(1/2). μ W cosecα (r₁ + r₂)
(2/3). μ W cosecα (r₁ + r₂)
(1/2). μ W cosecα [(r₁³ - r₂³)/(r₁² - r₂²)]
(2/3). μ W cosecα [(r₁³ - r₂³)/(r₁² - r₂²)]
D. (2/3). μ W cosecα [(r₁³ - r₂³)/(r₁² - r₂²)]
5,367 r.p.m.
6,000 r.p.m.
9,360 r.p.m.
12,000 r.p.m.
Right side pivot of this link
Left side pivot of this link
A point obtained by intersection on extending adjoining links
Cant occur
Lower pair
Higher pair
Open pair
Close pair
Pitch circle dia. × cosφ
Addendum circle dia. × cosφ
Clearance circle dia. × cosφ
Pitch circle dia. × sinφ
Free vibration
Forced vibration
Damped vibration
Under damped vibration
Primary unbalanced force
Secondary unbalanced force
Two cylinders of locomotive
Partial balancing
Pendulum type governor
Dead weight governor
Spring loaded governor
Inertia governor
Decreases linearly with time
Increases linearly with time
Decreases exponentially with time
Increases exponentially with time
m/(m + M)
M/(m + M)
(m + M)/m
(m + M)/M
Radial component only
Tangential component only
Coriolis component only
Radial and tangential components both
A point on the pitch curve having minimum pressure angle
A point on the pitch curve having maximum pressure angle
Any point on the pitch curve
Any point on the pitch circle
1-3 m/s
3-15 m/s
15-30 m/s
30-50 m/s
Second inversion of double slider crank chain
Third inversion of double slider crank chain
Second inversion of single slider crank chain
Third inversion of slider crank chain
Completely constrained motion
Partially constrained motion
Incompletely constrained motion
Freely constrained motion
ω² R cosθ
ω² (R - r₁) cosθ
ω² (R - r₁) sinθ
ω² r₁ sinθ
μ₁ = μ sinβ
μ₁ = μ cosβ
μ₁ = μ/sinβ
μ₁ = μ/cosβ
Single slider crank chain
Whitworth quick return motion mechanism
Crank and slotted lever quick return motion mechanism
All of the above
tp /16
tp /4
4 tp
16 tp
Less
More
Equal
May be less or more depending on efficiency
Broken belt
Broken belt and its adjacent belts
All the belts
There is no need of changing any one as remaining belts can take care of transmission of load
Tip of the gear tooth and flank of pinion
Tip of the pinion and flank of gear
Flanks of both gear and pinion
Tip of both gear and pinion
Hartnell governor
Hartung governor
Wilson-Hartnell governor
All of these
Four
Five
Six
Seven
In plane rotation with variable velocity
In plane translation with variable velocity
In plane motion which is a resultant of plane translation and rotation
Restrained to rotate while sliding over another body
Static friction
Dynamic friction
Limiting friction
Coefficient of friction
Same
Two times
Four times
None of these
Lower pair
Higher pair
Self-closed pair
Force-closed pair
(r₁² - r₂²)/(r₁ - r₂)
(r₁² - r₂²)/(r₁ + r₂)
(r₁³ - r₂³)/(r₁² - r₂²)
(r₁³ - r₂³)/(r₁ - r₂)
Of rotation of the cam for a definite displacement of the follower
Through which the cam rotates during the period in which the follower remains in the highest position
Moved by the cam from the instant the follower begins to rise, till it reaches its highest position
Moved by the cam from beginning of ascent to the termination of descent
A rigid link rotates instantaneously relative to another link at the instantaneous centre for the configuration of the mechanism considered.
The two rigid links have no linear velocity relative to each other at the instantaneous centre.
The velocity of the instantaneous centre relative to any third rigid link is same whether the instantaneous centre is regarded as a point on the first rigid link or on the second rigid link.
All of the above