Turbine Loss
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Transcript of Turbine Loss
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Estimation of Losses in Large Turbines
P.M.V. Subbarao
Associate Professor
Department of Mechanical Engineering
Indian Institute of Technology, Delhi
Accounting of Losses is Saving of Losses
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Sequence of Energy Losses
Steam
Thermal
PowerSteam
kineticPower
Blade
kinetic
Power
Nozzle Losses
Moving Blade
Losses
Stage Losses
Isentropic efficiency of
Nozzle
Blade Friction Factor
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Losses in Turbine Stage
Losses in Regulating valves : The magnitude of loss of pressure
due to throttling with the regulating valves fully open is:
Dpv = 3 to 5% of pmax.
Loss in nozzle blades.
pressure loss in moving blades. Loss due to exit velocity.
Loss due to friction of the disc and blade banding
Loss associated with partial admission.
Loss due to steam leakages through clearances.
Loss due to flow of wet steam.
Loss due to exhaust piping.
Loss due to steam leakage in seals.
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Losses in Nozzles
Losses of kinetic energy of steam while flowing through nozzlesor guide blade passages are caused because of
Energy losses of steam before entering the nozzles,
Frictional resistance of the nozzles walls,
Viscous friction between steam molecules,
Deflection of the flow,
Growth of boundary layer,
Turbulence in the Wake and
Losses at the roof and floor of the nozzles.
These losses are accounted by the velocity coefficient, f.
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Loss in nozzle cascade, 2 211 / 2000n th cD kJ/kg
2 221 / 2000m th wD kJ/kgLoss in moving blade cascade,
2
2/ 2000evh cD kJ/kgExit velocity Energy
Theoretical steam velocity at nozzle exit,1 0
2000t nc h m/s.
1.Relative steam velocity at entry to moving blade cascade,
2 2
1 1 1 12 cosw c u uc m/s
Absolute velocity at moving blade exit,
2 2
2 2 2 22 cosc w u uw m/s.
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0
0
m nrb
E h h
E D DBlade efficiency,
Available energy of stage,0 0 ev ev
E h h
D kJ/kg
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Turbine pressure profile at designed condition
0
2
4
6
8
10
12
14
16
MSPr
HP
1(1st
St.)
HP5
HP9
HP13
HP17
HP21
CRHPr IP
3IP
7IP
10
IP
12(Ex5
)IP
16
IPExh
st
LP
4(E
x3)
LP
6(Ex2
)
LP7
(Ex1
)
LPExh
st
Stages
Pr.
(MPa
)
Pr in HBD
Pr from Simulation
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Temperature profiles at designed condition
0
100
200
300
400
500
600
MSLine
HP3
HP7
HP11
HP15
HP19
HP23
CRH
TIP
3IP
7
IP12
(Ex5
)IP
16
IPExh
st
LP4(E
x3)
LP6(E
x2)
LPExh
st
Stages
Temperature
(degC)
Temp in HBD
Temp from Simulation
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HP Turbine per stage Enthalpy drop profiles at
designed condition.
14.4
14.6
14.8
15
15.2
15.4
15.6
15.8
16
16.2
HP1(1st
St.)
HP2HP
3HP
4HP
5HP
6HP
7HP
8HP
9
HP10
HP11
HP12
HP13
HP14
HP15
HP16
HP17
HP18
HP19
HP20
HP21
HP22
HP23
HP24
HP25
Stages
EnthalpyDrop
(kJ/kg)
Stagnation Enthalpy Drop
Static Enthalpy Drop
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Nozzle& Moving Blade Losses for HP Stages at Designed
condition
0.4
0.5
0.6
0.7
0.8
0.9
1
1.1
HP1(1st
St.)HP
3HP
5HP
7HP
9
HP11
HP13
HP15
HP17
HP19
HP21
HP23
HP25
Stages
Loss
(kJ/kg)
Nozzle loss
Moving blade loss
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IP Turbine per stage Enthalpy drop profiles at
designed condition.
15
20
25
30
35
40
IP1
IP2
IP3
IP4
IP5
IP6
IP7
IP8
IP9
IP1
0
IP1
1
IP1
2
(Ex5)
IP1
3
IP1
4
IP1
5
IP1
6
IP1
7
IP1
8
IP1
9
IP2
0
Stages
Enthalpydrop(kJ/kg)
Stagnation Enthalpy drop
Static Enthalpy drop
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Nozzle& Moving Blade Losses for IP Stages at
Designed condition
0.4
0.50.6
0.7
0.8
0.91
1.1
1.2
1.3
1.4
IP1
IP3
IP5
IP7
IP9
IP11
IP13
IP15
IP17
IP19
Stages
Loss(kJ/kg)
Nozzle loss
Moving blade loss
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LP Turbine per stage Enthalpy drop profiles at designed
condition.
60
70
80
90
100
110
120
LP1
LP2
LP3
LP4
(Ex3)
LP5
LP6
(Ex2)
LP7
(Ex1)
LP8
Stages
Enthalpydro
p(kJ/kg)
Stagnation Enthalpy drop
Static Enthalpy drop
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Nozzle& Moving Blade Losses for LP Stages at Designed
condition
0
1
2
3
4
5
6
7
8
9
LP 1 LP 2 LP 3 LP 4
(Ex 3)
LP 5 LP 6
(Ex 2)
LP 7
(Ex 1)
LP 8
Stages
Loss(kJ/kg)
Nozzle loss
Moving blade loss
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GLAND Leakage Flows
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Gland leakage losses
The steam leaked out from the system does not work on the blades,
it represents energy loss
1.Diaphragm leakageIt takes place in stages through the radial clearance between the
stationary nozzle diaphragm and the shaft or drum.
2.Tip leakage
It occurs in stages through the clearance between the outer peripheryof the moving blades and the casing due to the pressure difference
existing across the blade.
3.Shaft leakage
Shaft leakage occurs through radial clearance between the shaft andcasing at both high and low pressure ends of turbines.
At the high pressure end , steam leaks out to the atmosphere,
whereas at the LP end, the pressure being less than the atmospheric ,
air leaks into the shell
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Loss by leakage through diaphragm gland,
1
1 1
g g g rbd k F
F z
Loss by leakage through banding gland,
1
1
1
1.8eq rbb
d l
F d
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Leakage Losses for Turbine Stages
0
0.005
0.01
0.015
0.02
0.025
0.03
HP1(1stSt.
)HP5HP9HP13HP17HP21HP25 IP4 IP8
IP12(Ex5
)
IP16IP20
LP4(Ex3
)LP8
stages
Losses(kJ/kg)
Gland loss
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Turning loss
These occurs as the steam turns in the blade passage.
Disc friction loss
When the turbine disc rotates in the viscous steam, there is surface friction loss
due to relative motion between the disc and steam particles. Due to centrifugalforce , steam thrown radially outward.
The moving disc exerts a drag on the steam, sets it in motion from root to tip,
and produces a definite circulation.
Some part of Kinetic energy of steam is lost due to this friction.
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Friction loss,
32
1
fr fr
f
d uk
F c
Relative Internal efficiency, 1 1d b
ri rb fr
Effective enthalpy drop, 0i rih E
Power of the stage,.
i iP m h
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Profile Losses for Turbine Stages at Designed
Condition
0
0.0005
0.001
0.0015
0.002
0.0025
0.003
H
P1
(1stSt.)
HP5
HP9
HP1
3
HP1
7
HP2
1
HP2
5
IP4
IP8
IP1
2(Ex5)
IP1
6
IP2
0
LP4
(Ex3)
LP8
Stages
Loss
(kJ/kg)
Profile Loss
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Losses associated with partial admission of steam
Partial admission of steam to turbine stages is employed in cases when thevolume flow rate of steam is not high (ie. Turbine of low capacity)
In turbine with partial admission ,steam is fed onto the moving blades only
an arc of length , rather than along the entire circumference.
Along the arc , there is no active flow of steam , and the blade passage
opposing this arc are filled with stagnant steam from the disc chamber.
Owing to the rotation of the disc , the steam filling this passage is entrained
by centrifugal force and moves from the roots to tips of moving blade;
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Steam can even flow from one side of the blade to the opposite side
Diagram of windage currents
in a partial admission turbine
stages
The work associated with this motion of the steam in bladepassages of the inactive portion of the arc of moving blades, is lost-
Usual energy of the turbine stage is decreased by the energy loss
associated wit this motion ( windage) of steam in blade passages
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Residual velocity loss
Steam leaving the last stage of the turbine has certain velocity,
which represent the amount of kinetic energy that cannot beimparted to the turbine shaft and thus it is wasted
Exhaust end loss
1. Exhaust end loss occur between the last stage of low pressureturbine and condenser inlet.
2. Exhaust loss depends on the absolute steam velocity.
Turbine Exhaust end loss = Expansion-line -end point - Used energy endpoint.
Typical exhaust loss curve :
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Turn-up loss
Total Exhaust
Loss
Gross hoodloss
Actual leaving
loss
Annulus
restriction loss
(1 0.01 )
3600
a
an
an
Q v YV
A
Annulus velocity
(m/sec)
Condenser flow
rate
Annulus area
Percentage of Moisture at
the Expansion line endpoint
Typical exhaust loss curve :
Annulus Velocity (m/s)
ExhaustLossofdr
yflow
0 120 240 180 240 300 360
10
20
30
40
50
SP.Volume
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Problems in Low pressure turbine
In the case of condensing turbines the last few stages operate
under wet steam conditions. This results in the formulation of minute droplets of water.
These droplets under the influence of centrifugal force are thrownout towards the periphery.
At the same time these droplets of water receive an accelerating
force from the steam particles in the direction of flow . Thus some of the kinetic energy of the flowing steam is lost in
accelerating these water droplets.
The absolute velocity of the steam is considerably greater thanthat of the water droplets into the moving blade passages.
The water droplets are deflected onto the back of the movingblades as a result of which the moving blades experience animpact force caused by impingement of the moving blades.
As a result of this moving blades experience an impact forcecaused by the impingement of water droplets on their backs.
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The practical investigations that the blade tips are subjected towear from one side water droplets present in the last few stagescan also result in erosion damage of turbine blades and nozzles .
One of the loss mechanisms in the steam turbine is the kineticenergy of the steam as it leaves the last stage blade.
The lower the kinetic energy, the higher the steam turbineefficiency will be.
The magnitude of loss is proportional to the square of the ratio of
the volume flow rate of the steam through the last stage of thesteam turbine and the annulus area of the turbine exit.
To decrease the loss, a larger turbine exit annulus area is needed.
An increase in the last stage blade annulus area can be
accomplished by either using shorter blades mounted on a largerdiameter rotor (largerhub) or
by using longer blades mounted on a smaller diameter rotor.
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The low-pressure turbine exhaust end is one of the important factors
affecting the turbine performance.
The size of the exhaust end is determined by the number of exhaust
flows and the length of the last stage blades.
In general, the larger the exhaust ends, the lower the full load net heat
rate. Under the part-load conditions.
Turbines with a large exhaust end will deteriorate more rapidly in
performance.
C l ti L f T bi St t D i d
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Cumulative Loss for Turbine Stages at Designed
Condition
0
1
2
3
4
5
6
7
89
10
HP1(1stS
t.)HP
5HP
9
HP13
HP17
HP21
HP25 IP
4IP
8
IP12(Ex
5)
IP16IP
20
LP4(Ex3
)LP
8
Stages
Loss
(kJ/kg)
Cumulative loss