Comparative Analysis on Performance of a Gas Turbine Power Plant with a Spray Cooler

Transcription

1 International Journal of scientific research and management (IJSRM) Volume 1 Issue 7 Pages Website: ISSN (e): Comparative Analysis on Performance of a Gas Turbine Power Plant with a Spray Cooler Padilam Naveen Kumar a, A Rama Krishna a, G. R. Vidya Sagar Raju a, a B.V.C. Engg. College, Odalarevu, A.P., India. padilamnaveenkumar@gmail.com, padilamnaveenkumar@yahoo.com Abstract: For geographic regions where major power demand and highest electricity prices occur during the warm months,a gas turbine inlet air cooling technique is a useful option for increasing output of a gas turbine power plants. The objective of this analysis was to establish the potential benefits of improving the performance of the current gas turbine plant into a more advanced cycle with high efficiency and power output through inlet cooling. The hypothesis was that low performance of the gas turbine plant was caused by high ambient temperature; the use of spray cooler was adopted to bring the air condition temperature close to ISO condition. Inlet air cooling increases the power output by taking advantage of gas turbine s feature of higher mass flow rate. Industrial gas turbines that operate at constant speed are constant volume flow combustion machines. As the specific volume of air is directly proportional to the temperature, the increase of the density results in higher mass flow rate, once the volumetric rate is constant. As a result the gas turbine power output enhances. Different methods are available for reducing compressor intake air temperature. Spray coolers make use of evaporation of water to reduce the gas turbine inlet air temperature. It is the most cost-effective system. In this analysis, performance characteristics were determined for a set of actual operational conditions including ambient temperature, relative humidity turbine inlet temperature and pressure ratio. The results obtained show that the use of a spray cooler on the existing gas turbine cycle gives better thermal efficiency. The power output of a gas turbine plant with spray cooler was found to have increased by over 6.66% accompanied by 2.72% increase in mechanical efficiency and with a reduction in specific fuel consumption of Thus the results shows that retrofitting the existing gas turbine plant with inlet air cooling system gives better plant performance. Introduction Gas turbines are used for electricity generation in most countries of the world. They can be started and stopped easily allowing them to be brought into service as required to meet energy demand at peak conditions. Because of natural gas availability and at low prices cosmpared to distillate fuels, many countries of the world, example India utilizes large conventional gas turbines as based load units. The average efficiencies of gas turbine plants in the Indian energy utility sector over the past decade was in the range 36-42%.The low efficiencies of the gas turbine plants are tired to many factors which include operation mode, poor maintenance procedures, age of plant, discrepancies in operating data, high ambient temperature and relative humidity, power output and efficiency of a gas turbine plant depends largely the condition of the compressor inlet air temperature. The performance output during hot conditions is less compared to the performance at high air temperature and humid environment, so cooling the inlet air temperature to gas turbine, increases the air density, which enhances the mass flow rate of air and gives better power output. Research has shown that gas turbine power output decreases by 15% for 10 0 C increase in compressor inlet air temperature. It has also been reported that high ambient temperature increase the turbine s heat rate resulting in gas turbine plants producing 24-33% less power in summer than winter at an average increase in 5% in fuel consumption. Many literature works have extensively investigated the turbine inlet air cooling effect on the gas turbine performance enhancement. Varnham (2010) reported that refrigerative cooling can uses vapor compression refrigeration equipment and O&M costs for mechanical chillers are cheaper than absorption systems, but capital costs are higher and parasitic power requirement can be 30% of the power gain. Jaber et al (2006) studied the influence of air cooling intake on the gas turbine performance by comparing two different cooling systems, evaporative and cooling coil. Their results showed that the evaporative cooling and chiller system present similar improvement in the power output, about MW, but the cooling coil of the mechanical chiller consumes more energy to run the vapor compression refrigeration unit and the overall plant performance decreases. ALhazmy and Najjar (2004) compare two different techniques of air coolers, water spraying system and cooling coils and the results were analyzed for a specific set of operational and design conditions.the spray coolers are less expensive than chiller coils. However, it is extremely affected by ambient temperature and relative humidity. This method is capable of reducing the ambient air temperature by 3-15 o C, Producing power augmentation by 1-7%, and increasing the efficiency by 3%. Padilam Naveen Kumar, IJSRM volume 1 issue 7 Oct 2013 [ Page 254

2 Furthermore, with the rapid increase in electricity demand in India and the expected shortages in power supply to delays in implementation of the major power projects, retrofitting the gas turbine power plants in the power sector with inlet air-pre-cooling system is an attractive investment opportunity for gas turbine power plants, India. This analysis studies the performance enhancement and modification of an active 220 MW SAMALKOT POWER STATION RELIANCE INFRASTRUCTURE LTD., INDIA, using the prevailing modified Brayton cycle is compared with base condition (without air cooling ). The above figure shows working of spray cooler. Cold water is sprayed into the dry atmospheric air entering the system with the help of injectors. The water spraying system in counter flow in evaporative cooler and modelled as an adiabatic saturator. The dry air mixes with water becoming saturated where the dry bulb temperature (DBT) of inlet air reaches initial Wet Bulb Temperature (WBT). Gas Turbine Cycle with Spray Cooler Simple Gas Turbine Cycle The above figure shows a standard gas turbine power plant consists of Spray cooler, compressor, combustion chamber and turbine. The working fluid passing through the compressor is the air, and it assumed to be an ideal gas, while in the turbine the working fluid are the flue gases. The above figure illustrates the simple gas turbine cycle. It is composed of a compressor that supplies air at high pressure to the compressor, which provides flue gas at high pressure and temperature turbine. These engines are of constant volume and their power output is directly proportional and limited by the air mass flow rate. As the compressor has a fixed capacity for a given rotational speed and volumetric flow rate of air, their volumetric capacity remains constant. Therefore, the mass flow rate of air enter into the gas turbine varies with their specific mass, which means that it depends on the temperature and the relative humidity of the ambient air. Gas turbine is critically limited by the predominating ambient temperature, mainly in hot and dry regions. It occurs because the power output is inversely proportional to the ambient temperature. The temperature drop provides an augment in the air density and consequently elevates air mass flow rate; this behaviour increases the power output and efficiency. Spray Cooler The heat interaction between the ambient air and the saturated air is presented as CP a (T a -T 1 )=(ω 1 -ω a )h fg...(1) ω =.... (2) Where ω a and ω 1 are humidity ratios before and after the saturation respectively. In general ω is related to the water vapour pressure at saturation as presented in Eq.2 (cengel and Boles, 2011), P is pressure of air at intake and P v is saturated pressure of water at intake. The cooler outlet temperature is obtained in Eq.3 T 1 =T a -(T a T wb ) x ɳ.. (3)...(4) Where T a =Ambient Temperature T 1 =Cooler Outlet Temperature T wb =Wet Bulb Temperature ɳ= Cooler efficiency The working fluid passing through the compressor is assumed to be an ideal mixture of air and water vapour. The total enthalpy of atmospheric air is given below in Eq.4, (cengel and Boles, 2011): h= h a + ω x h v =Cp x T + ω x h g... (4) Padilam Naveen Kumar, IJSRM volume 1 issue 7 Oct 2013 [ Page 255

3 Where h a = Enthalpy of dry air h v = Enthalpy of water vapour The enthalpy of water vapour can be evaluated approximately as in Eq.5,(cengel and Boles, 2011): h v = xT...(5) The total temperature of the fluid leaving the compressor having an isentropic efficiency ɳ c can be evaluated using ideal gas relation obtained in Eq.6 SFC =...(14) The specific fuel consumption is expressed in Eq.14.The Specific fuel consumption compares the ratio of the fuel used by an engine to a certain force such as the amount of power the engine produces. This is a very important economic criteria. T 02 =T 1 + = T [ -1]...(6) Where r p= Compression Ratio k =Specific Ratio Similarly the total temperature leaving the turbine having isentropic efficiency ɳ T, is given as Eq.7: Eq.8 T 04 =T 03 -ɳ T (T 3 T 4 ).. (7) The total mass flow rate of humid air is given as m. ha=m. mda+ωm. da=(1+ω)m. da...(8) Where, mda and mha are mass flow rates of humid air and dry air. The compressor work is calculated from the mass flow rate and enthalpy change across the compressor Eq. 9: w. e = m. air(1+ω)x(c pa T 02 T 1 )+ω(h 02 -h 1 )...(9) Similarly, the turbine work is obtained as Eq. 10: W T =(m air +(1+ω)+m f )x(c pg T 3 -C pg T 04 )+ω(h 3 -h 04 )...(10) The energy of exhaust gas E G is obtained as Eq. 11: E G = (m air +(1+ω)+m f )x(c pg T 04 -(C pg T 01 )+ω(h 04 -h 01 )...(11) The net power obtained from the gas turbine is Eq. 12: W net =W T -W c...(12) The thermal efficiency of the gas turbine power plant is evaluated as Eq. 13: ɳ th =...(13) Gas Turbine cycle parameters Data used for the analysis are obtained from maintenance data sheet of 220 MW SAMALKOT POWER STATION RELIANCE INFRASTRUCTURE LTD., INDIA. Description Cycle Adoption Values Single shaft, Simple cycle Industrial Turbine 1385[K] 141[kg/s] Turbine inlet temperature Air flow rate Isentropic efficiency of 85.4% Compressor Isentropic efficiency of 86.8% Turbine Combustion efficiency 99% Inlet Pressure ratio 100[mm of H 2 o] Exhaust Pressure 200 [mm of H 2 o] Combustion chamber 1.2% pressure loss Fuel, LHV Materials and Methods Natural gas; [kJ/kg Operating data for Gas turbine unit were collected from the daily turbine control log sheet for a period of two years. The daily average operating variables were calculated using MS Excel worksheets and the thermodynamic properties were determined using an Engineering Equation Software (EES). The analysis of the plant was divided into different control volumes and performance of the plant was estimated using component-wise modelling. Mass and energy conservation laws were applied to each component and the performance of the plant was determine for the simple system (without spray cooler) and for the cooled system (with spray cooler). The efficiencies of the turbine components were evaluated employing Kotas exergy models. Results for the two scenarios were compared. Results The results of the effect of spray cooler on the performance of the gas turbine plant are presented. Padilam Naveen Kumar, IJSRM volume 1 issue 7 Oct 2013 [ Page 256

4 Figure 1 and 2 shows the variation in thermal efficiency with ambient temperature and power output for cooled and simple cycles at 60% Relative Humidity (RH). Fig. 3: Specific fuel consumption versus ambient temperature for simple and cooled cycles Fig. 1: Efficiency Vs ambient temperature for simple sand cooled cycles Fig. 4: Energy of exhaust versus ambient temperature for simple and cooled cycles Discussion Fig.2: Power output Vs ambient temperature for simple and cooled cycles The power output and the efficiency of the gas turbine cycle were calculated for different ambient air temperatures and for relative humidity of 60%. Thermodynamic properties such as specific heats, humidity ratio of air, and enthalpy of steam and combustion gasses were evaluated as a function of temperature, pressure, relative humidity by using an Engineering Equation Software (EES). Figure 1 and 2 shows the variation in thermal efficiency with ambient temperature and power output for cooled and simple cycles at 60% relative humidity. From the results a degree increase in ambient temperature lead to 0.79% drop in gas turbine rated power. For low ambient temperature of 23 C (296K) and Relative Humidity (RH) at ISO standard design condition of 60%, the turbine output power increased by Padilam Naveen Kumar, IJSRM volume 1 issue 7 Oct 2013 [ Page 257

5 about 6% with a 2.1% increase in thermal efficiency. At high ambient temperature of 32 C (305K) and 60% relative humidity, the power output increased by 7.95% with a 2.7% increase in thermal efficiency. The Specific Fuel Consumption (SFC) of gas turbine decreases as the ambient temperature increases as shown in Fig. 3. At low ambient temperature of 23 C and 60% relative humidity, the specific fuel consumption drops by 0.92% and at high ambient temperature of 32 C (305K) and 60% RH,the specific fuel consumption drops by 2.0%. Figure 4 shows that at an ambient temperature of 23 C (296K) 60% relative humidity, the energy of exhaust gases increases by 8.19% and at high ambient temperature of 33 C (306K) decrease to ISO standard condition, the energy of exhaust gases increases by 10.03%. This means that lowering the inlet air temperature will lead to an increase in the exhaust gas flow rate with more heat recovered from the exhaust gases. Conclusion The performance of spray cooler is dependent on ambient temperature and humidity. The system works efficiently during dry and hot climatic conditions prevalent in some locations in India. The results obtained show that, the use of an inlet air cooling system as a measure for system enhancement was found to increase the power output of the gas turbine by over 7%, accompanied by 2.7% increase in machine efficiency. A drop in specific fuel consumption of 2.0 and 10.03% increase in energy of exhaust were observed. The irreversibility rate is less for the cooled cycle with improvement in thermal efficiency which is due to less entropy generation. However, comparing the cooled cycle and the simple cycle it was observed that for any ambient temperature and relative humidity, the cooled cycle improves all the performance indices of the gas turbine plant. The payback period for the spray cooler is between 4-5 years. Water needed for operation of sprayer may be a serious constraint in some areas, but condensing water from the exhaust system is one method for recovering partially the makeup water for spray cooler especially in extreme dry climates., in order to select a particular cooling technique for adoption in India energy utility sector, research including system performance and economic analysis of the cooling methods will appear to be merited. and Gas Turbine World Wide Gas Turbine Publications, USA. Himmelblau, D.M. and J.B. Riggs, Basic Principles and Calculations in Chemical Engineering. 8th Edn., Prentice Hall London, New Jersi, ISBN: , pp: 752. Jaber, Q.M., J.O. Jaber and M.A. Khawaldah, Assessment of power augmentation from gas turbine power plants using different inlet air cooling systems. J. Mech. Ind. Eng., 1: Johnson, R.S., The theory and operation of evaporative coolers for industrial gas turbine installations. The American Society of Mechanical Engineers, New York. Karim, Z.A.A., Effect of inlet air cooling on gas turbine performance. Proceedings of the International Conference on Mechanical and Manufacturing Engineering, (MME 08), Johor Bahru Malaysia. Kolp, D.A., W.M. Flye and H.A. Guidotti, Advantages of air conditioning and supercharging an LM6000 gas turbine Inlet. J. Eng. Gas Turbine Power Trans. ASME, 117: DOI: / Kotas, T.J., The Exergy Method of Thermal Plant Analysis. 1st Edn., Krieger Pub., Malabar, FL., ISBN-10: , pp: 328. Kumara, N.R., K.R. Krishnab and A.V.S.R. Rajuc, Performance improvement and exergy analysis of gas turbine power plant with alternative regenerator and intake air cooling. Energy Eng., 104: DOI: / Landry, M. and S. Sairan, The capacity augmentation of an 18MW gas turbine using ice Harvesting Thermal Energy Storage (TESTIAC). Power-Gen Asia, 94, Henry Vogt Machine, USA and Tenaga National Research and Development Sdn. Bhd. Malaysia. McCracker, C.D., Off-peak air-condition: Major energy save. ASHRAE J., 2: Mercer, M., One stop shop for inlet cooling systems diesel and gas turbine. Worldwide Gas Turbine Publications, USA. Mohanty, B. and J. Paloso Jr., Enhancing gas turbine performance by intake air cooling using an absorption chiller. Heat Recovery Syst. CHP, 15: DOI: / (95) Ondryas, I.S., D.A. Wilson, M. Kawamoto and G.L. Haub, Options in gas turbine power augmentation using inlet air chilling. Eng. Gas Turbine Power Trans. ASME, 113: DOI: / REFERENCES Cengel, Y.A. and M.A. Boles, Thermodynamics: An Engineering Approach. 7th Edn., McGraw-Hill, New York, ISBN-10: pp: Cortes, C.R. and D.F. Williams, Gas turbine inlet air cooling techniques: An overview of current technologies. Power-Gen International, Las Vegas Neva, USA. Culp, A.W., Principles of Energy Conversion. 1st Edn., McGraw-Hill, New York, ISBN-10: pp: 499. Elliot, J., Chilled air takes weather out of equation. Diesel Padilam Naveen Kumar, IJSRM volume 1 issue 7 Oct 2013 [ Page 258