The writeup details the Heat Balance of BHEL 210 MW Turbine Cycle. The Input and Output steam condition of Turbines, Extractions, Deaerator, LP Heaters, Condensers etc have been computed as per the specifications of the turbine manufacturer
210 MW Turbine Cycle Heat Rate includes all parameters of Steam and Condensate at various inlets and outlets of HP, IP and LP Turbines, Condenser and also takes into consideration the regenerative HP, IP/LP Heaters in the Turbine Cycle. Well Illustrated with all diagrams.
This document describes the methodology for conducting an energy audit of a turbine cycle. It discusses collecting data on steam and water cycle parameters, measuring turbine efficiency, identifying factors that affect heat rate, and evaluating the performance of feedwater heaters. The key steps involve collecting design specifications and operational data, measuring temperatures, pressures, flows, and outputs, calculating turbine efficiency using enthalpy methods, identifying reasons for deviations from design performance, and analyzing factors like steam conditions, condenser performance, heat exchanger fouling that affect the heat rate.
This document discusses the performance calculation and monitoring of feedwater heaters in thermal power plants. There are three key variables used to monitor feedwater heater efficiency: terminal temperature difference (TTD), drain cooler approach (DCA), and feedwater temperature rise (TR). The TTD measures how close the outlet water temperature is to the saturation temperature, and a higher TTD indicates poorer performance. The DCA measures how close the drain outlet temperature is to the inlet water temperature, and a higher DCA can cause damage. These variables are calculated and trended monthly to monitor heater performance and identify any issues.
The document discusses the HP/LP bypass system used in thermal power stations. The bypass system allows live steam from the boiler to bypass the turbine and be dumped into the condenser. This allows the boiler to continue operating during turbine trips or startup before the turbine is up to temperature. It comprises HP and LP bypass valves, spray valves, and other components. The bypass system cuts startup time, allows boiler operation during trips, and helps match boiler and turbine temperatures for efficient operation.
This document discusses the calculation of heat rate and turbine cylinder efficiency for a 210 MW KWU turbine cycle. It describes the enthalpy method used to calculate heat rate, which involves measuring steam and flow parameters at various points and using steam tables to determine enthalpy values. The calculation is done in four parts: measurements, enthalpy calculations, determining hot reheat flow, and the final heat rate calculation. Turbine cylinder efficiency is also calculated using enthalpy drop methods by determining actual and theoretical enthalpy changes across the high pressure turbine. Standard methods and typical heat rates for different capacity turbines are also listed.
Feedwater heaters are used in thermal power plants to pre-heat feedwater and improve cycle efficiency. They extract steam from various turbine stages and use it to heat incoming feedwater in stages. This reduces the amount of heat needed in the boiler and lowers the condenser pressure, improving efficiency. Feedwater heaters come in low-pressure and high-pressure varieties and utilize extracted steam in shell-and-tube or open heat exchangers. Their performance impacts the overall plant heat rate and emissions. Maintaining optimal temperatures and addressing issues like fouling or leaks is important for efficiency.
This document describes the thermal power cycle of a steam turbine power plant. It includes diagrams of the boiler, turbines, condenser and other components. It discusses the efficiencies of the boiler (86.5%), high pressure turbine (81.11%), intermediate pressure turbine (89.83%) and low pressure turbine (85%). It states that the overall steam cycle efficiency is 40%, with 60% of heat being removed by the condenser. Losses at each stage are also outlined.
210 MW Turbine Cycle Heat Rate includes all parameters of Steam and Condensate at various inlets and outlets of HP, IP and LP Turbines, Condenser and also takes into consideration the regenerative HP, IP/LP Heaters in the Turbine Cycle. Well Illustrated with all diagrams.
This document describes the methodology for conducting an energy audit of a turbine cycle. It discusses collecting data on steam and water cycle parameters, measuring turbine efficiency, identifying factors that affect heat rate, and evaluating the performance of feedwater heaters. The key steps involve collecting design specifications and operational data, measuring temperatures, pressures, flows, and outputs, calculating turbine efficiency using enthalpy methods, identifying reasons for deviations from design performance, and analyzing factors like steam conditions, condenser performance, heat exchanger fouling that affect the heat rate.
This document discusses the performance calculation and monitoring of feedwater heaters in thermal power plants. There are three key variables used to monitor feedwater heater efficiency: terminal temperature difference (TTD), drain cooler approach (DCA), and feedwater temperature rise (TR). The TTD measures how close the outlet water temperature is to the saturation temperature, and a higher TTD indicates poorer performance. The DCA measures how close the drain outlet temperature is to the inlet water temperature, and a higher DCA can cause damage. These variables are calculated and trended monthly to monitor heater performance and identify any issues.
The document discusses the HP/LP bypass system used in thermal power stations. The bypass system allows live steam from the boiler to bypass the turbine and be dumped into the condenser. This allows the boiler to continue operating during turbine trips or startup before the turbine is up to temperature. It comprises HP and LP bypass valves, spray valves, and other components. The bypass system cuts startup time, allows boiler operation during trips, and helps match boiler and turbine temperatures for efficient operation.
This document discusses the calculation of heat rate and turbine cylinder efficiency for a 210 MW KWU turbine cycle. It describes the enthalpy method used to calculate heat rate, which involves measuring steam and flow parameters at various points and using steam tables to determine enthalpy values. The calculation is done in four parts: measurements, enthalpy calculations, determining hot reheat flow, and the final heat rate calculation. Turbine cylinder efficiency is also calculated using enthalpy drop methods by determining actual and theoretical enthalpy changes across the high pressure turbine. Standard methods and typical heat rates for different capacity turbines are also listed.
Feedwater heaters are used in thermal power plants to pre-heat feedwater and improve cycle efficiency. They extract steam from various turbine stages and use it to heat incoming feedwater in stages. This reduces the amount of heat needed in the boiler and lowers the condenser pressure, improving efficiency. Feedwater heaters come in low-pressure and high-pressure varieties and utilize extracted steam in shell-and-tube or open heat exchangers. Their performance impacts the overall plant heat rate and emissions. Maintaining optimal temperatures and addressing issues like fouling or leaks is important for efficiency.
This document describes the thermal power cycle of a steam turbine power plant. It includes diagrams of the boiler, turbines, condenser and other components. It discusses the efficiencies of the boiler (86.5%), high pressure turbine (81.11%), intermediate pressure turbine (89.83%) and low pressure turbine (85%). It states that the overall steam cycle efficiency is 40%, with 60% of heat being removed by the condenser. Losses at each stage are also outlined.
This document discusses heat rate audits in thermal power plants. It aims to identify causes of efficiency losses that increase heat rate. Some key points:
- Heat rate is the amount of heat input (fuel) required per unit of power generated and impacts generation costs. Lower heat rates reduce costs.
- Losses occur in the boiler, turbine, condenser/feedwater systems, circulating water system, and from electrical/steam auxiliaries.
- Common causes of higher heat rates include incomplete combustion, turbine erosion, condenser tube fouling, and electrical auxiliary inefficiencies.
- Tracking plant parameters and conducting monthly performance tests can identify losses and guide improvement efforts to lower heat rates.
The document provides instructions for various operations at a thermal power plant, including:
1) Charging the PRDS system and opening associated valves.
2) Opening valves in the cooling water system and starting the cooling water pump.
3) Heating the deaerator and establishing feedwater flow to the boiler by regulating valves.
4) Starting the boiler feed pumps and monitoring associated parameters.
5) Charging the main steam lines and monitoring drum level and flue gas temperatures.
6) Building condenser vacuum by opening air vents and valves, starting the ejectors, and admitting gland sealing steam.
Improve plant heat rate with feedwater heater controlHossam Zein
This document discusses improving thermal efficiency in power plants by optimizing feedwater heater performance and control. It contains the following key points:
1. Small deviations in heat rate can have large impacts on annual fuel costs, so precise control of feedwater heater levels is important for efficiency. Poor level control leads to heat losses.
2. Feedwater heaters use extraction steam to preheat feedwater and improve boiler efficiency. Accurate level control ensures optimal heat transfer. Instrument errors can degrade performance.
3. Two case studies show how unreliable level controls increased annual fuel costs by $243,000 in one plant and led to excessive heater bypasses in another. Updating controls provided paybacks of 1
MS Lines, Turbine Casings and rotors and other steam lines including Steam Stop Valves, MSV, CV, ESV heating, Turbine Rolling, Flange and Stud heating, Turbovisory and speeding the turbine to 3000 RPM.
The document discusses the turbine protection system of a thermal power plant. It describes 13 different turbine trip conditions such as low lube oil pressure, high drum level, low main steam temperature, high exhaust steam temperature, fire protection operation, axial shift limits, low vacuum, high hydrogen cooler temperatures, high exciter air temperatures, liquid in bushings, master fuel trip, generator faults, and emergency trip from control room. It provides details on the logic, sensors, and mechanisms for each protection system to safely trip the turbine during abnormal operating conditions.
The presentation details about the Boiler Operation specifically while lightup of boiler and loading of boiler. the course participants discuss in details about the operations carried in their respective power stations
Turbine Stress Control Logic, Calculation & WorkingTahoor Alam Khan
Turbine Stress Control is one of the complex logics of BHEL turbine. This presentation clearly explains the Logic, working, calculations and influence of the same on operation of steam turbine. For further details and understanding, I can be reached on tahoorkhn03@gmail.com.
The Presentation describes the basics about the Efficiency and performance of a steam based power plant. It also describes how the heat rate of the power plant is important from the point of view of fuel savings.
The document provides details about the cooling and sealing system of a 247MVA turbo generator. It describes the generator specifications including rating, connection type, phases, rated speed, and insulation class. It then summarizes the need for generator cooling using hydrogen gas and water to minimize heat and ensure uniform temperature distribution. The rotor and stator cooling systems are explained along with specifications. Finally, the generator sealing system is outlined, which uses seal oil to prevent hydrogen leakage and maintain differential pressure between the oil and hydrogen.
This document provides information on performing routine online tests of high pressure feedwater heaters (HPH). It describes the objectives of the tests, required instrumentation, test procedures including data collection over 30 minutes, and calculations to analyze the results. Key parameters examined include terminal temperature difference (TTD), drain cooler approach temperature (DCA), and extraction steam flow. Sample test report formats are also provided.
This document contains:
1) A block diagram of the plant Rankine cycle showing the main steam, high pressure turbine, intermediate pressure turbine, and low pressure turbine.
2) Heat and mass balance diagrams for the high pressure and low pressure sections of the plant, showing temperatures, pressures, enthalpies, and mass flows throughout the system.
3) A section on important heat rate formulas, defining heat rate as the heat input required to produce a unit of electrical output, and providing the specific guaranteed and actual heat rates for the plant.
Boiler Follow Mode: The boiler is divorced from the generation control, which means the steam turbine utilizes stored energy in the boiler to provide immediate load response. The boiler must then change firing rate to bring pressure back to setpoint.
Turbine Follow Mode: Turbine control valves maintain a set pressure while the boiler fires to maintain load. Drawback here is a slower generation response. There are variations with this scheme, in that the turbine control valves can be fully opened at higher loads to minimize the energy penalty associated with the DP loss across them. In that case, it has been called sliding-pressure control, or even cascade control.
Coordinated Control: In general, you provide various logic schemes to move the steam turbine valves for quick load response, as well as fire the boiler for the anticipated energy requirements of the boiler (generally via an energy balance equation).
Thermal Power Plant Simulator, Cold, warm and Hot rolling of Steam TurbineManohar Tatwawadi
The presentation describes the cold rolling, warm rolling and hot rolling and synchronising of steam turbine. The Temperature Matching Chart for Turbine metal and Steam is also discussed in the presentation
This document discusses vapor power cycles and combined power cycles. It provides information on sub-systems in a vapor power plant with a focus on sub-system A. The document then discusses the Rankine cycle as the ideal cycle for vapor power plants and compares it to the Carnot cycle. It also discusses the sequence of processes in the ideal Rankine cycle and performing energy analysis on the cycle. The document continues discussing actual vapor power cycles compared to the ideal cycle and ways to increase the efficiency of the Rankine cycle such as lowering condenser pressure, superheating steam, and increasing boiler pressure.
This document discusses heat rate audits in thermal power plants. It aims to identify causes of efficiency losses that increase heat rate. Some key points:
- Heat rate is the amount of heat input (fuel) required per unit of power generated and impacts generation costs. Lower heat rates reduce costs.
- Losses occur in the boiler, turbine, condenser/feedwater systems, circulating water system, and from electrical/steam auxiliaries.
- Common causes of higher heat rates include incomplete combustion, turbine erosion, condenser tube fouling, and electrical auxiliary inefficiencies.
- Tracking plant parameters and conducting monthly performance tests can identify losses and guide improvement efforts to lower heat rates.
The document provides instructions for various operations at a thermal power plant, including:
1) Charging the PRDS system and opening associated valves.
2) Opening valves in the cooling water system and starting the cooling water pump.
3) Heating the deaerator and establishing feedwater flow to the boiler by regulating valves.
4) Starting the boiler feed pumps and monitoring associated parameters.
5) Charging the main steam lines and monitoring drum level and flue gas temperatures.
6) Building condenser vacuum by opening air vents and valves, starting the ejectors, and admitting gland sealing steam.
Improve plant heat rate with feedwater heater controlHossam Zein
This document discusses improving thermal efficiency in power plants by optimizing feedwater heater performance and control. It contains the following key points:
1. Small deviations in heat rate can have large impacts on annual fuel costs, so precise control of feedwater heater levels is important for efficiency. Poor level control leads to heat losses.
2. Feedwater heaters use extraction steam to preheat feedwater and improve boiler efficiency. Accurate level control ensures optimal heat transfer. Instrument errors can degrade performance.
3. Two case studies show how unreliable level controls increased annual fuel costs by $243,000 in one plant and led to excessive heater bypasses in another. Updating controls provided paybacks of 1
MS Lines, Turbine Casings and rotors and other steam lines including Steam Stop Valves, MSV, CV, ESV heating, Turbine Rolling, Flange and Stud heating, Turbovisory and speeding the turbine to 3000 RPM.
The document discusses the turbine protection system of a thermal power plant. It describes 13 different turbine trip conditions such as low lube oil pressure, high drum level, low main steam temperature, high exhaust steam temperature, fire protection operation, axial shift limits, low vacuum, high hydrogen cooler temperatures, high exciter air temperatures, liquid in bushings, master fuel trip, generator faults, and emergency trip from control room. It provides details on the logic, sensors, and mechanisms for each protection system to safely trip the turbine during abnormal operating conditions.
The presentation details about the Boiler Operation specifically while lightup of boiler and loading of boiler. the course participants discuss in details about the operations carried in their respective power stations
Turbine Stress Control Logic, Calculation & WorkingTahoor Alam Khan
Turbine Stress Control is one of the complex logics of BHEL turbine. This presentation clearly explains the Logic, working, calculations and influence of the same on operation of steam turbine. For further details and understanding, I can be reached on tahoorkhn03@gmail.com.
The Presentation describes the basics about the Efficiency and performance of a steam based power plant. It also describes how the heat rate of the power plant is important from the point of view of fuel savings.
The document provides details about the cooling and sealing system of a 247MVA turbo generator. It describes the generator specifications including rating, connection type, phases, rated speed, and insulation class. It then summarizes the need for generator cooling using hydrogen gas and water to minimize heat and ensure uniform temperature distribution. The rotor and stator cooling systems are explained along with specifications. Finally, the generator sealing system is outlined, which uses seal oil to prevent hydrogen leakage and maintain differential pressure between the oil and hydrogen.
This document provides information on performing routine online tests of high pressure feedwater heaters (HPH). It describes the objectives of the tests, required instrumentation, test procedures including data collection over 30 minutes, and calculations to analyze the results. Key parameters examined include terminal temperature difference (TTD), drain cooler approach temperature (DCA), and extraction steam flow. Sample test report formats are also provided.
This document contains:
1) A block diagram of the plant Rankine cycle showing the main steam, high pressure turbine, intermediate pressure turbine, and low pressure turbine.
2) Heat and mass balance diagrams for the high pressure and low pressure sections of the plant, showing temperatures, pressures, enthalpies, and mass flows throughout the system.
3) A section on important heat rate formulas, defining heat rate as the heat input required to produce a unit of electrical output, and providing the specific guaranteed and actual heat rates for the plant.
Boiler Follow Mode: The boiler is divorced from the generation control, which means the steam turbine utilizes stored energy in the boiler to provide immediate load response. The boiler must then change firing rate to bring pressure back to setpoint.
Turbine Follow Mode: Turbine control valves maintain a set pressure while the boiler fires to maintain load. Drawback here is a slower generation response. There are variations with this scheme, in that the turbine control valves can be fully opened at higher loads to minimize the energy penalty associated with the DP loss across them. In that case, it has been called sliding-pressure control, or even cascade control.
Coordinated Control: In general, you provide various logic schemes to move the steam turbine valves for quick load response, as well as fire the boiler for the anticipated energy requirements of the boiler (generally via an energy balance equation).
Thermal Power Plant Simulator, Cold, warm and Hot rolling of Steam TurbineManohar Tatwawadi
The presentation describes the cold rolling, warm rolling and hot rolling and synchronising of steam turbine. The Temperature Matching Chart for Turbine metal and Steam is also discussed in the presentation
This document discusses vapor power cycles and combined power cycles. It provides information on sub-systems in a vapor power plant with a focus on sub-system A. The document then discusses the Rankine cycle as the ideal cycle for vapor power plants and compares it to the Carnot cycle. It also discusses the sequence of processes in the ideal Rankine cycle and performing energy analysis on the cycle. The document continues discussing actual vapor power cycles compared to the ideal cycle and ways to increase the efficiency of the Rankine cycle such as lowering condenser pressure, superheating steam, and increasing boiler pressure.
Thermodynamic Cycles for Power Generation—Brief Review
Real Steam Power Plants—General Considerations
Steam-Turbine Internal Efficiency and Expansion Lines
Closed Feed water Heaters (Surface Heaters)
The Steam Turbine
Turbine-Cycle Heat Balance and Heat and Mass Balance Diagrams
Steam-Turbine Power Plant System Performance Analysis Considerations
Second-Law Analysis of Steam-Turbine Power Plants
Gas-Turbine Power Plant Systems
Combined-Cycle Power Plant Systems
This document discusses performance assessment of cogeneration plants with gas and steam turbines. It outlines procedures for measuring heat rate and efficiency, including collecting steam and power output data during testing. An example calculation is provided for a small cogeneration plant producing 100kW of power from a back pressure turbine using 5.1 tonnes/hour of steam. The turbine efficiency is calculated as 34% and the overall plant efficiency is 30.6%. Questions are also provided regarding turbine heat rate, cylinder efficiency, parameters for efficiency evaluation, and the need for performance assessment.
This document is a seminar report submitted by Rabindra Kumar Guin on the topic of thermal power plants. It provides an overview of the major equipment used in thermal power plants, including boilers, turbines, condensers, pumps, and more. It also explains the basic working principle of the Rankine cycle used in thermal power generation, where heat is converted to mechanical work and then electrical energy. The report discusses the advantages and disadvantages of thermal power plants and concludes by discussing opportunities to improve efficiency and reduce emissions from these important sources of electricity.
Engineering applications of thermodynamicsNisarg Amin
The document discusses different thermodynamic cycles used in steam power plants, including Rankine, reheat, and regeneration cycles. It provides diagrams and equations to analyze each cycle. The Rankine cycle involves boiling water to steam, expanding the steam in a turbine, condensing it back to water, and pumping the water to high pressure. Both the reheat and regeneration cycles improve the Rankine cycle efficiency by adding additional heat transfer processes. The reheat cycle reheats steam after the high-pressure turbine, while regeneration uses feedwater heating to preheat water before boiling.
The document provides details about an industrial training project at the Wanakbori Thermal Power Station (WTPS). It includes:
1) An acknowledgment thanking those who facilitated the training.
2) An index outlining the topics to be covered, including details of the boiler, turbine, condenser, coal handling plant, and more.
3) An abstract stating the aim was to study the mechanical instruments involved in power generation and improve practical knowledge.
The document discusses Heat Recovery Steam Generators (HRSGs). HRSGs recover heat from gas turbine exhaust to produce steam. They operate in either combined cycle mode, where steam drives a turbine, or cogeneration mode where steam is used for industrial processes. HRSGs contain evaporator, economizer, and superheater sections to produce steam. They can also include reheaters, deaerators, and preheaters. HRSGs come in natural circulation, forced circulation, or once-through designs and can be unfired, fired, supplementary fired, or exhaust fired depending on heat input. HRSGs vary in operation pressure as either single or multi-pressure. Post-combustion emission controls like
The document proposes replacing pressure reducing valves (PRVs) with backpressure steam turbine-generators at a heat plant to increase efficiency. Currently, PRVs reduce steam pressure from 180 psig to 25 psig without recovering work. Installing a turbine would capture this pressure reduction as electricity. Calculations show the turbine cycle would achieve an efficiency of 77.2% versus 76.6% for the PRV cycle. Case studies at other universities found turbines reduced emissions by 1,200-2,000 metric tons annually and saved $120,000-275,000 per year. A pre-design analysis identified space in the plant basement as optimal for a turbine, which could fit through double doors and utilize existing steam piping.
The document provides details about Akshaya Kumar Bakshi's summer internship report at Pragati Power Corporation Limited (PPCL). It summarizes that PPCL is a Delhi government undertaking that generates power through various gas-based combined cycle power plants. It describes PPCL's key projects including the 1500 MW Pragati-III CCGT project in Bawana, Delhi. The document then provides technical details about the components, systems, cycles and operation of PPCL's gas turbine and steam turbine power generation process.
the presentation describes in details about the feed water and condensate heaters used in Thermal Power Stations or elsewhere. The performance parameters of the heaters are also described in details.
This document discusses performance assessment of cogeneration systems with steam and gas turbines. It provides definitions of key performance terms like plant heat rate and turbine cylinder efficiency. It outlines the purpose of performance testing being to determine power output and plant heat rate. The document describes test procedures for steam turbine cogeneration systems including required measurements, calculations of thermal and electrical energy, and an example calculation for a small cogeneration plant.
This document discusses vapor power cycles and combined power cycles. It covers the Carnot vapor cycle and how the Rankine cycle is better suited as a model for vapor power plants. Methods to increase the efficiency of the Rankine cycle are analyzed, including lowering the condenser pressure, superheating steam, increasing boiler pressure, using reheat cycles, and regenerative cycles. Combined cycles and cogeneration are also introduced.
This document proposes three options for a waste heat recovery system and heat pump to reduce fuel consumption and improve energy efficiency at a process plant. Option 1 involves using recovered heat from oven exhausts and a compressor to heat pretreatment bath tanks. Option 2 uses recovered heat to pre-heat oven intake air and heat one pretreatment tank. Option 3 combines options 1 and 2 with a heat pump to heat additional pretreatment tanks. Calculations estimate potential heat sources, energy and cost savings for each option. Diagrams illustrate the proposed air to water and air to air heat recovery approaches.
Improvement of rankine efficinecy of steam power plantsDhilip Pugalenthi
The Rankine cycle is a thermodynamic cycle that generates about 80% of the world's electricity. It uses a heat source to boil water into high-pressure steam, which powers a turbine connected to an electric generator. The reduced-energy steam is then condensed into liquid water and pumped back to repeat the cycle. Improving the Rankine cycle involves increasing the steam temperature and pressure through techniques like superheating, reheating, and raising boiler pressure to boost efficiency. The cycle is limited by materials constraints but remains the dominant method for generating electricity from heat.
Pinch analysis technique to optimize heat exchangerK Vivek Varkey
This document summarizes a student project applying pinch analysis to optimize the heat exchanger network (HEN) for a CFU unit at an ONGC Hazira plant. The student calculated heat duties for 5 heat exchangers and determined the minimum hot and cold utility requirements. By drawing temperature interval diagrams, the student designed an optimized HEN that couples process streams to maximize heat exchange and minimize utility needs. The optimized design was found to reduce heating utility needs by 83.4% and cooling needs by 33.8% compared to the current design.
This document describes the design of a 1 MW power plant based on a superheated Rankine cycle. Key components include a steam generator with economizer, boiler and superheater sections, a high pressure turbine operating from 100-20 bar, a low pressure turbine from 20-0.1 bar, a condenser, an open feedwater heater containing a deaerator, a closed feedwater heater, and a reheater. Thermodynamic calculations are shown to select locations and operating conditions for these components. Performance is calculated with a net work output of 968.28 kW, heat input of 2557.14 kW, and heat rejected of 2358.52 kW.
In any thermal power generation plant, heat energy converts into mechanical work. Then it is converted to electrical energy by rotating a generator which produces electrical energy.
Thermal power plants generate electricity through combustion of fuels like coal and gas. The key components are the boiler, steam turbine, and electric generator. Control systems regulate critical functions like fuel and air management, steam temperatures, feedwater levels, and turbine speed. Supercritical plants operate at higher pressures and temperatures for greater efficiency. Combined cycle plants further improve efficiency by capturing waste heat from gas turbines to power additional steam turbines.
Similar to 210 MW BHEL Turbine Cycle Heat Balance (20)
The presentation is based on the discussions of starting operations of a coal based thermal power plant. This presentation is based on the in-house training to the operation engineers of the thermal power plant. It describes the activity chart for the starting of boiler, Turbine and synchronising of Generator, picking up the load etc.
This is a presentation series part 3 on Frequently Asked Questions on Steam Turbines in large steam power plants. All questions are answered properly and any doubt may be mailed to the writer.
Green building concepts and good building practicesManohar Tatwawadi
The power sector must adopt the green building concepts and go for good building practices. In fact all industries need to go for the same. The same practices can also be adopted in all commercial as well as residential buildings.
Auxiliary Consumption and Saving due to Increase in Boiler EfficiencyManohar Tatwawadi
Discussions on Auxiliary consumption in a 4 X 210 MW TPS, the common systems and individual unitwise Auxiliary consumption has been briefed in the presentation. Also savings in various aspects due to increase in Boiler Efficiency are also discussed in the presentation.
COMPRESSED AIR SYSTEM . ENERGY CONSERVATION OPPORTUNITIESManohar Tatwawadi
The presentation gives an idea as to how the compressed air system is designed and the performance of the compressed air system. The losses, conservation of energy, the cost of leakages etc are discussed in the presentation
This document contains frequently asked questions and answers about steam turbines. It discusses issues like speed variation, vibration, deposits, erosion, washing, compounding, and monitoring. Questions cover topics such as reducing speed variation through governor adjustments, the effects of deposits on efficiency, solid particle erosion, monitoring internal efficiency, and reducing vibration damage through blade design modifications. Causes and remedies of issues like governor lubrication problems, safety trip valve trips, and foreign particle damage are also addressed.
- A stage in an impulse turbine consists of moving blades behind a nozzle, while in a reaction turbine each row of blades is a stage.
- Diaphragms hold the nozzles and seals between turbine stages. Tip leakage is a problem in reaction turbines where steam escapes across moving blade tips.
- Thrust bearings maintain the rotor's axial position, while radial bearings support the rotor at each end of the steam cylinder and must be accurately aligned.
- Deposits in a turbine can be detected through pressure monitoring, efficiency monitoring, and exhaust steam temperature monitoring. Deposits are removed through washing with condensate or wet steam for water soluble deposits and mechanically after dismantling for water insoluble
The presentation gives a basic idea of cooling towers in big industries including the Power Plants. The performance of cooling towers and the commonenly used terms with reference to the cooling towers are also discussed at length. Care to be taken while in freezing temperatures in the European countries is also discussed.
The presentation is based on the discussions about the safety in Power Plants and substations. The presentation is a part of the seminar on Electrical safety and reliability. The reporting of accidents was also discussed at length in the seminar
Cost accounting, cost control and cost reduction in TPSManohar Tatwawadi
The subject matter discuss in details about the cost accounting being practiced in a thermal power station for calculating the actual cost of generation of electricity. The cost centres and the cost affecting factors alongwith steps to reduce the cost of generation are described in the presentation. The PPMS system adopted can be further be well designed by any power plant engineer.
Environmental and pollution control in Thermal Power StationsManohar Tatwawadi
The presentation gives the basic idea as to the environment, pollutions and laws, the governing bodies and the limits of the emmissions. Also specifically about the solid waste, liquid waste and the gas emmissions from the Thermal Power Plants.
Energy Audit & Energy Conservation Opportunities in Electrical Equipments ...Manohar Tatwawadi
The discussion is for the Energy Conservation drive in the thermal power plants in the Auxilliary Consumption of the Electrical Auxilliaries in the Plant and thereby identify the steps to be taken for the reduction in Auxilliary Consumption
The presentation details the process of combustion in a 500 MW Coal based Thermal Power Plant where the main fuel is Pulverised coal. It details about the combustion of coal partical in the furnace and also the combustion equations related to the process, the excess air that is supplied.
The presentation gives an idea about the primary requirements for the establishment of a coal based THERMAL POWER STATION. The estimates are quite fair.
The discussion on "Handling of Turbines During Emergencies" has been detailed in the ppt. Some case studies are also discussed in the session where the course participants express their difficulties while coming across the emergencies in handling the turbines at their locations.
Effect of Coal Quality and Performance of Coal pulverisers / MillsManohar Tatwawadi
The presentation discusses about the change in performance parameters of a pulveriser due to change in coal quality and the measurement of performance and troubleshooting of coal firing system as a whole.
ENERGY AUDIT METHODOLOGY FOR TURBINE CYCLE IN A POWER PLANTManohar Tatwawadi
This document outlines the methodology for conducting an energy audit of a turbine cycle. It discusses collecting operational data on the steam turbine and associated equipment. Key measurements of steam and water parameters throughout the cycle are described. The document explains evaluating the turbine's heat rate and efficiency using enthalpy calculations. Factors that could impact the heat rate such as equipment performance, operating conditions and maintenance issues are identified. Methods to analyze the performance of feedwater heaters and determine deviations are also provided.
This document discusses biomass power plants and provides calculations to determine the amount of biomass needed to generate 1 megawatt hour (MWh) of electricity. It explains that biomass is considered carbon neutral, as long as it is replanted and harvested sustainably. Common sources of biomass for fuel are then outlined, along with their composition and heating values. A simple calculation is presented that determines about 0.72 kilograms of biomass on a moisture-and-ash-free basis is needed to generate 1 MWh, with adjustments made depending on the biomass moisture content and ash percentage. Annual biomass requirements are estimated for a sample 5 megawatt biomass power plant.
This document discusses various strategic planning tools including SWOT analysis, Porter's five forces analysis, competitor analysis, and resource gap analysis. SWOT analysis involves analyzing internal strengths and weaknesses as well as external opportunities and threats. Porter's five forces model examines the competitive environment through analyzing the threat of new entrants, bargaining power of suppliers and buyers, threat of substitutes, and rivalry among existing competitors. Competitor analysis assesses a competitor's objectives, strategies, assumptions, capabilities, and potential responses. Resource gap analysis identifies performance gaps between business requirements and current capabilities to determine investment needs.
Boiler Drum level measurement in Thermal Power StationsManohar Tatwawadi
The paper describes the basics of Boiler Drum water Level measurement in a Thermal Power Station. The Single element and three element control has been described in a very simple manner. Useful for the Thermal Engineers
artificial intelligence and data science contents.pptxGauravCar
What is artificial intelligence? Artificial intelligence is the ability of a computer or computer-controlled robot to perform tasks that are commonly associated with the intellectual processes characteristic of humans, such as the ability to reason.
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Artificial intelligence (AI) | Definitio
An improved modulation technique suitable for a three level flying capacitor ...IJECEIAES
This research paper introduces an innovative modulation technique for controlling a 3-level flying capacitor multilevel inverter (FCMLI), aiming to streamline the modulation process in contrast to conventional methods. The proposed
simplified modulation technique paves the way for more straightforward and
efficient control of multilevel inverters, enabling their widespread adoption and
integration into modern power electronic systems. Through the amalgamation of
sinusoidal pulse width modulation (SPWM) with a high-frequency square wave
pulse, this controlling technique attains energy equilibrium across the coupling
capacitor. The modulation scheme incorporates a simplified switching pattern
and a decreased count of voltage references, thereby simplifying the control
algorithm.
Software Engineering and Project Management - Introduction, Modeling Concepts...Prakhyath Rai
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Building the Analysis Models: Requirement Analysis, Analysis Model Approaches, Data modeling Concepts, Object Oriented Analysis, Scenario-Based Modeling, Flow-Oriented Modeling, class Based Modeling, Creating a Behavioral Model.
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4. Mosca vol I -Fisica-Tipler-5ta-Edicion-Vol-1.pdf
210 MW BHEL Turbine Cycle Heat Balance
1. MANOHAR TATWAWADI total output power solutions Page 1
210 MW BHEL Turbine Cycle Heat Balance
Calculation of Heat Rate of 210 MW BHEL Turbine Cycle with Regenerative Feed Water Heating
consisting of seven feed water heaters shown in the schematic flow diagram attached.
From station to station the C.W. Temp for the condenser cooling changes and therefore the vacuum
conditions and the exhaust temperature also changes accordingly. A specimen calculation shown has
been done for the values at 652000 kgs of steam per hour flow at 130 kg/cm2
absolute pressure and
5550
C superheat Temperature. Similar such calculations can be done at different loads for calculation of
heat rate of the turbine regenerative feed water heating cycle at those particular loads.
While calculating the Turbine Heat Rate following assumptions have been made in the original drawings,
giving the values of Enthalpy and other Properties.
1. Under cooling in the drain coolers of Heater No 6 and heater No 7 has been taken as 100
C. The
effect of drain cooler of Heater No 5 has been ignored.
2. Wherever a dash has been given in place of reading, the equipment is inoperative in that range.
3. The values of temperatures mentioned are approximate. Whenever the steam is wet (especially
at the LP Exhaust), instead of giving the temperature, dryness fraction has been mentioned in
the temperature column.
4. When press in Heater No 5 approaches 10.5 Kg/cm2
absolute, drain from Heater No 6 is diverted
to Deaerator bypassing Heater No 6 and drain of Heater No 5 is diverted to Heater No 4.
5. The Specific Heat Rate does not include the consumption of steam in the main Ejector.
Similar such calculations for the turbine heat rate can also be carried out for over load working of TA set
at 215.78 MW and at 211.05 MW Loads, at 670 T/hr steam flow and with 3% makeup water added to
the Hotwell of Condenser and at different cooling water temperatures ranging from 300
C to 360
C at
Condenser inlet. A separate calculation can also be done to calculate the turbine heat rate when HP
Heaters are out of service at 206.135 MW Load.
These figures should however, be not taken as guaranteed performance figures and will vary from
station to station depending upon the actual working conditions, age of stations etc.
1) INTRODUCTION
Before calculating the Turbine Heat Rate we shall first consider the stage by stage efficiency of the
Turbine Cycle.
A Complete Turbine Cycle single line schematic diagram is as per attached drawing, wherein the
parameters for Steam, Condensate and Feed water are marked for full load. Similar such chart can be
worked out by inserting the values for the parameters calculated from BHEL Drawing No C-210-
130/TDC-210-60.2. The Turbine Cycle Diagram indicates the direction of flow of various fluids involved.
2. MANOHAR TATWAWADI total output power solutions Page 2
2) STAGE BY STAGE EFFICIENCY
2.1 Ejector:-
Ejector is supplied with steam from Deaerator (d4) at 4.5Kg/cm2
having 1550
C Temp and the condensate
from hotwell passes through the same, which is pumped by the condensate extraction pump to the
further feed water regenerative heating cycle. The ejector drain is recovered back to the flash chamber
on the condenser. Calculations have been made assuming the efficiency of 99.8% for the Ejector from
which the Enthalpy / Temperature for the drain from the Ejector to the Flash Chamber is derived.
2.2 Gland Steam Condenser GC1:-
The Gland Steam Condenser GC1, which is next to the Ejector in the regenerative feed water heating
cycle, sucks steam and air mixture from outermost HP, IP and LP Turbine glands. The necessary required
vacuum of about 100 mm is established in the Gland Steam Condenser by an Ejector, which is provided
with steam (d2) from the Deaerator. The condensate (gd1) is recovered back to the flash chamber on
the condenser. From the calculations it is seen that the efficiency of the Gland Steam Condenser No 1 is
99.7%.
3. MANOHAR TATWAWADI total output power solutions Page 3
2.3 LP Heater No 1:-
The Feed water Heater 1 (LP Heater No 1) is fed with Extraction Steam (e1) from the Extraction No 1 on
LP Turbine and the heater drain (hd1) is fed to the flash chamber on condenser. The condensate after
GC1 flows through Heater No 1. From the calculations shown in the sketch the efficiency comes to
99.80%.
2.4 Gland Steam Condenser No 2:-
Gland Steam Condenser No 2 is fed with Leakage steam from HP and IP Turbine Glands and the drain
from GC2 is recovered back to flash tank on the condenser. As per the calculations shown in the sketch,
the efficiency comes to 80%, because not all the condensate at full load passes through GC2. However,
actually a part of the condensate is bypassed over GC2. The efficiency of GC2 drops accordingly. That is
to say that if 80% of the condensate is passing through GC2, the efficiency drops to 80%.
4. MANOHAR TATWAWADI total output power solutions Page 4
2.5 LP Heater No 2:-
The steam from IP Turbine Extraction No 2 (e2) is fed to the feed water heater LP Heater No. 2. The
drain (hd2) is pumped back with the help of Drip Pump into the main condensate flow path before the
condensate entry to Heater no 3 as shown. This also increases the temperature of condensate from
100.860
C to 1o1.520
C at the entry in Heater No 3. From the calculations as above the efficiency of LP
Heater No 2 comes to 99.8%.
2.6 LP Heater No 3:-
Heater No 3 is provided with steam from IP Turbine Extraction No 3 (e3) and the drain from heater no 4
(hd4) is also fed back to heater No 3. It may also be noted that the amount of condensate passing
through heater No 3 increases in quantity by the amount of drain from heater No 2 (hd2). Heater no 3
drain is fed back to LP Heater No 2. The calculated efficiency of LP Heater No 3 comes to 99.8%.
5. MANOHAR TATWAWADI total output power solutions Page 5
2.7 LP Heater no 4:-
LP Heater No 4 is fed with Extraction steam from IP Turbine (e4). Leakage steam from HP and IP Glands
(g3) is also fed to the LP Heater No 4. Drain from LP Heater No 4 is fed back to LP Heater No 3. HP Heater
No 5 drain (hd5) is cascaded to LP Heater No 4 below 150 MW load. For loads more than 150 MW HP
Heater No 5 drain normally goes to Deaerator. In the calculations at full load, HP Heater No 5 drain (hd5)
is not considered as fed to Heater No 4. The calculated Efficiency comes to 99.7%.
2.8 Deaerator:-
Dearator is supplied with heating steam from Extraction tapped from either Extraction no 5 or
Extraction No 6 (ed). Extraction No 5 is taken from IP Turbine and Extraction No 6 is taken from HP
Turbine at HP Exhaust. For loads below 150 MW, deaerator heating steam supply (ed) is derived from
Extraction No 6, which is changed over to Extraction No 5 at loads above 150 MW. Auxiliary steam
supply to the main Ejector, Gland steam ejector and sealing steam of Turbine Glands is changed over
from auxiliary PRDS to Deaerator.
6. MANOHAR TATWAWADI total output power solutions Page 6
The Deaerator pegging steam supply is initially given from auxiliary PRDS, which is changed over from
auxiliary source to Extraction No 6 at about 90 to 100 MW Load.
The gland leakage from ESV and IV is fed to the deaerator. Heater No 5 and Heater No 6 Drains (hd5 or
hd6) are also fed to the deaerator. Actually HP Heaters are taken in service after 60 to 70 MW Load is
taken on the turbine. Heater No 5 Drain (hd5) goes to Heater No 4 for loads less than 150 MW. For
Turbine loads higher than 170 MW, Heater No 6 Drain (hd6) goes to Heater No 5. And heater no 5 drain
(hd5) is diverted to Deaerator instead of Heater No 4. From the heat balance calculations, the deaerator
efficiency comes to 96.8%.
2.9 Boiler Feed Pump:-
It may be noted that the total quantity of feed water supplied from feed water tank to boiler feed water
pump is equal to main steam flow to the HP Turbine.
In this connection, it may be noted that heat added by Boiler Feed water pump due to Mechanical
churning of water has been also taken into consideration, which is equal to 4179320 Kcal.
2.10 HP Heater No 5:-
HP Heaters are taken into service in block after a load of 60 to 70 MW is taken on the turbogenerator.
HP Heater No 5 is supplied with steam from Extraction No 5 (e5) taken from IP Turbine. Heater No 5
Drain (hd5) goes to Heater No 4 below 150 MW, which is changed over to Deaerator at loads more than
7. MANOHAR TATWAWADI total output power solutions Page 7
170 MW. Heater No 6 Drain (hd6) is cascaded to Heater no 5. From the heat balance calculations the
efficiency of HP Heater No 5 comes to 93.7%.
2.11 HP Heater No 6:-
Heater No 6 is supplied with steam from Extraction No 6 (e6) from HPT Exhaust. It is cold reheat steam.
The spindle leakage steam from HPT (g5) is also fed to Heater No 6. Heater No 7 Drain (hd7) is cascaded
to Heater no 6 and Heater no 6 drain (hd6) is cascaded to Heater No 5. From the calculations the
efficiency is 99.7%.
2.12 HP Heater No 7:-
Heater No 7 is provided with Extraction steam from HP Turbine (e7). The drain (hd7) is cascaded to
Heater No 6. Feed water at the outlet of the heater is finally fed to back to the boiler through the feed
water regulating valve. From the calculations the efficiency comes out to be 99.5%.
8. MANOHAR TATWAWADI total output power solutions Page 8
2.13 Condenser:-
210 MW Turbine has two condensers connected in parallel. The total quantity of the condensed steam
exhausted from the LP Turbine is mixed with drains from Ejector consisting of condensate of steam from
Deaerator(d4) and GC1 condensate of steam from HPT and IPT.
The steam from LPT at a Pressure of 0.0889Kg/cm2 and quantity 460008 kg/hr is condensed by cooling
water quantity 270000 m3 which equals to 27000000 kg/hr and hence the circulating water required for
cooling 1 kg of steam is 27000000/460008 = 58.6 kg.
From the heat balance equation of condenser:-
The total heat loss to cooling water = Steam from LPT Exhaust * Enthalpy of water at Hotwell
= 2 X 230004 * (589.18 – 43.16) = 251173568 Kcal/hr.
If the condenser efficiency is assumed to be 80% then the gain in temp of cooling water
= (251173568/0.8)/27000000 = 110
C
From the calculations shown it will be seen that if 270000 m3
/h water flow is maintained for the
circulating water through the condenser having 80% efficiency the terminal temperature difference for
the circulating water will be of the order of 110
C.
9. MANOHAR TATWAWADI total output power solutions Page 9
3) TURBINE CYCLE HEAT RATE
The turbine cycle heat rate is calculated as per the formula:-
Total Heat Supplied to the Turbine in kcal QM*(MSE - FWE) + QR*(RHE - CRHE)
Heat Rate =
Total Generation in KWH W
QM= Main Steam Flow = 652000 Kg/hr
MSE= Main Steam Enthalpy = 819.94 Kcal/kg
FWE= Feed Water Enthalpy at HP7 Outlet = 253.94 kcal/kg
QR = Reheat Steam Flow = 566369 kg/hr
RHE = Enthalpy of Reheat Steam = 845.83 Kcal/kg
CRHE= Enthalpy of Cold Reheat Steam = 732.99 Kcal/kg
W = Total Power Developed at Generator output in KWH = 211902 KWH
652000 * (819.94 - 253.94) + 566369 * (845.83 – 732.99)
HR at 210 MW =
211902
652000 * 566 + 566369 * 112.84 432941078
= = = 2043.11 Kcal/KWH
211902 211902
Calculated Heat Rates at different loads are :-
a) 2043.11 Kcal/KWH at 210 MW
b) 2068 Kcal/KWH at 176 MW,
c) 2070 Kcal/KWH at 150 MW and
d) 2156 Kcal/KWH at 100 MW
4) EXTRACTIONS
4.1 Total Heat given to Turbine Cylinders
High Pressure Turbine
Flow Enthalpy Heat in Kcal
Input Steam 652000 819.94 534600880
Output Steam 566369 732.99 415142813
Heat Given to HP Turbine 119458067
Intermediate Pressure Turbine
Flow Enthalpy Heat in Kcal
Input Steam 566369 845.83 479051891
Output Steam 470857 678.41 319434097
Heat Given to IP Turbine 159617794
10. MANOHAR TATWAWADI total output power solutions Page 10
Low Pressure Turbine
Flow Enthalpy Heat in Kcal
Input Steam 470857 678.41 319434097
Output Steam 460008 589.18 271027514
Heat Given to LP Turbine 48406583
Total input to the Turbine Cylinders = Heat given to HP + IP + LP Cylinders
= 119458067 + 159617794 + 48406583 = 327482444 Kcal for generating 211902 kWH of Power.
A small quantity of Leakage steam from ESV & IV spindle leaks to Deaerator and gland steam condenser,
which is also utilized for feed water regenerative heating. The condensate derived thereby is also added
in the system. The heat content of this auxiliary steam is neglected.
4.2 The total quantity of steam extracted for regeneration
Symbol Work Pressure Temp. Flow Enthalpy Total Heat
e1 Extraction 1 LP Heater 1 0.8895 45 11989 622.05 7,457,757
e2 Extraction 2 LP Heater 2 1.369 183 25369 678.41 17,210,583
e3 Extraction 3 LP Heater 3 2.974 264 21033 715.68 15,052,897
e4 Extraction 4 LP Heater 4 6.911 364 23838 762.69 18,181,004
ed Steam to Deaerator Deaerator 12.96 449 5984 802.92 4,804,673
e5 Extraction 5 HP Heater 5 12.96 444 16640 802.92 13,360,589
e6 Extraction 6 HP Heater 6 28.07 327 40391 732.99 29,606,199
e7 Extraction 7 HP Heater 7 42.18 381 31844 755.97 24,073,109
Total Extraction Flow / Enthalpy 177088 TPH 129,746,812
Total Steam Extracted*100 177088 * 100
Percentage of quantity of steam extracted = = = 27.16%
Total Steam supplied 652000
Total Heat to Extractions *100 129746812*100
Percentage of Heat Tapped = = = 39.61%
Total Heat input to the cylinders 327482444
Out of the above heat given to the extractions, total heat regained by feed water regenerative heating
cycle:-
Upto LP Heater No 2 480106 * (100.86-43.16) = 27702116 Kcal
After LP Heater No 3 555281 * (156.52 – 100.86) = 30906940 Kcal
After Deaerator 555281 * (166.71 – 156.52) = 5658313 Kcal
In Feed water Pump 652000 * (173.12 – 166.71) = 4179320 Kcal
After HP Heater 7 652000 * (253.94 – 173.12) = 52694640 Kcal
Total heat regained by Feed Water = 121141330 Kcal
11. MANOHAR TATWAWADI total output power solutions Page 11
Heat Loss in Feed Water Regenerative Heating Cycle = Total heat to extractions – Heat regained
= 129746812 – 121141330 = 8605482 Kcal
4.3 Total Heat Lost to cooling water
= (Enthalpy of steam at exhaust – Enthalpy of condensate in Hotwell)* Quantity of Exhaust steam
= (589.18 – 43.16) * 460008 = 251173568 Kcal
4.4 Turbine gross heat rate
Turbine Heat Input - (Heat Extracted from all Ext.)+(Heat Lost in Regen. Heating)+ ( Heat Lost to CW)
Power Generated
327482444 – 129746812 + 8605482 + 251173568
211902
= 2159 Kcal/kwh
4.5 Specific Steam Consumption
At normal specified steam pressure and temperature of Main Steam and Reheat Steam Specific Steam
Consumption of this turbine is as below:-
Load in kw 211902 202000 176669 151400 101200
Specific Steam Consumption 3.004 2.966 3.006 3.045 3.077
(in Kg/kwh)
******************
12. MANOHAR TATWAWADI total output power solutions Page 12
210 MW Parameters at different regimes at CW Temp 300
C
S.N
PARAMETERS PRESSURE IN KG/SQCM ABS TEMPERATURE / DRYNESS
Regime IN KW 211902 202200 176669 151400 101200 211902 202200 176669 151400
10120
0
A MAIN STEAM
1 MAIN STEAM 130 130 130 130 130 535 535 535 535 535
2 COLD REHEAT (CRH) 28.07 26.4 22.52 18.96 12.22 327 322 311 301 286
3 HOT REHEAT (HRH) 24.19 23.2 20.17 17.22 11.46 535 535 535 535 535
3.1 STEAM AFTER IPT 1.369 1.299 1.134 0.971 0.6725 183 184 184 185 190
3.2 STEAM BEFORE LPT 1.343 1.274 1.118 0.9519 0.6594 183 183 183 183 183
4
LPT EXHAUST TO
COND 0.0889 0.086 0.0798 0.0739 0.0637 0.9529 0.9549 0.9001 0.9663
B EXTRACTION STEAM
e7 TO HEATER NO 7 42.18 39.77 34.38 29.06 19.68 381 375 364 354 349
e6 TO HEATER NO 6 28.07 26.7 22.58 18.96 12.22 327 322 311 301 286
e5 TO HEATER NO 5 12.96 12.27 10.65 9.068 6.2 444 444 444 444 446
ed TO DEAERATOR 12.96 12.27 10.65 9.068 12.22 444 444 444 444 286
e4 TO HEATER NO 4 6.911 6.545 5.694 4.858 3.334 364 364 364 365 365
e3 TO HEATER NO 3 2.974 2.808 2.453 2.097 1.44 264 265 265 265 271
e2 TO HEATER NO 2 1.369 1.299 1.134 0.971 0.6729 183 184 184 185 190
e1 TO HEATER NO 1 0.2895 0.2754 0.241 0.2073 0.1449 0.992 0.9935 0.9965 61 68
C SERVICE STEAM
d1 TO GLAND SEALING 1.03 143
d2 TO EJECTOR OF GC1 4.5 155
d3 LEAKAGE INTO LPT 0.0889 0.086 0.0798 0.0739 0.0637 139
d4 TP MAIN EJECTOR 4.5 155
D LEAK OFF STEAM
g1 TO GLAND COOLER 1 0.97 286
g2 TO GLAND COOLER 2 0.361 0.343 0.308 0.265 0.197 346 337 329 318 296
g3 TO HEATER 4 6.911 6.545 5.694 4.853 3.334 403 400 393 386 383
g4
FROM SPINDLES TO
DEAERATOR 7.5 479
g5 TO HEATER 5 28.07 26.4 22.98 18.96 12.22 464 457 448 438 433
13. MANOHAR TATWAWADI total output power solutions Page 13
210 MW Parameters at different regimes at CW Temp 300
C
Tag
No
PARAMETERS ENTHALPY KCAL/KG QUANTITY IN KG/HR
Regime IN KW 211902 202200 176669 151400 101200 211902 202200 176669 151400 101200
A MAIN STEAM
1 MAIN STEAM 819.94 819.94 819.94 819.94 819.94 652000 616000 531000 449000 304000
2 COLD REHEAT (CRH) 732.99 730.57 727.11 723.41 720.69 566369 534409 484930 395441 259703
3 HOT REHEAT (HRH) 845.83 846.22 846.86 847.54 848.82 566369 534409 484930 395441 259703
3.1 STEAM AFTER IPT 678.41 678.84 679.34 680 682.82 470857 447226 390074 333899 230723
3.2 STEAM BEFORE LPT 678.41 678.84 679.34 680 682.82 470857 447226 390074 333899 230723
4
EXHAUST STEAM TO
COND 589.18 590.08 592.41 595.31 606.03 230024 218790 191648 134954 115604
B EXTRACTION STEAM
e7 TO HEATER NO 7 755.97 753.53 750.42 746.79 746.64 31844 29654 24925 20263 13294
e6 TO HEATER NO 6 732.99 730.57 727.11 723.41 720.65 40391 37134 29752 23261 4638
e5 TO HEATER NO 5 802.92 803.23 803.88 804.52 808.2 16440 13129 6605 545
ed TO DEAERATOR 802.92 803.23 803.88 804.52 720.69 5984 7937 11610 14306 18728
e4 TO HEATER NO 4 762.69 763.02 763.73 764.56 767.84 23838 22311 18460 14945 3108
e3 TO HEATER NO 3 715.68 716.07 716.63 717.2 720.32 21033 19547 16312 13584 8488
e2 TO HEATER NO 2 678.41 678.84 679.36 680 682.32 25369 13756 19679 16276 10038
e1 TO HEATER NO 1 622.05 622.43 623.07 623.78 626.45 11989 10787 7919 5132 634
C SERVICE STEAM
d1 TO GLAND SEALING 659.83 2930
d2 TO EJECTOR OF GC1 659.8 400
d3 LEAKAGE INTO LPT 659.83 570
d4 TP MAIN EJECTOR 659.83 1500
D LEAK OFF STEAM
g1 TO GLAND COOLER 1 728.2 728.22 728.29 728.36 728.48 1260
g2 TO GLAND COOLER 2 756.8 752.66 748.77 743.1 732.92 4949 4733 4225 3735 2863
g3 TO HEATER 4 782.31 780.58 777.65 774.47 773.97 4935 4663 4020 3399 2301
g4
FROM SPINDLES TO
DEAERATOR 820.28 820.29 820.32 820.35 820.39 2300
g5 TO HEATER 5 806.5 803.66 799.78 795.63 795.4 4381 4140 3568 3017 2043
14. MANOHAR TATWAWADI total output power solutions Page 14
210 MW Parameters at different regimes at CW Temp 300
C
Tag
No
PARAMETERS ENTHALPY KCAL/KG QUANTITY IN KG/HR
Regime IN KW 211902 202200 176669 151400 101200 211902 202200 176669 151400 101200
E CONDENSATE
5.0 HOTWELL 43.16 42.53 41.11 39.66 36.92 460008 437577 383296 329907 231289
5.W CEP SUCTION 43.16 42.53 41.11 39.66 36.92 480106 456529 398599 341934 237891
5.D BEFORE EJECTOR 43.16 42.53 41.11 39.66 36.92 480106 456529 398599 341934 237891
5.A AFTER EJECTOR 45.07 44.54 43.41 43.35 40.79 480106 456529 398599 341934 237891
5.1 AFTER GC1 47.18 46.76 45.96 45.32 44.86 480106 456529 398599 341934 237891
5.2 AFTER HEATER 1 61.05 59.92 57.08 53.77 46.35 480106 456529 398599 341934 237891
5.3 AFTER GC2 68.1 66.99 64.29 61.17 54.47 480106 456529 398599 341934 237891
5.4 AFTER HEATER 2 100.86 99.31 95.9 91.07 81.32 480106 456529 398599 341934 237891
5.5 BEFORE HEATER 3 101.52 99.97 96.12 91.69 81.87 555281 526534 463675 390683 376826
5.6 AFTER HEATER 3 125.27 123.83 118.85 113.82 102.33 555281 526534 463675 390683 376826
5.7 AFTER HEATER 4 156.52 154.33 148.83 143.18 129.23 555281 526534 463675 390683 376826
F FEED WATER
6.0 BFP SUCTION 166.71 652000 616000 531000 449000 304000
7.0 AFTER FEED PUMP 173.12 652000 616000 531000 449000 304000
7.1 AFTER HP HEATER 5 189.61 187.14 180.76 173.75 173.12 652000 616000 531000 449000 304000
7.2 AFTER HP HEATER 6 228.8 225.28 216.632 207.35 185.82 652000 616000 531000 449000 304000
9.0 AFTER HP HEATER 7 253.94 250.11 241.1 231.11 209.73 652000 616000 531000 449000 304000
G DRAINS
gd1 FROM GC1 100 1660
hd1 FROM HEATER NO 1 65.93 64.8 61.86 58.6 54.14 11989 10787 7919 5132 634
gd2 FROM GC2 72.94 71.78 69.26 65.97 59.38 4949 4733 4225 3735 2868
hd2 FROM HEATER NO 2 105.78 104.24 100.34 96.01 86.23 75175 70275 65076 48749 29935
hd3 FROM HEATER NO 3 130.26 128.32 123.83 118.77 107.25 49806 46519 45397 32473 19897
hd4 FROM HEATER NO 4 161.73 159.51 153.97 148.72 134.2 28773 26974 29085 18639 11409
hd5 FROM HEATER NO 5 189.51 186.91 180.38 173.22 93265 84059 6605 545
hd6 FROM HEATER NO 6 198.05 195.43 188.86 181.64 180.99 76616 70930 53245 46541 19976
hd7 FROM HEATER NO 7 238.65 234.98 225.92 216.29 194.08 31344 29654 24925 20263 13294
15. MANOHAR TATWAWADI total output power solutions Page 15
H PRESSURE IN HEATERS
HEATERS DATA AT
LOADS 211902 202200 176669 151400 101200 TTD
HP7 HEATER NO 7 38.8 36.59 31.63 26.74 18.1 2.5
HP6 HEATER NO 6 26.67 25.09 21.44 18.01 11.6 4.5
HP5 HEATER NO 5 11.92 11.29 9.8 8.343 2
LP4 HEATER NO 4 6.358 6.021 5.238 4.469 3.067 5
LP3 HEATER NO 3 2.736 2.584 2.267 1.929 1.325 5
LP2 HEATER NO 2 1.26 1.195 1.043 0.8933 0.467 5
LP1 HEATER NO 1 0.2664 0.2534 0.2217 0.1907 0.1333 5
I HEAT RATE IN KCAL/KWH
Regime IN KW 211902 202200 176669 151400 101200
HEAT RATE
Kcal/KWH 2040 2039 2051 2066 2154
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