1. Nabakishore Satnami
Assistant Engineer
Mechanical Engineering Department
BTPS’A(1X500MW)
DAMODAR VALLEY CORPORATION

2.  Throttle governing
 Nozzle control governing
 Bypass governing
 Combination of the above

3.  The demand to utility network is not constant and generating
units do not always operate at full load.
 A simplest way of varying steam flow rate is by throttling
(controlling through A Valve).
ppump
Steam Generator
Pump
∆pSG ∆pvalve
The flow rate is controlled by increasing pressure drop across the valve.

4. ∆pvalve
∆pvalve ∆pvalve ∆pvalve
∆pturbine
Mass Flow Rate of Steam
A decrease in mass flow rate of steam is associated with a drop in turbine inlet pressure

5. •Relationship between load and steam consumption for a turbine governed
by throttling is given by the well-known Willians line.
m = m0 + mK
 
Steam flow rate ( kg/sec) and
Steam rate
m

steam rate( kg/kJ)
K
m
m0

Load ( k), kW

6. Expansion lines of the Non-rehat Condensing turbine
Pbowl
PT
Exit from governing stage
P P1
Design flow expansion line
∆HS
Enthalpy , h
Design flow expansion line
Entropy ,s

7. Throttle governing of a steam turbine on the h-s diagram
Po1 Po"
Po
∆HS
Enthalpy , h
Entropy ,s

8. m0 various from one machine to another and is generally in the range of 10 to 14% of
full load value.
m is the slope of the willians line and therefore is the change of steam flow rate per
unit change of turbine load.
Pressure variation……….
As the steam turbine system various its operation to satisfy the demand, steam
pressure at various turbine locations change accordingly.
steam pressure
p )
re HP
s u 1(
es e
pr tag
x
bo re i ns
le P)
z su 2 (I
Noz Pres n stage
ei )
3 (LP
Absolute
sur e
Pre e in stag
s
sur
Pres
m0 m1
Steam flow through turbine

9. Nozzle control governing
 The steam consumption rate is much smaller for the nozzle control than for throttle
control.
 At full load, all the nozzles will be delivering steam at full pressure and the turbine will
be operate at maximum efficiency.
 At some part load condition one group of nozzles may be shut off while the other nozzles
are fully operated.
 THROTTLING EFFECTS ON STEAM WILL BE EITHER ELIMINATED OR MINIMIZED
!!!!!!!!!!!

10. Nozzle control governing

11. By pass Governing
To produce more power ( when on over load) additional steam
may be admitted a by-pass valve to the later stage of the turbine.

12. Procedure for calculating Extraction Pressure during part Load operation
Step 1 : Assume the steam extraction pressure (Say design value multiplied by the
throttle steam flow rate ratio).
m
p = pdesign
md

Step 2 : Steam flows for feedwater heating are determined by using the
principle of energy conservation.
Step 3 : If the calculated value are not within a desirable range of the
assumed, the new values for extraction pressures must be
assumed and the new heat balance repeated.
Step 4 : In general, it takes three or four trials before the extraction
pressures are correctly estimated.

13. Regenerative Feed Water Heater Extraction Steam Flow
Variation with Varying Load

14. Upstream and Downstream Pressure Correlations
The flow of extraction steam through the NRV can be safely assumed analogous
with flow through orifice.

15. The normalized correlation between Upstream and Downstream
Pressures:
 pdown   pup 
ln  ÷= c + m.ln  ÷
 p0   p0 
The normalized correlation between Upstream and Downstream
Pressure Difference and Mass Flow Rate:
 . 
m
ln  . ÷= p +q ln  ∆ 

p
÷
m ÷  pmax 
 max 

16.  The relation between pressure variation and mass flow in the multi stage turbine
groups is expressed by the Ellipse Law , proposed by stodola.
 This law when applied to cases of non-controlled expansion in multi stage turbines,
employ the definition of flow coefficient Φ , in m2 , described by the following
equation:
m
Φ=
p
v
In which m is the steam mass flow rate ( kg/sec)
P= Pressure (kPa)
v=specific volume
The stodla ellipse law states that,
2
B 
Φi α 1 −  i ÷
 pi 

17.  Where Bi is the static pressure in the outlet of the group (kPa) and p i is the
total inlet pressure of this same group.
 This relation is only applied for group with a very large number of stages,
but is can be applied for at least eight-stage groups with 50% reaction. The
proportionality in the former equation can be eliminated as follows:
2
B 
1−  i ÷
Φi  pi 
=
Φ id B 
2
1 −  iD ÷
 piD 
 Where the subscript D means design conditions. Flow coefficients follow
equation 1. Cook(1985) suggests that a fairly good approximation is
obtained by taking steam static pressure Bi at the outlet of a given group as
the inlet steam pressure of the next one, pi+1.
 By rearranging the last equation, one obtains

18. Bi
pi =
1 − Φ 2 YiD
i
Where YiD = (P2ID- B2iD) / ( p2 iD ΦiD) is the stodla constant.
Note : This coefficient depends directly on the ratio between inlet and outlet
steam pressures of the turbine.
In such case, the control valve of the turbines are kept totally open, and pressure
control at the turbine inlet is achieved by the boiler and main pump of the plant.

19.  At part load operation , steam flow rate reduces the velocity ratio ( u/V ai).
 On load variations the enthalpy drops in the last stages of turbine and in the governing
stages of turbines with nozzle distribution are subjected to the greatest changes.
 In case of decrease in enthalpy drop ( ho) the absolute velocity of steam exit from the nozzle
cascade decreases and the velocity ratio increases .
 The increased velocity ratio causes a negative incidence angle and steam flow strikes the
suction side of the blade. It also increases the degree of reaction and the leakage loss
increase. Thus it reduces the stage efficiency.

20. OFF-DESIGN IMPACT
(A) Variation of Main Steam Flow:
(1) Effect on Pressures of Different Stages
MS Pressure remains constant
1st Stage pressure decided by flow rate
Pressures of all stages are lowered
(2) Effect on Temperatures of Different Stages
MS Temperature remains constant
Temperatures of all HP stages are lowered
Temperatures of other stages not changed much except LP last stages
(3) Effect on Enthalpy Drops of Different Stages
Enthalpy drops of all HP stages are lowered
Enthalpy drops of other stages not changed much except LP last stages

21. (4) Effect on Losses of Different Stages
Nozzle & Moving Blade Exit velocity loss decrease with load (HP stages)
Not much variation in IP & LP stages (except last LP stages)
Profile loss and cumulative loss vary according to load variation
Effect visible in HP stages but not in other stages (except last LP stages)
Last stage Exit velocity loss proportional with load variation
(5) Effect on Efficiencies of Different Stages
For 210 MW turbine, more or less the same except last LP stages
For 500 MW turbine, efficiencies of HP and IP initial stages less at part
load
(6) Effect on Internal Power of Different Stages
Varies proportionally with mass flow rate for all stages.
(7) Effect on Cycle Efficiency & Heat Rate of Different Stages
Cycle Efficiency deteriorates and Heat Rate increased with lower mass
flow rate

22. (B) Variation of Main Steam Pressure:
(All effects are limited to HP Stages only)
(1) Effect on Losses of Different Stages
At higher pressure, more throttle loss
Other losses increase at higher pressure
(2) Effect on Efficiencies of Different Stages
HP Stages efficiencies remain almost constant at different pressure
(3) Effect on Internal Power of Different Stages
Internal power of HP stages increase with increased pressure
(4) Effect on Cycle Efficiency & Heat Rate of Different Stages
Cycle Efficiency deteriorates and Heat Rate increased with lower Main
Steam Pressure

23. (C) Variation of Main Steam Temperature:
(All effects are limited to HP Stages only)
(1) Effect on Enthalpy Drops of Different Stages
Enthalpy drop of each HP stages increase with rise in MS Temperature
(2) Effect on Losses of Different Stages
Nozzle & Moving Blade Losses increase with Temperature rise
Profile loss & Cumulative loss increase with Temperature rise
(3) Effect on Efficiencies of Different Stages
HP Stages efficiencies remain almost constant at different temperatures
(4) Effect on Internal Power of Different Stage
Internal power of HP stages increase with increased temperature
(5) Effect on Cycle Efficiency & Heat Rate of Different Stages
Cycle Efficiency deteriorates and Heat Rate increased with lower Main
Steam Temperature

24. (D) Variation of Re-heat Steam Temperature:
(All effects are limited to IP and LP Stages only)
(1) Effect on Enthalpy Drops of Different Stages
Enthalpy drop of each IP and LP stages increase with rise in RH
Steam Temperature
(2) Effect on Losses of Different Stages
Nozzle & Moving Blade Losses increase with Temperature rise
Profile loss & Cumulative loss increase with Temperature rise
(3) Effect on Efficiencies of Different Stages
Slight improvement in Stage Internal Efficiencies at lower RH
steam temperature
(4) Effect on Internal Power of Different Stage
Internal power of both IP & LP stages increase with increased
RH steam temperature
(5) Effect on Cycle Efficiency & Heat Rate of Different Stages
Cycle Efficiency deteriorates and Heat Rate increased with lower
Reheat Steam Temperature

25. (E) Variation of Condenser Pressure:
(All effects are limited to LP last few Stages only)
(1) Effect on Pressure of Different Stages
Pressures increase with increase in Condenser pressure (LP last 3-4 stages)
(2) Effect on Temperature of Different Stages
Temperatures increase with increase in Condenser pressure (LP last 3-4
stages)
(3) Effect on Enthalpy Drop of Different Stage
Per stage Enthalpy drop decreases sharply with increase in Condenser
pressure (LP last 3-4 stages)
(4) Effect on Losses of Different Stages
Losses increase with increase in Condenser pressure (LP last 3-4 stages)
(5) Effect on Efficiency of Different Stages
Stage Efficiency decreases with increase in Condenser pressure (LP last 3-4
stages)
(6) Effect on Cycle Efficiency & Heat Rate of Different Stages
Cycle Efficiency deteriorates and Heat Rate increased with higher Condenser
Pressure