Ratio of actual discharge to the theoretical discharge

Sum of actual discharge and the theoretical discharge

Difference of theoretical discharge and the actual discharge

Product of theoretical discharge and the actual discharge

C. Difference of theoretical discharge and the actual discharge

Geometric similarity

Kinematic similarity

Dynamic similarity

None of these

Directly proportional to N

Inversely proportional to N

Directly proportional to N²

Inversely proportional to N²

10-15°

20-25°

30-40°

50-60°

10° to 15°

15° to 20°

20° to 25°

25° to 30°

Power produced by the turbine to the energy actually supplied by the turbine

Actual work available at the turbine to the energy imparted to the wheel

Workdone on the wheel to the energy (or head of water) actually supplied to the turbine

None of the above

Tangential flow impulse turbine

Inward flow impulse turbine

Outward flow impulse turbine

Inward flow reaction turbine

Equal to

1.2 times

1.8 times

Double

Centrifugal

Axial flow

Reciprocating

Mixed flow

Adjustable blades

Backward curved blades

Vaned diffusion casing

Inlet guide blades

Two cylinders, two rams and a storage device

A cylinder and a ram

Two coaxial rams and two cylinders

A cylinder, a piston, storage tank and control valve

Horizontal

Nearly horizontal

Steep

First rise and then fall

175.4 r.p.m.

215.5 r.p.m.

241.5 r.p.m.

275.4 r.p.m

Same

0.75 B.H.P.

B.H.P./0.75

1.5 B.H.P.

Accumulating oil

Supplying large quantities of oil for very short duration

Generally high pressures to operate hydraulic machines

Supplying energy when main supply fails

0 to 25 m

25 m to 250 m

Above 250 m

None of these

Air lift pump

Jet pump

Hydraulic coupling

Hydraulic press

0.50 to 0.65

0.65 to 0.75

0.75 to 0.85

0.85 to 0.90

Rectilinear flow

Radial flow

Free vortex motion

Forced vortex

Medium head application from 24 to 180 m

Low head installation up to 30 m

High head installation above 180 m

All types of heads

Directly proportional to diameter of its impeller

Inversely proportional to diameter of its impeller

Directly proportional to (diameter)² of its impeller

Inversely proportional to (diameter)² of its impeller

Radially, axially

Axially, radially

Axially, axially

Radially, radially

No flow will take place

Cavitation will be formed

Efficiency will be low

Excessive power will be consumed

Closed

Open

Depends on starting condition and flow desired

Could be either open or closed

One-fourth

One-half

Three-fourth

Double

0 to 4.5

10 to 100

80 to 200

250 to 300

Greater than 15°

Greater than 8°

Greater than 5°

Less than 8°

Designing new impeller

Trimming the impeller size to the required size by machining

Not possible

Some other alterations in the impeller

Directly as the air or gas density

Inversely as square root of density

Inversely as density

As square of density

At the level of tail race

Little above the tail race

Slightly below the tail race

About 2.5 m above the tail race to avoid cavitations.

Velocity of flow at inlet to the theoretical jet velocity

Theoretical velocity of jet to the velocity of flow at inlet

Velocity of runner at inlet to the velocity of flow at inlet

None of the above