎠
2 1
1 2
1
K
K
L R
L
R L R
α
⎛ ⎞
∴ ∴ = ⎜ ⎟
⎝ ⎠
21. The life of a ball-bearing is inversely proportional to [GATE-1993]
(a) (Load)1/3
(b) (Load)3
(c) (Load)3.3
(d) (Load)2
21. Ans. (B)
22. The life of a ball bearing at a load of 10 kN is 8000 hours. Its life in hours, if the
load is increased to 20 kN, keeping all other conditions the same, is [GATE-2000]
(a) 4000 (b) 2000 (c) 1000 (d) 500
22. Ans. (c)

23. The dynamic load capacity of 6306 bearing is 22 kN. The maximum radial load it
can sustain to operate at 600 rev/min, for 2000 hours is [GATE-1997]
(a) 4.16 kN (b) 3.60 kN (c) 6.2S kN (d) 5.29 kN
23. Ans. (D)
24. The basic load rating of a ball bearing is [GATE-1998]
(a) the maximum static radial load that can be applied without causing any plastic
deformation of bearing components.
(b) the radial load at which 90% of the group of apparently identical bearings run for
one million revolutions before the first evidence of failure.
(c) the maximum radial load that can be applied during operation without any plastic
deformation of bearing components.
(d) a combination of radial and axial loads that can be applied without any plastic
deformation.
24. Ans. (b)
Selection of Taper Roller Bearings 437
25. Assertion (A): Tapered roller bearings are sensitive to the tightening between
inner and outer races. [IES-2002]
Reason (R): Tapered roller bearings are always provided with adjusting nut for
tightening.
25. Ans. (b)
26. Which bearing is preferred for oscillating conditions? [IES-1992]
(a) Double row roller bearing (b) Angular contact single row ball bearing
(c) Taper roller bearing (d) Needle roller bearing
26. Ans. (d)
27. Match List-I (Bearings) with List-II (Applications) and select the correct answer
using the codes given below the lists:
A. Cylindrical roller 1. Radial loads
B. Ball-bearing 2. Machine needs frequent dismantling and assembling
C. Taper rolling bearing 3. Radial loads with lesser thrust
D. Angular contact hall-bearing 4. Shock loads
5. Axial expansion of shaft due to rise in temperature
A B C D A B C D
(a) 4 3 1 5 (b) 1 3 2 5
(c) 4 1 2 3 (d) 5 4 1 3
27. Ans. (c)

below the lists:
List I List II
A. End thrust 1. Plain bearing [IES-1998]
B. No cage 2. Ball bearing
C. More accurate centering 3. Needle bearing
D. Can be overloaded 4. Tapered roller bearing
(a) 3 4 2 1 (b) 4 3 1 2
(c) 3 4 1 2 (d) 4 3 2 1
28. Ans. (d)
below the Lists:
List-I List-II [IES-1997]
(Bearing) (Purpose)
A. Ball bearing 1. Heavy loads with oscillatory motion
B. Tapered Roller bearings 2. Light loads
C. Spherical Roller bearings 3. Carrying both radial and thrust loads
D. Needle Roller bearings 4. Self-aligning property
(a) 4 1 3 2 (b) 2 1 4 3
(c) 2 3 1 4 (d) 2 3 4 1
29. Ans. (d)
30. Tapered roller bearings can take [IES-1996]
(a) radial load only (b) axial load only
(c) both radial and axial loads and the ratio of these being less than unity.
(d) both radial and axial loads and the ratio of these being greater than unity.
30. Ans. (c)
31. In a collar thrust bearing, the number of collars has been doubled while
maintaining coefficient of friction and axial thrust same. It will result in [IES-2002]
(a) same friction torque and same bearing pressure
(b) double friction torque and half bearing pressure
(c) double friction torque and same bearing pressure
(d) same friction torque and half bearing pressure
31. Ans. (d)
Lubrication of Rolling Contact Bearings
453
Sliding Contact Bearings
32. Which of the following are included in the finishing operations for porous bearing?
1. Infiltration 2. Sizing 3. Heat treatment 4. Coining [IES-2005]
32. Ans. (a)

Basic Modes of Lubrication 456
33. Increase in values of which of the following results in an increase of the
coefficient of friction in a hydrodynamic bearing?
[IES 2007]
1. Viscosity of the oil. 2. Clearance between shaft and bearing.
3. Shaft speed.
(a) 1 and 2 only (b) 1 and 3 only
(c) 2 and 3 only (d) 1, 2 and 3
33. Ans. (b) 2 is false Petroff’s law says
Co efficient of friction (f) = 2π
P
NSμ
× ⎟⎟
⎠
⎞
⎜
⎝
⎛
c
r
f ↑ if (i) μ ↑ ; (ii) c↓ ; (iii) Ns ↑
34. What is the main advantage of hydrodynamic bearing over roller bearing?
[IES-2005]
(a) Easy to assemble (b) Relatively low price
(c) Superior load carrying capacity at higher speeds (d) Less frictional
resistance
34. Ans. (c)
35. Consider tile following statements: [IES-2006]
Radius of friction circle for a journal bearing depends upon
1. coefficient of friction 2. radius of the journal
3. angular speed of rotation of the shaft
(a) 1,2 and 3 (b) Only 1 and 2 (c) Only 2 and 3 (d) Only 1 and 3
35. Ans. (b) radius of friction circle = f r×
36. A friction circle is drawn when a journal rotates in bearing. Its radius depends on
the coefficient of friction and the [IES-1993]
(a) magnitudes of the forces on the journal (b) angular velocity of the journal
(c) clearance between the journal and the bearing (d) radius of the journal
36. Ans. (d) Friction circle's radius = rμ × (r = radius of the journal)
37. The radius of the friction circle in a journal bearing is dependent on coefficient of
friction and the [IES-2002]
(a) angular velocity of the journal (b) radius of the journal
(c) magnitudes of the forces on the journal (d) journal and bearing clearance
37. Ans. (b)
38. In a journal bearings, the radius of the friction circle increases with the increase in
(a) load (b) radius of the journal [IES-1997]
(c) speed of the journal (d) viscosity of the lubricant
38. Ans. (b)
39. Consider the following statements: [IES 2007]
For a journal rotating in a bearing under film lubrication conditions, the frictional
resistance is
1.proportional to the area of contact 2. proportional to the viscosity of
lubricant
3.proportional to the speed of rotation 4. independent of the pressure

(a) 1, 2, 3 and 4 (b) 1 and 4 only
(c) 2, 3 and 4 only (d) 2 and 3 only
39. Ans. (a) Viscous resistance (F) = T ×Area =
t
NLD
DL
t
DN
6060
22
μπ
π
μπ
=×
40. The bearing characteristic number in a hydrodynamic bearing depends on
(a) Length, width and load (b) length, width and speed. [IES-1996]
(c) Viscosity, speed and load (d) viscosity, speed and bearing pressure.
40. Ans. (d)
41. Which one of the following is a criterion in the design of hydrodynamic journal
bearings?
(a) Sommerfeld number (b) rating life
(c) Specific dynamic capacity (d) Rotation factor [GATE-2005]
41. Ans. (a)
42. In a journal bearing P = average gearing pressure, Z = absolute viscosity of the
lubricant, N = rotational speed of the journal. The bearing characteristic number is
given by [IAS-1997]
(a) ZN/p (b) p/ZN (c) Z/pN (d) N/Zp
42. Ans. (a)
43. It is seen from the curve that there is a minimum value of the coefficient of friction
(μ) for a particular value of the Bearing Characteristic Number denoted by α. What is
this value of the Bearing Characteristic Number called? [IES-2004]
(a) McKee Number (b) Reynolds Number
(c) Bearing Modulus (d) Somerfield Number
43. Ans. (c)
44. Assertion (A): In equilibrium position, the journal inside a journal bearing remains
floating on the oil film. [IES-1995]
Reason (R): In a journal bearing, the load on the bearing is perpendicular to the axis
of the journal.
44. Ans. (b) Both A and R are true but R is not correct explanation for A.
45. A full journal bearing having clearance to radius ratio of 1/100, using a lubricant
with [IES-2001]
-3
μ=28×10 Pa s supports the shaft journal running at N = 2400 r.p.m. If bearing
pressure is 1.4 MPa, the Somerfield number is
(a) -3
8×10 (b) -5
8×10 (c)0.48 (d) 0.48×10
45. Ans. (a)
46. A natural feed journal bearing of diameter 50 mm and length 50 mm operating at
20 revolution/second carries a load of 2.0 KN. The lubricant used has a viscosity of
20 mPas. The radial clearance is 50 μ m. The Sommerfeld number for the bearing is
(a) 0.062 (b) 0.125 (c) 0.250 (d) 0.785 [GATE-
2007]

46. Ans. (c)
47. A sliding contact bearing is operating under stable condition. The pressure
developed in oil film is p when the journal rotates at N r.p.m. The dynamic viscosity of
lubricant is μ and effective coefficient of friction between bearing and journal of
diameter D is f. Which one of the following statements is correct for the bearing?
[IES-2001]
(a)f is directly proportional to μ and p
(b)f is directly proportional to μ and N
(c)f is inversely proportional to p and f)
(d)f is directly proportional to μ and inversely proportional to N
47. Ans. (b)
48. Which one of the following sets of parameters should be monitored for
determining safe operation of journal bearing? [IES-2000]
(a) Oil pressure, bearing metal temperature and bearing vibration
(b) Bearing vibration, oil pressure and speed of shaft
(c) Bearing metal temperature and oil pressure
(d) Oil pressure and bearing vibration
48. Ans. (a)
49. Consider the following pairs of types of bearings and applications: [IES-2000]
1. Partial Journal bearing………………. Rail wagon axles
2. Full journal bearing ………………….Diesel engine crank-shaft
3. Radial bearing ……………………….Combined radial and axial loads
Which of these pairs is/are correctly matched?
(a) 1 alone (b) 1 and 2 (c) 2 and 3 (d) 1, 2 and 3
49. Ans. (b)
50. Match List-I (Applications) with List-II (Choice of Bearings) and select the correct
answer using the codes given below the lists: [IAS-2004]
List – I List - II
(Applications) (Choice of Bearings)
A. Granite table of a coordinate measuring machine1. Hydrodynamic bearing
B. Headstock spindle of a lathe 2. Deep groove ball bearing
C. Crank shaft of a diesel engine 3. Hydrostatic bearing
D. Armature of 0.5 kW induction motor 4. Taper roller bearing
(a) 1 4 3 2 (b) 3 2 1 4
(c) 1 2 3 4 (d) 3 4 1 2
50. Ans. (a)
the lists:
List I (Requirement) List II (Type) [IES-1995]
A. High temperature service 1. Teflon bearing.
B. High load 2. Carbon bearing
C. No lubrication 3. Hydrodynamic bearing
D. Bushings 4. Sleeve bearing
(a) 1 2 3 4 (b) 4 1 2 3
(c) 2 1 3 4 (d) 2 3 1 4
51. Ans. (d)

52. Assertion (A): In anti-friction bearings, the frictional resistance is very low as the
shaft held by it remains in floating condition by the hydrodynamic pressure developed
by the lubricant. [IES-2006]
Reason (R): In hydrodynamic journal bearings, hydrodynamic pressure is developed
because of flow of lubricant in a converging -diverging channel
52. Ans. (a)
53. Satisfactory hydrodynamic film in a journal bearing is formed when [IES-2006]
(a) journal speed is low, unit pressure on the bearing is high and viscosity of lubricant
used is low
(b) journal speed is low, unit pressure on the bearing is low and viscosity of lubricant
used is low
(c) journal speed is high, unit pressure on the bearing is high and viscosity of
lubricant used is high
(d) appropriate combination of journal speed, unit pressure on bearing and lubricant
viscosity exists resulting in low coefficient of friction
53. Ans. (c)
54. In an oil-lubricated journal bearing, coefficient of friction between the journal and
the bearing. [IES-1995]
(a) remains constant at all speeds.
(b) is minimum at zero speed and increases monotonically with increase in speed.
(c) is maximum at zero speed and decreases monotonically with increase in speed.
(d) becomes minimum at an optimum speed and then increases with further increase
in speed.
54. Ans. (d)
55. Match List I with List II and select the correct answer: [IES-2002]
List I (Bearings) List II (Load type)
A. Hydrodynamic Journal bearing 1. High radial and thrust load combined
B. Rectangular Hydrostatic bearing 2. Radial load only
C. Taper Roller bearing 3. Thrust load only
D. Angular contact ball bearing 4. Medium to low radial and thrust
combined
A B C D A B C D
(a) 2 3 1 4 (b) 4 1 3 2
(c) 2 1 3 4 (d) 4 3 1 2
55. Ans. (a)
56. Assertion (A): Oil as a cutting fluid result in a lower coefficient of friction.
Reason (R): Oil forms a thin liquid film between the tool face and chip, and it provides
'hydrodynamic lubrication'. [IES-2000]
56. Ans. (a)
57. Which one of the following pair is correctly matched? [IES-2000]
(a) Beauchamp tower ……………………First experiments on journal bearings
(b) Osborne Reynolds ……………………Antifriction bearings
(c) Somerfield number……………………Pivot and Collar bearings
(d) Ball bearings………………………….Hydrodynamic lubrication
57. Ans. (c)
58. Match List-I (Type of Anti-friction Bearing) with List-II (Specific Use) and select
the correct answer using the code given below the Lists: [IES-2006]
List-I List -II

A. Self-aligning ball bearing 1. For pure axial load
B. Taper roller bearing 2. For hinged condition
C. Deep groove ball bearing 3. For pure radial load
D. Thrust ball bearing 4. For axial and radial load
A B C D A B C D
(a) 2 1 3 4 (b) 3 4 2 1
(c) 2 4 3 1 (d) 3 1 2 4
58. Ans. (c)
59. Which one of the following types of bearings is employed in shafts of gearboxes
of automobiles? [IES-1999]
(a) Hydrodynamic journal bearings (b) Multi-lobed journal bearings
(c) Antifriction bearings (d) Hybrid journal bearings
59. Ans. (c)
60. Assertion (A): In hydrodynamic journal bearings, the rotating journal is held in
floating condition by the hydrodynamic pressure developed in the lubricant.
[IES-1994]
Reason (R): Lubricant flows in a converging-diverging channel.
60. Ans. (a) Both A and R are true and R provides correct explanation for A
61. In a hydrodynamic journal bearing, there is [IAS-2001]
(a) a very thin film of lubricant between the journal and the bearing such that there is
contact between the journal and the bearing
(b) a thick film of lubricant between the journal and the bearing
(c) no lubricant between the journal and the bearing
(d) a forced lubricant between the journal and the bearing
61. Ans. (b)
62. Which one of the following is the lubricator regime during normal operation of a
rolling element bearing? [IAS-2000]
(a) Hydrodynamic lubrication (b) Hydrostatic lubrication
(c) Elasto-hydrodynamic lubrication (d) Boundary lubrication
62. Ans. (c) There is elastic deformation of the contacting surfaces as surfaces are
not sufficiently rigid. Here fluid film pressure is also high.
63. A journal bearing of diameter 25 cm and length 40 cm carries a load of 150 kN.
The average bearing pressure is [IAS-1997]
(a) 1.5 kN/cm2
(b) 15 kN/cm2
(c) 150 kN/cm2
(d) none of the above
63. Ans. (d) The average bearing pressure = 2load 150
0.15kN / cm
projected area 25 40
= =
×
64. Which one of the curves shown below
represents the characteristic of a hydrodynamically
lubricated journal bearing?
(a) 1 (b) 2 (c) 3 (d) 4 [IAS-1998]
64. Ans. (c)

65. Consider the following statements:
For a proper hydrodynamic lubrication for a given journal bearing. [IAS-1996]
1. the higher the viscosity, the lower the rotating speed needed to float the journal at
a given load.
2. The higher the rotating speed, the higher the bearing load needed to float the
journal
at a given viscosity.
3. the higher the bearing load, the higher the viscosity needed to float the journal at a
given speed.
Of these statements:
(a) 1, 2 and 3 are correct (b) 1 and 2 are correct
(c) 2 and 3 are correct (d) 1 and 3 are correct
65. Ans. (a)
66. To restore stable operating condition in a hydrodynamic journal bearing, when it
encounters higher magnitude loads, [GATE-1997]
(a) oil viscosity is to be decreased (b) oil viscosity is to be increased
(c) oil viscosity index is to be increased (d) oil viscosity index is to be
decreased
66. Ans. (b)
67. List l List II [GATE-1997]
(A) Automobile wheel mounting on axle 1. Magneto bearing
(B) High speed grinding spindle 2. Angular contact bearing
(C) I.C. Engine connecting rod 3. Taper roller bearing
(D) Leaf spring eye mounting 4. Hydrodynamic journal bearing
5. Sintered metal bearing
6. Teflon/Nylon bush.
67. Ans. (A) -3, (B) -1, (C)-4, (0)-6
GATE -1996
68. In thick film hydrodynamic journal bearings, the coefficient of friction [GATE-
1996]
(a) increases with increases in load (b) is independent of load
(c) decreases with increase in load (d) may increase or decrease with increase in
load
68. Ans. (c)
69. Assertion (A): An important feature of film lubrication is that once a lubricant film
is formed on the mating surfaces by running the bearing with a lubricant having a
high degree of oiliness, it is possible to change to a lubricant with a much lower
oiliness.
Reason (R) Lubricants of high oiliness are liable to decompose or oxidize and hence
are not suitable for general lubrication purposes. [IAS-1999]
69. Ans. (a)
70. Thrust bearings of the sliding type are often provided with multiple sector-shaped
bearing pads of the tilting type instead of a continuous angular bearing surface in
order to
(a) distribute the thrust load more non-uniformly
(b) provide limited adjustments to shaft misalignments
(c) enable the formation of a wedge shaped oil film [IAS 1994]
(d) enable lubricating oil to come into contact with the total bearing area

70. Ans. (c)
Hydrostatic Step Bearing 464
71. The most suitable bearing for carrying very heavy loads with slow speed is
(a) hydrodynamic bearing (b) ball bearing (c) roller bearing (d) hydrostatic
bearing [IAS 1994]
71. Ans. (d)
72. Starting friction is low in
(a) Hydrostatic lubrication (b) Hydrodynamic lubrication [GATE-1992]
(c) Mixed (or semi-fluid) lubrication (d) Boundary lubrication
72. Ans. (a)
73. Assertion (A): Hydrostatic lubrication is more advantageous when compared to
hydrodynamic lubrication during starting and stopping the journal in its bearing.
[IES-1998]
Reason (R): In hydrodynamic lubrication, the fluid film pressure is generated by the
rotation of the journal.
73. Ans. (b)
Energy Losses in Hydrostatic Bearing
466
Temperature Rise 483
Bearing Materials 495
Lubricating Oils 497
Greases 502
Comparison of Rolling and Sliding
Contact bearings 503
74. Match List -I (Bearings) with List-II (Applications) and select the correct answer
using the codes given below the lists: [IAS-1998]
List –I List-II
A. Journal bearing 1. Electric motors
B. Thrust bearing 2. Watches
C. Conical pivot bearing 3. Marineengines
D. Ball bearing 4. Swivelling chairs
(a) 3 4 1 2 (b) 4 2 1 3
(c) 3 4 2 1 (d) 4 2 3 1

74. Ans. (c)

5. Fluctuating Load
Consideration for Design
Stress Concentration 117
1. While calculating the stress induced in a closed coil helical spring, Wahl's factor
must be considered to account for [IES-2002]
(a) the curvature and stress concentration effect (b) shock loading
(c) poor service conditions (d) fatigue loading
1. Ans. (a)
2. A loaded semi-infinite flat plate is
having an elliptical hole (A/B = 2) in the
middle as shown in the figure. The
stress concentration factor at points
either X or Y is
(a) 1
(b) 3
(c) 5
(d) 7
[IES-2000]
2. Ans. (c)
3. A large uniform plate containing a rivet-hole is subjected to uniform uniaxial
tension of 95 MPa. The maximum stress in the plate is [GATE-1992]
(a) 100 MPa (b) 285 MFa
(c) 190 MFa (d) Indeterminate
3. Ans. (b)

Stress concentration due to a central hole in a plate subjected to an uni-axial loading.
If a=b the hole reduces to a circular one and thereforeσ3 = 3σ1
which gives kt =3.
4. In a semi-infinite flat plate shown in the figure, the theoretical stress
concentration factor kt for an elliptical hole of major axis 2a and minor axis 2b is given
by
(a) Kt =
b
a
(b) Kt =1+
b
a
(c) Kt =1+
a
b2
(d) Kt = 1+
b
a2
[IAS-1998]
4. Ans. (d)
5. Assertion (A): Endurance limits for all materials are always less than the ultimate
strength of the corresponding materials. [IAS 1994]
Reason (R): Stress concentration in a machine part due to any dislocation is very
damaging when the part is subjected to variable loading.
5. Ans. (a)
Fluctuating Stresses 127
6. In designing a shaft for variable loads, the S.N. diagram can be drawn by
(a) Joining the Sut at 0 cycles and Se at 106
cycles by a straight line on an S.N. graph
(b) Joining the 0.9 Sut at 1000 cycles and Se at 106
cycles by a straight line on a
log S- log N graph [IES 2007]
(c) Joining the 0.9 Sut at 1000 cycles and Se at 106
cycles by a straight line on an S-N
graph
(d) Joining the Sut at 1000 cycles and 0.9 Se at 106
cycles by a straight line on a log
S- log N graph
(Sut stands for ultimate tensile strength and Se for the endurance limit)
6. Ans. (b)

1. Endurance strength of a component is not affected by its surface finish and
notch sensitivity of the material.
2. For ferrous materials like steel, S-N curve becomes asymptotic at 106
cycles.
(a) 1 only (b) 2 only (c) Both 1 and 2 (d) Neither 1 nor 2
7. Ans. (b) 1 is false: affected
8. The S-N curve for steel becomes asymptotic nearly at [GATE-2004]
(a) 103
cycles (b) 104
cycles (c) 106
cycles (d) 109
cycles
8. Ans. (c)
9. A cylindrical shaft is subjected to an alternating stress of 100 MPa. Fatigue
strength to sustain 1000 cycles is 490 MPa. If the corrected endurance strength is 70
MPa, estimated shaft life will be [GATE-2006]
(a) 1071 cycles (b) 15000 cycles (c) 281914 cycles (d) 928643 cycles
9. Ans. (c)
It is a finite life problem. The line AB is the failure line. Where
( ){ }103, log 0.9 ultA σ but here it will be ( ){ }103, log 490A and
( ){ }106, log eB σ here it is ( ){ }106, log 70B
Therefore ( ){ }10 10, log , log 100F N we have to find N
EF DB
AE AD
=
Or
10
10 10 10 10
log 3 6 3
log 490 log 100 log 490 log 70
N − −
=
− −
or N = 281914 cycles.

Endurance Limit 128
10. Match List I (Mechanical Property) with List II (Measured in Terms of) and select
the correct answer using the codes given below the lists: [IAS-2003]
List-I List-II
(Mechanical Property) (Measured in Terms of)
(A) Strength (Fluctuating load) 1. Percentage elongation
(B) Toughness 2. Modulus of elasticity
(C) Stiffness 3. Endurance limit
(D) Ductility 4. Impact strength
(a) 2 1 3 4 (b) 3 4 2 1
(c) 2 4 3 1 (d) 3 1 2 4
10. Ans. (b)
11. Match List I with List II and select the correct answer: [IAS-2000]
List I List II
A. Proof stress 1. Torsion test
B. Endurance limit 2. Tensile test
C. Leaf Spring 3. Fatigue test
D. Modulus of rigidity 4. Beam of uniform strength
A B C D A B C D
(a) 2 3 4 1 (b) 2 3 1 4
(c) 3 2 4 1 (d) 3 2 1 4
11. Ans. (a)
12. Match 4 correct pairs between list I and List II for the questions
List I List II [GATE-1994]
(a) Strain rosette 1. Critical speed
(b) Beams 2. Mohr's circle
(c) Section modulus 3. Coil springs
(d) Wahl's stress factor 4. Flexural rigidity
(e) Fatigue 5. Endurance limit
(f) Somerfield number 6. Core section
12. Ans. (a) – 2, (c) – 4, (d) – 3, (e) - 5
the lists:
List I (Material properties) List II (Tests to determine material
properties)
A. Ductility 1. Impact test
B. Toughness 2. Fatigue test
C. Endurance limit 3. Tension test
D. Resistance to penetration 4. Hardness test [IES-1993]
(a) 3 2 1 4 (b) 4 2 1 3
(c) 3 1 2 4 (d) 4 1 2 3
13. Ans. (c)
14. When σ and Young's Modulus of Elasticity E remain constant, the energy-
absorbing capacity of part subject to dynamic forces, is a function of its [IES-1992]
(a) length (b) cross-section (c) volume (d) none of the
above
14. Ans. (c)

Notch Sensitivity 130
15. In terms of theoretical stress concentration factor (Kt) and fatigue stress
concentration factor (Kf), then notch sensitivity 'q' is expressed as [GATE-2004]
( )
( )
( )
( )
( )
( )
( )
( )
1 1 11
( ) ( ) ( ) ( )
1 1 11
f f ft
t t tf
K K KK
a b c d
K K KK
− − +−
− + +−
15. Ans. (a)
Soderberg and Goodman Diagrams 146
16. A thin supercritical pressure vessel of 200 mm diameter and 1 mm thickness is
subjected to an internal pressure varying from 4 to 8 MPa. Assume that the yield,
ultimate, and endurance strength of material are 600, 800 and 400 MPa respectively.
The factor of safety as per Goodman’s relation is [GATE-2007]
(a) 2.0 (b) 1.6 (c) 1.4 (d) 1.2
16. Ans. (c)
17. The yield strength of a steel shaft is twice its endurance limit. Which of the
following torque fluctuation represent the most critical situation according to
Soderberg criterion? [GATE-1993]
(a) -T to +T (b) -T/2 to +T (c) 0 to +T (d) +T/2 to +T
17. Ans. (a)

18. Assertion (A): Soderberg relation is used for design against fatigue. [IES-
1996]
Reason (R): Soderberg relation is based on yield strength of the material whereas all
other failure relations for dynamic loading are based on ultimate strength of the
material.
18. Ans. (a)
19. The design calculations for members subject to fluctuating loads with the same
factor of safety yield the most conservative estimates when using [IES-1995]
(a) Gerber relation (b) Soderberg relation (c) Goodman relation (d) none of the
above.
19. Ans. (b)
20. In the figure shown, it
the line AB represents
Goodman criterion of
failure, then soderberg
criterion could be
represented by line
(a) AD
(b) D
(c) DC
(d) AC
[IES-1992]
20. Ans. (d)
Gyroscopic motion
21. A flywheel has a mass of 300 kg and a radius of gyration of 1m. It is given a spin
of 100 r.p.m about its horizontal axis. The whole assembly rotates about a vertical
axis at 6 rad/sec. The gyroscopic couple experienced will be
[IAS-1996]
(a) 3π kNm (b) 6π kNm (c) 180π kNm (d) 360π kNm
21. Ans. (b)
Gyroscopic couple = pIωω = 2 2
p
2 100
mk 300 1 6 Nm 6 KNm
60
π
ωω π
×⎛ ⎞
= × × × =⎜ ⎟
⎝ ⎠
22. For a disk of moment of inertia I the spin and precession angular velocities are ω
and ωp respectively. The magnitude of gyroscopic couple is…………. [GATE-
1994]

22. Ans. I ω . ωp
1. The effect of gyroscopic couple on a car while negotiating a curve is that its
outer wheels tend to get lifted from the ground.
2. If spin vector is rotated about the precession vector axis in a direction
opposite to that of precession through 90o
, the new position of the spin vector
indicates the direction of the torque vector.
Which of the following statements given above is/are correct?
(a) 1 only (b) 2 only (c) Both 1 and 2 (d) Neither 1 nor 2
23. Ans. (d)
24. Assertion (A): The precession of the axis of rotation of a shaft causes a
gyroscopic reaction couple to act on the frame to which the bearings are fixed.
[IES-2002]
Reason (R): The reaction of the shaft on each bearing is equal and opposite to the
action of the bearing on the shaft.
24. Ans. (b)
25. Assertion (A): There is a danger of locomotive wheels being lifted above rails at
certain speeds. [IES-2001]
Reason (R): Lifting of the locomotive wheel above rails at certain speed is due to
gyroscopic action.
25. Ans. (c)
26. A bicycle remains stable in running through a bend because of
(a) gyroscopic action (b) Corioli’s acceleration (c) centrifugal action (d) radius of
curved path
26. Ans. (a)
[IAS 1994]
27. An aeroplane makes a half circle towards left. The engine runs clockwise when
viewed from the rear. Gyroscopic effect on the aeroplane causes the nose to……..
(lift/dip) [GATE-1995]
27. Ans. Lift
6. Miscellaneous
28. In a 2-D CAD package, clockwise circular arc of radius 5, specified from P1 (15,
10) to P2(10, 15) will have its center at [GATE-2004]
(a) (10, 10) (b) (15, 10) (c) (15, 15) (d) (10, 15)
28. Ans. (c)
29. What is the correct sequence of the following steps in engine analysis?
[IES-1997]
1. Vibration analysis 2. Inertia force analysis.
3. Balancing analysis 4. Velocity and Acceleration analysis.
Select the correct answer using the codes given below:
(a) 2, 4, 1, 3 (b) 2, 4, 3, 1 (c) 4, 2, 1, 3 (d) 4, 2, 3, 1
29. Ans. (b)

30. A device for lifting or lowering objects suspended from a hook at the end of a
retractable chain or cable is called [IES-1994; 1995]
(a) hoist (b) jib crane (c) chain conveyor (d) elevator
30. Ans. (a)
31. Consider the following design considerations:
1. Tensile failure 2. Creep failure 3. Bearing failure 4 Shearing failure 5. Bending
failure
The design of the pin of a rocker arm of an I.C. engine is based on IES-1995]
(a) 1, 2 and 4 (b) 1, 3 and 4 (c) 2, 3 and 5 (d) 3, 4 and 5.
31. Ans. (d) Design of pin of a rocker arm of an I.C. engine is based on bearing,
shearing, and bending failures.
32. Consider the following statements regarding the differential of an automobile:
[IES-1994]
1. The speed of the crown wheel will always be the mean of the speeds of the two
road wheels.
2. The road wheel speeds are independent of the number of teeth on the planets.
3. The difference between the speeds of the road wheels depends on the number of
teeth on the planets.
4. The ratio of speeds of the road wheels depends upon the number of teeth on the
gear wheels attached to them and on the crown wheel.
Of these statements
(a) 1 and 2 are correct (b) 3 and 4 are correct (c) 1 and 3 are correct (d) 2 and 4 are
correct.
32. Ans. (d)
33. Interchangeability can be achieved by [IES-1993]
(a) standardisation (b) better process planning
(c) simplification (d) better product planning
33. Ans. (a) Interchangeability can be achieved by standardisation.
34. In an automobile service station, an automobile is in a lifted up position by means
of a hydraulic jack. A person working in the service station gave a tap to one rear
wheel and made it rotate by one revolution. The rotation of another rear wheel is
[IES-1993]
(a)zero (b) also one revolution in the same
direction
(c) also one revolution but in the opposite direction (d) unpredictable
34. Ans. (a) When one rear wheel is rotated, other is free.
35. Which of the following stresses are associated with the tightening of a nut on a
stud?
1. Tensile stresses due to stretching of stud.2. Bending stresses of stud.
[IES-1993]
3. Transverse shear stresses across threads.
4. Torsional shear stresses in threads due to frictional resistance.
Select the correct answer using the codes given below:
Codes: (a) 1, 2 and 3 (b) 1, 2 and 4 (c) 2, 3 and 4 (d) 1, 3 and 4
35. Ans. (a)
36. Match the following [IES-1992]
List -I (Dynamometer) List – II (Characteristics)

A. Torsion Dynamometer 1. High speeds and low power
B. Tesla fluid friction dynamometer 2. Power absorbed independent of size of
flywheel.
C. Prony brake 3. Power absorbed available for useful
applications
D. Swinging field dynamometer 4. Large powers
36. Ans. (d)
37. Rope brake dynamometer uses [IAS-2001]
(a) water as lubricant (b) oil as lubricant (c) grease as lubricant (d) no
lubricant
37. Ans. (d)
Statement for Linked Answer Questions 38 and 39:
A band brake consists of a lever attached to one
end of the band. The other end of the band is fixed
to the ground. The wheel has a radius of 200 mm
and the wrap angle of the band is 270o
. The
braking force applied to the lever is limited to 100
N, and the coefficient of friction between the band
and the wheel is 0.5. No other information is given.
38. The maximum tension that can be generated in the band during braking is
[GATE-2005]
(a) 1200 N (b) 2110 N (c) 3224 N (d) 4420 N
38. Ans. (b)
39. The maximum wheel torque that can be completely braked is [GATE-2005]
(a) 200 N.m (b) 382 N.m (c) 604 N.m (d) 844 N.m
39. Ans. (b)
40. In a band brake the ratio of tight side band tension to the tension on the slack
side is 3. If the angle of overlap of band on the drum is 180° the coefficient of friction
required between drum and the band is [GATE-2003]
(a) 0.20 (b) 0.25 (c) 0.30 (d) 0.35
40. Ans. (d)

41. Consider the following statements regarding power:
1. It is the capacity of a machine. [IAS-1997]
2. The efficiency is always less than unity as every device operates with some loss of
energy.
3. A dynamometer can measure the power by absorbing it.
4. Watt-hour is the unit of power.
Of these statements:
(a) 1, 2 and 3 are correct (b) 2, 3 and 4 correct
(c) 1, 3 and 4 are correct (d) 1, 2 and 4 are correct
41. Ans. (a)
42. A block-brake shown below has a face width of 300 mm and a mean co-efficient
of friction of 0.25. For an activating force of 400 N, the braking torque in Nm is
[GATE-2007]
(a) 30 (b) 40 (c) 45 (d) 60
42. Ans. (c)

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