Boiler Feed Pump - Presentation handbook.pdf

Pumps in Steam Power Plants

P M V Subbarao

Professor

M h i l E i i D t t

Life Inducing Devices

Mechanical Engineering Department I I T Delhi

Pumps in Steam Power Plants

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Stea

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• Turbogenerator & Auxiliaries – 3 sets.g • Steam generator equipment – 6 sets. • Chemical feed system – 13 sets.

• Fuel Oil systems – 14 sets.

• Lubricating oil systems – 5 sets. • Fire Protection systems – 6 sets. • Service water system – 7 sets.

• Miscellaneous around 4 sets

Pump services in Main Steam Cycle

• Turbogenerator and auxiliaries

– Condenser circulating pumpsCondenser circulating pumps – Screen wash-water pumps

– Cooling tower make-up pumps

• Steam generator equipment

– Condensate pumps

– Condensate booster pumpsCo de sate booste pu ps – Boiler-feed pumps

– Boiler-feed booster pumps Deaerator make p p mps – Deaerator make-up pumps

Boiler Feed Pumps

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• The boiler feed pump (BFP) is one of the most important auxiliary equipments in coal-fired power plants

auxiliary equipments in coal fired power plants.

• With the increase in steam parameters of thermodynamic cycle and the growth of unit capacity, the power capacity of boiler feed pumps is also growing.

• The power consumption of BFP has been accounted for about 5% of power generation capacity in the large generating units 5% of power generation capacity in the large generating units. • The reasonable choice for boiler feed pump driving mode

plays an important role in the operation economy of the entire power plant.

• The type and number of BFP and the design of its water

supply system have a great impact on thermal efficiency and supply system have a great impact on thermal efficiency and operation cost

Boiler-Feed Pump Capacity

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• The total boiler-feed pump capacity is established by adding to

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the maximum boiler flow a margin to cover boiler swings and the eventual reduction in effective capacity from wear.

• This margin varies from as much as 20% in small plants to asThis margin varies from as much as 20% in small plants to as little as 5% in the larger central stations.

• The total required capacity must be either handled by a single pump or subdivided between several duplicate pumps

operating in parallel.

• Industrial power plants generally use several pumpsIndustrial power plants generally use several pumps.

• Central stations tend to use single full-capacity pumps to serve turbo-generators up to a rating of 100 or even 200 MW and two pumps in parallel for larger installations.

Cross-section, single 65,000 hp boiler feed pump,

1300 MW f

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Suction Conditions

Suct o Co d t o s

• The net positive suction head (NPSH) represents the net p ( ) p suction head at the pump suction, referred to the pump centerline, over and above the vapor pressure of the feedwater

feedwater.

• If the pump takes its suction from a deaerating heater, the

feedwater in the storage space is under a pressure equivalent to the vapor pressure corresponding to its temperature.

• Therefore the NPSH is equal to the static submergence between the water level in the storage space and the pump between the water level in the storage space and the pump centerline less the frictional losses in the intervening piping.

• Theoretically, the required NPSH is independent of operating temperature. • Practically this temperature must be taken into account when establishing the • Practically, this temperature must be taken into account when establishing the

recommended submergence from the deaerator to the boiler-feed pump.

• A margin of safety must be added to the theoretical required NPSH to protect the boiler-feed pumps against the transient conditions that follow a sudden reduction boiler-feed pumps against the transient conditions that follow a sudden reduction in load for the main turbogenerator.

• The discharge pressure of the condensate pump or the booster pump must be carefully established so the suction pressure of the boiler-feed pump cannot fall carefully established so the suction pressure of the boiler-feed pump cannot fall below the sum of the vapor pressure at pumping temperature and the required NPSH.

• Careful attention must be given to any strainer that might be installed in theCareful attention must be given to any strainer that might be installed in the pump suction piping.

• The pressure drop increase across the strainer is indicative of foreign material and it reduces the net positive suction head available (NPSHA) to the pump and it reduces the net positive suction head available (NPSHA) to the pump. • Strainers in the pump suction pipe are most often removed following plant

Transient Conditions Following Load Reduction

• Following a sudden load reduction, the turbine governor reduces the steam flow in order to maintain the proper relation between turbine and generator power and to hold the unit at synchronous turbine and generator power and to hold the unit at synchronous speed.

• The consequence of this reduction is a proportionate pressure reduction at all successive turbine stages, including the bleed stage that supplies steam to the deaerator.

• The check valve in the extraction line closes and isolates theThe check valve in the extraction line closes and isolates the heater from the turbine.

• As hot feedwater continues to be withdrawn from the heater and cold condensate to be admitted to the heater, the pressure in the direct-contact heater starts to drop rapidly.

• The check valve reopens when the heater pressure has beenThe check valve reopens when the heater pressure has been reduced to the prevailing extraction pressure and stable

Alternate Means for Low Load Conditions

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oad Co d t o s

• In the event that circumstances do not permit the provision of sufficient NPSH margin to provide adequate protection to the sufficient NPSH margin to provide adequate protection to the boiler-feed pumps during a sudden turbine load reduction, two alternate means are available to compensate for these

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circumstances:

• A small amount of steam from the boiler can be admitted to the direct-contact heater through a pressure-reducing valve, to g p g , reduce the rate of pressure decay in the heater.

• A small amount of cold condensate from the discharge of the

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condensate pumps can be made to bypass all or some of the closed heaters and be injected at the boiler-feed pump suction to subcool the feedwater, thus providing additional NPSH

BOOSTER PUMPS

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• The increasing sizes of modern boiler-feed pumps coupled with the practice of operating these pumps at speeds p p g p p p

considerably higher than 3600 rpm have led to NPSH requirements as high as 46 to 76 m.

I t it i t ti l t i t ll th di t t t

• In most cases, it is not practical to install the direct-contact heaters from which the feed pumps take their suction high enough to meet such requirements.

• In such cases, it has become the practice to use boiler-feed

booster pumps operating at lower speeds, such as 1750 rpm, to provide a greater available NPSH to the boiler feed pumps

provide a greater available NPSH to the boiler-feed pumps than can be made available from strictly static elevation differences.

• Such booster pumps are generally of the single-stage, double-suction design.

Axially split case multistage boiler feed pump, up

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Radially split, segmental ring boiler feed pump

t 240 b

Radially split, double-case, barrel boiler feed pump

b

250 b

High-Speed, High-Pressure Boiler Feed Pumps

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• As steam pressures rose to 200 to 310 bar—the total head that was required to be developed by the pump rose to as high as was required to be developed by the pump rose to as high as 2140 and 3660 m.

• The only means available of achieving these higher heads at y g g 3000 rpm was to increase impeller diameter and the number of stages.

• The pumps had to have longer and longer shafts to • The pumps had to have longer and longer shafts to

accommodate the larger number of stages.

• This threatened to interfere with the long uninterrupted life g p between overhauls to which steam power plant operators were beginning to become accustomed.

Th l i l l ti t d th h ft b d i

• The logical solution was to reduce the shaft span by reducing the number of stages.

Drives for Boiler Feed Pumps

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• There are many factors which affect the driving modes of y g BFP, such as thermal economy and operational reliability,

amount of equipment investment and complexity of the system structure etc

structure, etc.

• Among the factors above, thermal economy is one of the most important factors when choosing the driving mode of BFP. • As is well known, there are two driving types that are

International View : Motor Driven BFPs

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• The designers and owners of coal-fired power plants in g p p

Western European countries tend to adopt motor-driven pumps system to feed water for boiler.

Th f th h i th t i t l ffi i f ll

• The reasons for the choice are that internal efficiency of small steam turbines which drive feed water pumps in their countries is almost equivalent to the product of the efficiency of power transmission and internal efficiency of low-pressure cylinder of main steam turbine.

• On this premise an integrated investment of motor driven feed • On this premise, an integrated investment of motor-driven feed

water pump system is lower than that of steam-driven feed water pump.

International View : Steam Driven BFPs

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• Other people such as American, Russian and Japanese

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consider that steam-driven mode is superior to motor-driven mode.

• The cause of this choice is that the internal efficiency of theThe cause of this choice is that the internal efficiency of the small steam turbine produced by companies in their countries has much higher than the product of the efficiency of power transmission and internal efficienc of lo press re c linder transmission and internal efficiency of low-pressure cylinder of main steam turbine.

• In other word, the net output of generating unit which has , p g g steam-driven feed water pumps is more than that of the same generating unit which feed water system is driven by

electromotor electromotor.

New Methods for Comparison

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• A new method called equivalent work efficiency rate to q y

evaluation thermal economy of the two main feed water pump driving modes.

Th l l ti f th t i f d t

• Thermal economy evaluation of the two main feed water pump driving modes.

• The heat consumption rate and comprehensive cost-based coal e eat co su pt o ate a d co p e e s ve cost based coa consumption based on the principle of energy value analysis.

COMPARISON OF THEIR HEAT CONSUMPTION

RATE

RATE

• Description of heat consumption ratep p • Analysis and discuss of an example

Description of heat consumption rate

• Generally speaking, heat consumption rate (HR) is the key indicator to determine thermal economy of thermodynamic

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cycle and operation of the turbine generator unit.

• From different point of view, it has two expression forms, one known as the gross heat rate, and the other called the net heat known as the gross heat rate, and the other called the net heat rate.

• Heat consumption rate is defined as the amount heat which

d 1kWh l i i b i i

generated 1kWh electricity by generating unit.

• For different thermodynamic cycle, the formula of heat rate has different expression forms.

has different expression forms.

• To the intermediate reheating unit whose boiler water is fed by motor-driven pump, the gross heat consumption rate can be expressed as

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The net heat consumption rate can be expressed as Formula

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To the intermediate reheating unit whose boiler water is fed by steam-driven pump the gross and net heat consumption rate are steam-driven pump, the gross and net heat consumption rate are formulated as

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Analysis of A Case Study

• As the actual operation of generating unit and the configuration parameters of motor-driven pumps were not exactly the same in

different generating unit the net heat rate of motor driven pump was different generating unit, the net heat rate of motor-driven pump was calculated based on an average power consumption of a variety of motor-driven pumps.

• These thermal calculations were preformed for a plan of condensing turbine-driven pump, and then net heat consumption rates in

different operation conditions were obtained different operation conditions were obtained.

• According to the average power of electromotor units and the

original design gross heat rates of the generator units, the net heat consumption rates of motor-driven constant speed pumps and

motor-driven variable speed pumps in the sliding pressure modes were calculated respectively after taken into account enthalpy rise in p y py feed water pump.

NET HEAT CONSUMPTION RATES OF FEED

WATER PUMP DRIVEN BY STEAM AND ELECTRICITY OF WATER PUMP DRIVEN BY STEAM AND ELECTRICITY OF

Comparison : Steam & Constant Speed Motor

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• Thermal economy of steam- driven pumps is better than that of y p p motor-driven pumps in different operation loads.

• In particular, thermal economy of constant speed electric pump

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declines quickly in low loads.

• As their operating speed is not adjusted, constant speed

electric pumps work in the variable load by reducing the pump

e ect c pu ps wo t e va ab e oad by educ g t e pu p

outlet pressure by the way of regulating flow which can be

performed by altering the pump speed through a throttle valve, so that thermal efficiency of generating units in low load

so that thermal efficiency of generating units in low-load declines much.

Comparison : Steam & Variable Speed Motor

C d h f h d i d f i bl d

• Compared to that of the motor-driven mode of variable speed, thermal economy of units which use steam-driven pumps to feed water in full load has increased but not significantly.g y

• Better at low load interval from 50% to 90%.

• The main reason is that the efficiency of hydraulic coupler is much lower than that of small steam turbine (SST) driving feed water pump particularly in low load, and there are

electro-mechanical loss and power transmission loss. p

• The internal efficiency of SST changes slightly in variable load conditions, although it is lower than that of main turbine in full

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load.

• At the same time SST can drive directly feed water pumps,

resulting in better thermal economy, because intermediate link of g y, energy conversion and transmission is few.

EQUIVALENT WORK EFFICIENCY

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• Relative equivalent work efficiency rate is defined that the q y ratio of power consumption of motor-driven pumps and electricity which can be generated in steam turbine by the equivalent enthalpy drops of the steam flow from extraction equivalent enthalpy drops of the steam flow from extraction point entering into SST.

• This definition can reflect thermal economy of energy owned by steam and electricity.

• The calculation method by equivalent work efficiency is easy to understand and be performed simultaneously avoiding the to understand and be performed, simultaneously avoiding the computational precision difficulty of small steam turbine

Comprehensive Cost-based Coal Consumption rate

• On the basis of the principle of energy value analysis, the term of comprehensive cost-based coal consumption the term of comprehensive cost based coal consumption rate (CCCR) was brought forward, and it is defined as the following expression.

• Comprehensive power generation costs are made of the unit • Comprehensive power generation costs are made of the unit

generating cost and the cost of plant electric consumption.

• Unit generating cost can be express as the product of standard coal consumption rate for generating and unit price of standard coal

• The cost of plant electrical power consumption is equal to the product of power consumption rate and pool purchase price.

p p p p p p

The physical meaning of CCCR

• The physical meaning of CCCR is that the power consumption of standard coal when 1kWh electricity generated according to of standard coal when 1kWh electricity generated according to comprehensive generating cost.

• Comprehensive cost-based coal consumption rate is a

corrected expression of standard coal consumption rate of power supply considering monetary values of electricity and coal.

• It reflects main comprehensive cost of generating electricity essentially.

Comparison of CCCR

Co pa so o CCC

CONCLUSIONS

CO C US O S

• With the increase of unit capacity, capacity of feed water p y, p y pump correspondingly will increase.

• The steam-driven mode of the variable-speed pumps by small

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steam turbine will be more and more acceptable to much more people.

• A steam-driven mode is better than motor-driven mode in stea d ve ode s bette t a oto d ve ode thermal economy.

• Compared with motor-driven pumps, steam-driven pumps are

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good to net electrical output increases for large units, reducing the net heat rate of generating and CCCR.

• The small steam turbine driving variable-speed pumps does g p p p well in declining of power consumption rate and rising of

operation efficiency, thus it could replace motor-driven pumps i f t

• in future.

• The driving mode of boiler feed pump is mainly affected by thermal economy of system.

t e a eco o y o syste .

• Besides thermal economy of system, the driving mode of

boiler feed pump also depends on comprehensive combination

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of investment income, operating reliability, complexity of system structure.

Head Vs Flow Rate & Selection of Operating Point

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Operation of Pumps at Low Flows

• There are a number of unfavorable conditions which may occur separately or simultaneously when the pump is operated at reduced flows. Some include:

• Cases of heavy leakages from the casing, seal, and stuffing box • Deflection and shearing of shafts

• Seizure of pump internalsSeizure of pump internals • Close tolerances erosion • Separation cavitation

• Product quality degradationProduct quality degradation • Excessive hydraulic thrust • Premature bearing failures

• Each condition may dictate a different minimum flow low requirement • Each condition may dictate a different minimum flow low requirement. • The final decision on recommended minimum flow is taken after

careful “techno-economical” analysis by both the pump user and the manufacturer.

Cavitation

Ca tat o

• As the liquid flows onto the impeller of the pump it is accelerated d i i i ll i f ll (B lli)

and initially its pressure falls (Bernoulli).

• The pressure subsequently increases as the fluid leaves the impeller and as the kinetic energy is recovered in the volute chamber

chamber.

• If the pressure of the liquid falls below the vapour pressure, P_v, the liquid boils, generating vapour bubbles or cavities-cavitation.

• The bubbles are swept into higher pressure regions by the liquidThe bubbles are swept into higher pressure regions by the liquid flow, where they collapse creating pressure waves and cause mechanical damage to solid surfaces.

• Moreover, pump discharge head is reduced at flow rates above the p p g cavitation point.

• Operation under these conditions is not desirable and damages the equipment.

NPSH (Net Pressure Suction Head).

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• Net Positive Suction Head Required, NPSHr

• NPSH is one of the most widely used and least understood terms associated with pumps. Understanding the significance of NPSH is very much essential during installation as well as operation of the pumps

pumps.

• Pumps can pump only liquids, not vapors

• Rise in temperature and fall in pressure induces vaporization • NPSH as a measure to prevent liquid vaporization

• NPSH as a measure to prevent liquid vaporization

• Net Positive Suction Head (NPSH) is the total head at the suction flange of the pump less the vapor pressure converted to fluid column height of the liquid.

height of the liquid.