Steam Turbine
Steam Turbine
Steam Turbine
The steam from the boiler is expanded in a nozzle, resulting in the emission
of a high velocity jet. This jet of steam impinges on the moving vanes or
blades, mounted on a shaft. Here it undergoes a change of direction of
motion which gives rise to a change in momentum and therefore a force.
• a. Pressure compounded
• b. Velocity compounded
• c. Pressure and velocity compounded impulse turbines.
Pressure
compounding
Involves splitting up of the whole
pressure drop
into a series of smaller pressure
drops across several stages of
impulse
Turbine.
Velocity drop is achieved through many moving rows of blades instead of a
single row of moving blades. It consists of a nozzle or a set of nozzles and
rows of moving blades attached to the rotor or the wheel and rows of fixed
blades attached to the casing
Pressure velocity compounding
Comparison between Impulse &
Reaction Turbine
Impulse turbine Reaction turbine
An impulse turbine has fixed nozzles that Reaction turbine makes use of the reaction
orient the steam flow into high speed jets. force produced as the steam accelerates
Blade profile is symmetrical as no through the nozzles formed by the rotor
pressure drop takes place in the rotor Blades have aerofoil profile (convergent p
blades drop occurs partly in the rotor
Suitable for efficiently absorbing Blades passage) since pressure
the high velocity and high Efficient at the lower pressure stages
pressure
Fine blade tip clearances are necessary
Steam pressure is constant across the
due
blades and therefore fine tip clearances are
not necessary to the pressure leakages
Efficiency is not maintained in the lower
pressure stages (high velocity cannot be Inefficient at the high pressure stages
achieved in steam for the lower pressure
due to the pressure leakages around
stages)
the blade tips
Fine tip clearances can cause damage
to
the tips of the blades
Losses in Steam Turbine
Profile loss: Due to formation of boundary layer on blade surfaces. Profile loss is a
boundary layer phenomenon and therefore subject to factors that influence boundary layer
development. These factors are Reynolds number, surface roughness, exit Mach number and
trailing edge thickness.
Secondary loss: Due to friction on the casing wall and on the blade root and tip. It
is a boundary layer effect and dependent upon the same considerations as those of profile
loss.
Tip leakage loss: Due to steam passing through the small clearances required
between the moving tip and casing or between the moving blade tip and rotating shaft. The
extend of leakage depends on the whether the turbine is impulse or reaction. Due to pressure
drop in moving blades of reaction turbine they are more
prone to leakages.
Disc windage loss: Due to surface friction created on the discs of an impulse
turbine as the disc rotates in steam atmosphere. The result is the forfeiture of shaft power for
an increase in kinetic energy and heat energy of steam
continue
Lacing wire loss: Due to passage blockage created by the presence of lacing wires
in long blade of LP Stages.
Wetness loss: Due to moisture entrained in the low pressure steam at the exit of LP turbine.
The loss is a combination of two effects; firstly, reduction in efficiency due to absorption of
energy by the water droplets and secondly, erosion of final moving blades leading edges.
Annulus loss: Due to significant amount of diffusion between adjacent stages
or where wall cavities occur between the fixed and moving blades. The extent of
loss is greatly reduced at high annulus area ratios (inlet/outlet) if the expansion of
the steam is controlled by a flared casing wall.
Leaving loss: Due to kinetic energy available at the steam leaving from the last
stage of LP turbine. In practice steam does slow down after leaving the last blade,
but through the conversion of its kinetic energy to flow friction losses.
Partial admission loss: Due to partial filling of steam, flow between the blades is
considerably accelerated causing a loss in power.
TURBINE
• FEATURES OF TURBINES
We shall consider steam as the working
fluid Single stage or Multistage
Axial or Radial turbines
Atmospheric discharge or discharge below atmosphere in
condenser Impulse/and Reaction turbine
• Impulse Turbines
Impulse turbines (single-rotor or multi-rotor) are simple stages of the
turbines. Here the impulse blades are attached to the shaft. Impulse blades
can be recognized by their shape. They are usually symmetrical and have
entrance and exit angles respectively, around 20 ° . Because they are
usually used in the entrance high-pressure stages of a steam turbine, when
the specific volume of steam is low and requires much smaller flow than
at lower pressures, the impulse blades are short and have constant cross
sections
IMPULSE TURBINE
If Va1 ≠ Va2, there will an axial thrust in the flow direction. Assume that Va is constant then,
Wt = UVa (tanα1+ tanα2) (3)
W UV (t β + t β ) (4)
Wt = UVa tanβ1+ tanβ2) Equation (4) is often referred to as the diagram work per unit mass flow and
hence the diagram efficiency is defined as
Work Done – Impulse Steam Turbine
Degree of reaction
Degree of reaction is a parameter that describes the relation
between the energy transfer due to the static pressure
change and the energy transfer due to dynamic pressure
change.
Degree of reaction is defined as the ratio of static
pressure drop in the rotor to the static pressure drop in the
stage. It is also defined as the ratio of static enthalpy drop in
the rotor to the static enthalpy drop in the stage
Degree of reaction
Zero reaction stage
Let us first discuss the special
case of zero reaction. According
to the definition
of reaction, When Λ = 0, equation
(upper) reveals that h1 = h2 and
equation (lower) that
β1 = β2.
Fifty percent reaction stage
From equation (16) for Λ = 0.5
α1
= β2 and the velocity diagram is
symmetrical Because of
symmetrical. symmetry, it is also
clear that α2 = β1. For Λ=1/2,
the enthalpy drop in the nozzle
row equals the enthalpy drop in
the rotor.
h0 - h1 = h1 - h2
Blade Height in Axial Flow
turbine
The continuity equation m = ρAV may be used to find the blade
height ‘h’. The annular area of flow = πDh. Thus the mass
flow rate through an axial flow turbine is