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Optimal Design of Gas Turbine Power Station. P M V Subbarao Professor Mechanical Engineering Department. More Ideas for better fuel Economy……. 1872, Dr Franz Stikze’s Paradox. Condition for Compact Gas Turbine Power Plant. At maximum power:. Important Comments:
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Optimal Design of Gas Turbine Power Station P M V Subbarao Professor Mechanical Engineering Department More Ideas for better fuel Economy…….
Important Comments: What if I am not interested in Compactness. Should I prefer high Pressure Ratio for Efficient Plant? Why the plant is compact at this condition? What else can be inferred form this condition?
The state-of-the-art • The newer large industrial gas turbines size have increased and capable of generating as much as 200 MW at 50 Hz. • The turbine entry temperature has increased to 12600C, and the pressure ratio is 16:1. • Typical simple cycle efficiencies on natural gas are 35%. • The ABB GT 13 E2 is rated at 164 MW gross output on natural gas, with an efficiency of 35.7%. • The pressure ratio is 15:1. • The combustion system is designed for low Nox production. • The dry Nox is less than 25 ppm on natural gas. • The turbine entry temperature is 11000C and the exhaust temperature is 5250C. • The turbine has five stages, and the first two rotor stages and the first three stator stages are cooled; • the roots of the last two stages are also cooled.
Siemens power corporation described their model V84.3. • This is rated at 152 MW at an efficiency of 36.1%. The pressure ratio is 16:1. • Six burners designed for low Nox emissions are installed in each chamber. • The turbine entry temperature is 12900C and the exhaust temperature is 550 C. • The turbine has four stages and the first three rotating stages are air cooled. • The effectiveness of the cooling is improved by inter-cooling the cooling air after it is with drawn from the compressor.
General Electric and European Gas Turbines have jointly developed the MS9001F 50Hz engine. • This unit generates 215 MW at an efficiency of 35%. • The engine uses an 18 stage compressor with an overall compression ratio of order of 20:1. • The gas turbine has three stages, with the first two stages cooled. • Turbine entry temperature is 1288 C. • These large high efficiency units can be used for peak lopping purposes. • The research for more efficient gas turbine-based power generation cycles has been underway for some time. The aims are: • - Higher turbine entry gas temperature, - Higher compressor efficiency and capability
The different manufactures participated and initiated the collaborative advanced gas turbine. • The outcome of their effort include a variety of advanced cycle options, including intercooling, humid air turbine, steam injection, reheat combustor and chemical recuperation. • The U.S. Department of Energy (DOE) has initiated a development program called the advanced turbine system (ATS). • The aim of ATS is to achieve over 60% efficiency, with low Nox and suitable operating costs at the end of a 10-year program. • They pictured the program with increasing in firing temperature up to over 1427 C and changes in cycle, as intercooling, reheat combustors, massive moisture injection and chemical recuperation.
Fuel GT24 (ISO 2314 : 1989) Natural gas Frequency 60 Hz Gross Electrical output 187.7 MW* Gross Electrical efficiency 36.9 % Gross Heat rate 9251 Btu/kWh Turbine speed 3600 rpm Compressor pressure ratio 32:1 Exhaust gas flow 445 kg/s Exhaust gas temperature 612 °C NOx emissions (corr. to 15% O2,dry) < 25 vppm
Fuel Natural gas Frequency 60 Hz Gross Electrical output 187.7 MW* Gross Electrical efficiency 36.9 % Gross Heat rate 9251 Btu/kWh Turbine speed 3600 rpm Compressor pressure ratio 32:1 Exhaust gas flow 445 kg/s Exhaust gas temperature 612 °C NOx emissions (corr. to 15% O2,dry) < 25 vppm 9756 kJ/kWh
The Ideal Machine • 1824: Sadi Carnot, who founded the science of thermodynamics, identified several fundamental ideas that would be incorporated in later internal combustion engines: • He noted that air compressed by a ratio of 15 to 1 would be hot enough (200°C) to ignite dry wood. • He recommended compressing the air before combustion. Fuel could then be added by "an easily invented injector". • Carnot realized that the cylinder walls would require cooling to permit continuous operation. • Later, Diesel thought he could avoid this, but found out the hard way. • He noted that usable heat would be available in the exhaust, and recommended passing it under a water boiler.
Developments in Gas Turbine Cycles • The wet compression (WC) cycle • The steam injected gas turbine (STIG) cycle • The integrated WC & STIG (SWC) cycle • Themo-chemical Recuperation cycles
Wet compression • One of the most effective ways to increase the gas turbine power output is to reduce the amount of work required for its compressor. • A gas turbine compressor consumes about 30 to 50% of work produced by the turbine.
P Representing wet compression process on P-V diagram W isothermal = f-1-2T-g-f (isothermal) Wwet compression = f-1-2K-g-f (wet compression) W isentropic = f-1-2S-g-f (isentropic) W polytropic = f-1-2n-g-f (polytropic) P 2T 2k 2s 2n g 2 f 1 P 1 0 V
The wet compression (WC) cycle • The wet compression cycle has the following benefits over the simple cycle. • Lower compressor work • Higher turbine work • Higher cycle efficiency
ISENTROPIC INDEX OF WET COMPRESSION PROCESS • Isentropic index of wet compression can be obtained from the equation Where k=Isentropic index of wet compression, dw/dT = Evaporative rate kg/k, L= Latent heat kJ/kg, R=Gas constant of humid air kJ/kg k.
ACTUAL WET COMPRESSION INDEX • Actual wet compression index can be obtained from the equation Where m=polytropic index of actual wet compression process, n=polytropic index of actual dry air compression
Compressor work with wet compression • Compressor work with wet compression is a function of • Pressure ratio , • Evaporative rate dw/dT and • Geometry of the compressor. • Wet compression work is much lower than that of dry air compression work. • The higher is the pressure ratio, more the saving in compressor work.
Variation of wet compression work with pressure ratio (Evaporative rate dw/dT=7.5e-4 kg/k)
VARIATION OF WET COMPRESSION WORK WITH THE EVAPORATIVE RATE FOR A GIVEN PRESSURE RATIO Pressure ratio = 7
REAL WET COMPRESSION WORK CONSIDERING OFF DESIGN BEHAVIOUR • For calculation purposes, if the design (dry) value of the polytropic efficiency is assumed to be maintained throughout the compression process, it is tantamount to the operation of the compressor at increased operating pressure ratio.
Comparison of Work Input For Wet and Dry Compression Considering Off-Design Behaviour
ACTUAL WET COMPRESSION WORK CONSIDERING OFF DESIGN BEHAVIOUR
Fuel Natural gas Frequency 60 Hz Gross Electrical output 187.7 MW* Gross Electrical efficiency 36.9 % Gross Heat rate 9251 Btu/kWh Turbine speed 3600 rpm Compressor pressure ratio 32:1 Exhaust gas flow 445 kg/s Exhaust gas temperature 612 °C NOx emissions (corr. to 15% O2,dry) < 25 vppm 9756 kJ/kWh
Super Heated Steam Water
The steam injected gas turbine (STIG) cycle • Steam injection into the combustion chamber of a gas turbine is one of the ways to achieve power augmentation and efficiency gain. • In a steam injected gas turbine (STIG), the heat of exhaust gasses of the gas turbine is used to produce steam in a heat recovery steam generator. • The steam is injected into the combustion chamber or before entering the combustion chamber (i.e. in the compressor discharge). • STIG cycle has higher cycle efficiency than the WC cycle. • STIG cycle gives higher net work out put than the WC cycle up to a pressure ratio of 7.
The integrated WC & STIG (SWC) cycle • It has the combined benefit of the advantage of higher efficiency of STIG cycle and higher net work output of WC cycle. • But its cycle efficiency is less than that of the STIG cycle owing to the need for higher heat input.
COMPARISION BETWEEN SIMPLE, WC, STIG AND INTEGRATED WC & STIG CYCLES
Comparison of typical parameters of simple, WC,STIG and SWC cycles.
Future work There are many areas and challenges which can be explored further to this work. They are: • Economic feasibility of these cycles need to be studied. • Compressor life reduction due to water injection. (because of the off design running conditions that prevail in reality). • The difficulties involved in designing a turbine to handle large mass flow rates of combustion gasses and steam. • The effect of steam injection in reducing NOX emissions.
A tree converts disorder to order with a little help from the Sun
Clues from Nature to get Better Fuel One of such clue is Thermo Chemical Recuperation The major reactions involved in Steam-TCR are well known, and the overall reaction for a general hydrocarbon fuel, CnHm, is:
The formation of carbon must be minimized in the operation of the reformer to minimize fouling of heat transfer surfaces, blinding of catalyst particles, plugging of flow paths and carbon losses.
The theoretical merits of the Steam-TCR concept are based on the overall endothermic nature of the reforming chemical reactions, and the formation of a low-thermal-value fuel gas replacing the high-thermal-value turbine fuel, with both factors contributing to improved efficiency
The chemical Reactions in Flue Gas TCR Cycle • Combustion of Methane with 100% theoretical air. Thermochemical recuperator: Reforming of Flue Gas Only • Combustion of reformed flue gas :
The chemical Reactions in Flue Gas & Methane TCR Cycle • Thermochemical recuperator: Reforming of Flue gas with methane • Combustion of reformed flue gas and methane mixture:
First Law Analysis of Thermochemical Recuperator Cooled exhust Turbine Exhaust Reformed fuel Fuel & Flue gas No work transfer, no heat transfer, change in kinetic and potential energies are negligible Energy lost by turbine exhaust = Increase in energy of reformed gas.
