design parameters steam turbine

7/28/2019 Design Parameters Steam Turbine

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OFF DESIGN PERFORMANCE PREDICTION OF

STEAM TURBINES


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Principle methods of load reduction

Throttle governing

Nozzle control governing

Bypass governing

Combination of the above


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PART-LOAD OPERATION

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).

Pump

ppump

DpSG

Steam Generator

Dpvalve

The flow rate is controlled by increasing pressure drop across the valve.


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Flow Characteristics of A Throttle Valve

Mass Flow Rate of Steam

Dpvalve

Dpturbine

Dpvalve

Dpvalve Dpvalve

A decrease in mass flow rate of steam is associated with a drop in turbine inlet pressure


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Willians LineRelationship between load and steam consumption for a turbine governedby throttling is given by the well-known Willians line.

Load ( k), kW

K

mSteam rate

Steamf

low

rate(kg/sec)and

steam

rate(kg/kJ)

0m

mKmm 0

m


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SHD

TP

bowlP

Exit from governing stage

Design flow expansion line

Design flow expansion line

P P1

Expansion lines of the Non-rehat Condensing turbine

Entropy ,s

Enthalpy,h


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Entropy ,s

Enthalpy,

hSHD

1oPo

P

Throttle governing of a steam turbine on the h-s diagram"

oP


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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.

m0

Steam flow through turbine

Absolu

testeam

pressure

m1


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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

!!!!!!!!!!!


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By pass Governing

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


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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).

Step 2 : Steam flows for feedwater heating are determined by using theprinciple 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.

d

designmmpp


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Regenerative Feed Water Heater Extraction Steam Flow

Variation with Varying Load


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Upstream and Downstream Pressure Correlations

The flow of extraction steam through the NRV can be safely assumed analogous

with flow through orifice.


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The normalized correlation between Upstream and Downstream

Pressures:

0 0

ln .lnupdown

ppc m

p p

The normalized correlation between Upstream and DownstreamPressure Difference and Mass Flow Rate:

.

.

maxmax

ln lnm p

p qp

m

D


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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 , in m2 ,described by the followingequation:

m

p

v

2

1i

i

i

B

p

In which m is the steam mass flow rate ( kg/sec)

P= Pressure (kPa)

v=specific volume

The stodla ellipse law states that,

Wh B i th t ti i th tl t f th (kP ) d i th


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Where Bi is the static pressure in the outlet of the group (kPa) and pi is thetotal 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:

Where the subscript D means design conditions. Flow coefficients followequation 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 inletsteam pressure of the next one, pi+1.

By rearranging the last equation, one obtains

2

2

1

1

i

ii

idiD

iD

B

p

B

p


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21

i

i

i iD

Bp

Y

Where YiD = (P2ID- B

2iD) / ( p

2iD iD) 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.

At t l d ti t fl t d th l it ti ( /V )


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At part load operation , steam flow rate reduces the velocity ratio ( u/Vai).

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.


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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


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(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 partload

(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 StagesCycle Efficiency deteriorates and Heat Rate increased with lower mass

flow rate


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(B) Variation of Main Steam Pressure:

(All effects are limited to HP Stages only)


At higher pressure, more throttle loss

Other losses increase at higher pressure


HP Stages efficiencies remain almost constant at different pressure

(3) Effect on Internal Power of Different Stages

Internal power ofHP stages increase with increased pressure

(4) Effect on Cycle Efficiency & Heat Rate of Different Stages

Cycle Efficiency deteriorates and Heat Rate increased with lower MainSteam Pressure


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(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


Nozzle & Moving Blade Losses increase with Temperature rise

Profile loss & Cumulative loss increase with Temperature rise


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


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(D) Variation of Re-heat Steam Temperature:

(All effects are limited to IP and LP Stages only)

(1) Effect on Enthalpy Drops of Different StagesEnthalpy drop of each IP and LP stages increase with rise in RH

Steam Temperature


Nozzle & Moving Blade Losses increase with Temperature riseProfile loss & Cumulative loss increase with Temperature rise

(3) Effect on Efficiencies of Different StagesSlight improvement in Stage Internal Efficiencies at lower RH

steam temperature

(4) Effect on Internal Power of Different StageInternal power of both IP & LP stages increase with increased

RH steam temperature

(5) Effect on Cycle Efficiency & Heat Rate of Different StagesCycle Efficiency deteriorates and Heat Rate increased with lower

Reheat Steam Temperature


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(E) Variation of Condenser Pressure:

(All effects are limited to LP last few Stages only)

(1) Effect on Pressure of Different StagesPressures increase with increase in Condenser pressure (LP last 3-4 stages)

(2) Effect on Temperature of Different StagesTemperatures increase with increase in Condenser pressure (LP last 3-4

stages)

(3) Effect on Enthalpy Drop of Different StagePer stage Enthalpy drop decreases sharply with increase in Condenser

pressure (LP last 3-4 stages)

(4) Effect on Losses of Different StagesLosses increase with increase in Condenser pressure (LP last 3-4 stages)

(5) Effect on Efficiency of Different StagesStage Efficiency decreases with increase in Condenser pressure (LP last 3-4

stages)

(6) Effect on Cycle Efficiency & Heat Rate of Different StagesCycle Efficiency deteriorates and Heat Rate increased with higher Condenser

Pressure

design parameters steam turbine

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