Thermal Analysis of Open-Cycle Regenerator Gas-Turbine Power-Plant

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1 Thermal Analysis of Open-Cyle Regenerator Gas-Turbine Power-Plant M. M. Rahman, Thamir K. Ibrahim, M. Y. Taib, M. M. Noor, K. Kadirgama and Rosli A. Bakar Abstrat Regenerative gas turbine engine yle is presented that yields higher yle effiienies than simple yle operating under the same onditions. The power output, effiieny and speifi fuel onsumption are simulated with respet to operating onditions. The analytial formulae about the relation to determine the thermal effiieny are derived taking into aount the effeted operation onditions (ambient temperature, ompression ratio, regenerator effetiveness, ompressor effiieny, turbine effiieny and turbine inlet temperature). Model alulations for a wide range of parameters are presented, as are omparisons with simple gas turbine yle. The power output and thermal effiieny are found to be inreasing with the regenerative effetiveness, and the ompressor and turbine effiienies. The effiieny inreased with inrease the ompression ratio to 5, then effiieny dereased with inreased ompression ratio, but in simple yle the thermal effiieny always inrease with inreased in ompression ratio. The inreased in ambient temperature aused dereased thermal effiieny, but the inreased in turbine inlet temperature inrease thermal effiieny. Keywords Gas turbine; power plant; thermal analysis; regeneration I. INTRODUCTION HE open-yle gas turbines offered low apital osts, Tompatness, and effiieny lose to that of the steam plants. Nevertheless, after the oil risis in the 197s the effiieny of power plants beame the top priority, and ombined-yle plants, first in the form of existing steam plant repowering, and later, as speially-designed gas-and-steam turbine plants, have beome a ommon power plant onfiguration [1]. Gas turbines that operate in simple yles have low effiienies beause the turbine exhaust gases ome out very hot and this energy is lost to the atmosphere. Better performane is reahed with advaned yles that take advantage of the energy ontained in the turbine exhaust gases to improve the yle or to transfer energy to ombined yles [], []. In gas-turbine power plant, the temperature of the exhaust gas leaving the turbine is often onsiderably higher than the temperature of the air leaving the ompressor. Therefore, the air leaving the ompressor at high-pressure an be heated by transferring heat to it from the hot exhaust gases in a ounter-flow heat exhanger, whih is also known as a regenerator or reuperator [4]. Authors are with Faulty of Mehanial Engineering, Universiti Malaysia Pahang., Kuantan, Malaysia. mustafizur@ump.edu.my Gas turbine regenerators are usually onstruted as shell-andtube type heat exhangers using very small diameter tubes, with the high pressure air inside the tubes and low pressure exhaust gas in multiple passes outside the tubes. The thermal effiieny of the Brayton yle inreases as a result of regeneration sine the portion of energy of the exhaust gases that is normally rejeted to the surroundings is now used to preheat the air entering the ombustion hamber. This, in turn, dereases the heat input (thus fuel) requirements for the same net work output. Note, however, that the use of a regenerator is reommended only when the turbine exhaust temperature is higher than the ompressor exit temperature. Otherwise, heat will flow in the reverse diretion (to the exhaust gases), dereasing the effiieny. This situation is enountered in gas turbines operating at very high-pressure ratios [5]. A regenerator with a higher effetiveness will save a greater amount of fuel sine it will preheat the air to a higher temperature prior to ombustion [6]. However, ahieving a higher effetiveness requires the use of a larger regenerator, whih arries a higher prie tag and auses a larger pressure drop beause shaft horsepower is redued. Pressure drop through the regenerator is important and should be kept as low as pratial on both sides. Generally, the air pressure drop on the high-pressure side should be held below % of the ompressor total disharge pressure. The effetiveness of most regenerators used in pratie is below.85. The thermal effiieny of an ideal Brayton yle with regeneration depends on the ratio of the minimum to maximum temperatures as well as the pressure ratio. Regeneration is most effetive at lower pressure ratios and low minimum-to-maximum temperature ratios [7]. A parametri study of the effet of ompression ratio, ambient temperature, turbine s inlet-temperature (TIT), the effetiveness of regenerator, ompressor effiieny, and turbine effiieny on the performane of the regenerative gas turbine yle and omparison with simple yle []. II. MODEL DESCRIPTION AND PROBLEM FORMULATION Figure 1 shows a gas turbine plant with regenerator, whih is a single shaft turbine. Generally, the priniple of the gas turbine yle is that air is ompressed by the air ompressor, and transferred to ombustion hamber (CC) in order to ombine with fuel for produing high-temperature flue gas. Afterward, high-temperature flue gas will be sent to gas turbine, whih onneted to the shaft of generator for produing eletriity [4]. The purpose of the single shaft turbine is to produe and 811

2 supply the neessary power required to run the ompressor, and is meant for produing the network output. In this regenerative yle, air after ompression enters in to a regenerator where it is heated by the exhaust gases oming from turbine. The preheated air then enters in to ombustion hamber, after heated addition to maximum permissible temperature in the ombustion hamber. The network output of the yle is thus proportional to the temperature drop in the turbine. 6 Exhaust Compress Fig. 1 The regenerative gas turbine yle. Fig. shows the T-S diagram for regenerative gas turbine yle. The atual proesses and ideal proesses are represented in dashed line and full line respetively. The ompressor effiieny ( η ), the turbine effiieny ( η t ) and effetiveness of regenerator (heat exhanger) ( ε ) are onsidered in this study. These parameter in terms of temperature are defined as in (1) [8]: T s T1 η = ; T T 1 T4 T5 η t = and T T 4 5s T T ε = (1) T T The work required to run the ompressor is expressed as in (): W = pa γ a 1 rp γ a 1 T1 () η where the speifi heat of air is expressed as in () [9]. 1 Air pa = T Ta a Ta 5 4 Ta The speifi heat of flue gas is written as Eq. (4) [9]. pg H.E = T C.C Fuel T The work developed by turbine is then rewrite as in (5): 4 5 Turbine W sh aft T G () (4) W = t pg 1 T4η t 1 (5) γ g 1 γ g rp where turbine inlet temperature (TIT) = T 4.The net work is expressed as in (6) W net = pg γ a 1 γ a 1 rp TIT η t 1 pat γ 1 (6) g 1 η γ g rp In the ombustion hamber, the heat supplied by the fuel is equal to the heat absorbed by air, Hene, Q add = pg The power output is, γ a 1 γ a ( ) rp 1 TIT T 1 1 ε 1+ η 1 ε TIT 1 η t 1 γ g 1 γ g rp a W net (7) Power = m & (8) where m& a = air mass flow rate,the air to fuel ratio is defined as in (9), LHV AFR = (9) Q The speifi fuel onsumption is expressed as (1): add 6 SFC = (1) AFR W Further the thermal effiieny of the yle is then expressed as in (11). net net η Wadd th = Q (11) 81

3 '' e=5 e=5 e=5 e=.75 e=.85 e= Fig. T-S diagram for regenerative gas turbine yle Ambient Temperature (k) III. RSULTS AND DISCUSSION The yle was modeled using the thermodynami analysis for the simple gas turbine and regenerative gas turbine. The pressure losses are assumed in this study. The effet of thermal effiieny, power and speifi fuel onsumption on operation onditions are analyzed in the following setion. A. Effet of Ambient Temperature (T1) Figure shows the effet of ambient temperature and regenerative effetiveness on thermal effiieny of gas turbine yle. Turbine inlet temperature (r p ) and effetiveness are of 145 K, 1 and.85 respetively. It an be seen that the thermal effiieny dereases with inreases of ambient temperature while dereases of regenerative effetiveness. The speifi work of the ompressors inreases as the ambient temperature inreases [1]. Thus the thermal effiieny for the regenerative gas turbine yles is redued. It an be notied that the gain of thermal effiieny inrease of 1.6% with inreases of regenerative effetiveness from (5-.95). The density of air inreases when ambient temperature dereases, whih auses an inrease in the air mass flow rate. The power and heat supplied to the ombustion hamber inreases with the gas mass flow rate inreases however, the power inrease is more than the inrease in the heat supplied in the ombustion hamber (Figure ). Fig. Variation of thermal effiieny on ambient temperature and regenerative effetiveness. Variation of thermal effiieny on inlet temperature of simple yle and regenerative yle is shown in Figure 4. It is observed that the thermal effiieny is higher for regenerative yle than simple yle. The variation of speifi fuel onsumption with ambient temperature is also shown in Figure 5. It shows that when the ambient temperature inreases the speifi fuel onsumption inreases too. This is beause, the air mass flow rate inlet to ompressor inreases with derease of the ambient temperature. So, the fuel mass flow rate will inrease, sine (AFR) is kept onstant. The power inrease is less than that of the inlet ompressor air mass flow rate ( ); therefore, the speifi fuel onsumption inreases with the inrease of ambient temperature. 5 5 Regenerative Cyle Simple Cyle Inlet Temperature (k) Fig. 4 Effet of ambient temperature on thermal effiieny for simple and regenerative yle. 81

4 Speifi Fuel Consumption(kg/kW.h) rp=4 rp=7 rp=1 rp=1 rp=16 rp=19 rp= ompression ratio. The inrease in ompression ratio means an inrease in power output, so the speifi fuel onsumption must inrease too. The relation between speifi fuel onsumption versus ompression ratios for regenerative gas turbine yle at different effetiveness values for regenerator shown in Figure 9. The thermal effiieny inreased with ompression ratio at deferent values for regenerative effetiveness as shown in Figure 1. Also the thermal effiieny inreased with inreased ompressor effiieny and turbine effiieny as shown in Figures 11 and Ambient Temperature (k) Fig. 5 Influene of ambient temperature on speifi fuel onsumption with deferent ompression ratio (TIT is alulated). B. Effet of Compression Ratio (r p ) Figure 6 shows the variation of the thermal effiieny with ompression ratio. The inrease in ompression ratio means an inrease in power output, so the thermal effiieny must inrease too. A diret effet of ompression ratio on the standard air thermal effiieny and the thermal effiieny of regenerative yle is shown in Figure 7. The thermal effiieny inreases with inrease of ompression ratio for the same inlet temperatures sine the ompression ratio will raise the temperature of the air entering the ombustion hamber whih is dereases the heat added, i.e. inreases the thermal effiieny. In regenerative yle the thermal effiieny inrease with ompression ratio to 5 then return the thermal effiieny derease with inrease ompression ratio. Regenerative Cyle Simple Cyle Compression Ratio Fig. 7 Effet of ompression ratio on thermal effiieny for simple and regenerative yle..7 T1=68 T1=8 T1=98 T1=1 T1= Compresion Ratio Fig. 6 Effet of ompression ratio and ambient temperature on thermal effiieny (speified TIT). Speifi Fuel Consumption(kg/kW.h) T1=68k T1=8k T1=98k T1=1k T1=8k Compresion Ratio Fig. 8 Influene of ompression ratio on speifi fuel onsumption with deferent ambient temperature (TIT is alulated). Figure 6 also present a relation between regenerative gas turbine yle thermal effiieny versus ompression ratios for different ambient air temperatures, whih reveals an opposite relation as the effiieny dereases as inlet air temperature inreases, a omparison between the results from the present study and the results shown in [Gas Turbine Theory] whih reveals an aeptable agreement as shown in Figure 7. Figure 8 shows the variation speifi fuel onsumption with 814

5 e=. 45. e=. 55 e= e=. 75 e=. 85 e= ompression Ratio Fig. 9 Influene of ompression ratio on speifi fuel onsumption (TIT is alulated) T1=68k T1=78k T1=88k T1=98k 5 T1=8k T1=18k T1=8k Isontropi Turbine Effiieny Fig. 1 Effet of isentropi turbine effiieny and ambient temperature on thermal effiieny. Speifi Fuel Consumption(kglkW.h) e=5 e=5 e=5 e=.75 e=.85 e=.95 The performane map of a regenerative gas turbine yle is shown in Figure 1 Present a relation between power outputs versus thermal effiieny for regenerative yle for different turbine inlet temperatures and different ompression ratios. The power output inreases as turbine inlet temperature inreases, for a given ompressor inlet temperature, turbine inlet temperature, ompressor effiieny, and turbine effiieny, there is a ompression ratio at whih the thermal effiieny reahes a maximum value; if the ompression ratio is inreased beyond this value, the thermal effiieny and net work will slowly derease as shown in Figure Compression Ratio Fig. 1 Effet of ompression ratio and reg. effetiveness on thermal effiieny (speified TIT). 5 5 T1=68k T1=78k 5 T1=88k T1=98k T1=8k T1=18k T1=8k Isontropi Compressor Effiieny Fig. 11 Effet of isentropi ompressor effiieny and ambient temperature on thermal effiieny..7 TIT=1k TIT=11k TIT=1k TIT=1k TIT=1k TIT=14k TIT=15k TIT=16k TIT=17k Power (kw) x 1 5 Fig. 1 Thermal effiieny-power dependene on ompression ratio and TIT. 815

6 Speifi Fuel Consumption(kg/kW.h) Power(kW) x 1 4 Fig. 14. Thermal effiieny-power dependene on ompression ratio. C. Effet of Turbine Inlet Temperature (TIT) The relation between turbine inlet temperature and thermal effiieny for different values of ambient temperature is shown in Figure15. As the turbine inlet temperature is inreased for the same exit temperature, the temperature drop will inrease giving higher power potential. This inrease in power leads to an inrease in the thermal effiieny as shown in Figure 16. T1=68k T1=78k T1=88k T1=98k T1=8k T1=18k T1=8k Turbine Inlet Temperature(k) Fig. 15 Effet of turbine inlet temperature and ambient temperature on thermal effiieny. rp=4 rp=7 rp=1 rp=1 rp=16 rp=19 rp= IV. CONCLUSION This paper has presented onsideration that should be inluded in determining the performane of a regenerative gas turbine power plant. A design methodology has been developed for parametri study and performane evaluation of a regenerative gas turbine. Parametri study showed that rp, ambient temperature and TIT played a very vital role on overall performane of a regenerative gas turbine. (i) The heat duty in the regenerator dereases with the pressure ratio but inreases with the dereases ambient temperature and inreases TIT this mean inreased thermal effiieny. (ii) The thermal effiieny of the simple gas-turbine yle experienes small improvements at large pressure ratios as ompared to regenerative gas turbine yle. (iii) In general, peak effiieny, power and speifi fuel onsumption our at ompression ratio (rp = 5) in the regenerative gas turbine yle. (iv) The thermal effiieny inreases and speifi fuel onsumption dereases with the regenerator effetiveness. ACKNOWLEDGMENT The authors would like to thank Universiti Malaysia Pahang for provides laboratory failities and finanial support under Dotoral Sholarship sheme. REFERENCES [1] P.K. Nag, 8. Power plant engineering. New Delhi: Tata MGraw- Hill Publishing Company Limited, 8. [] F.G. Mahmood, and D.D. Mahdi, A new approah for enhaning performane of a gas turbine (ase study: Khangiran Refinery), Applied Energy, vol. 86, pp , 9. [] H. Saravanamuttoo, G. Rogers, H. Cohen, and P. Strazniky, Gas Turbine Theory, England: Prentie Hall, 9. [4] M.J. Moran, and H.N. Shapiro, Fundamentals of Engineering Thermodynamis, New York: John Wiley & Sons, INC, 8. [5] S.M. Mahmoudi, V. Zare, F. Ranjbar, and L. Farshi, Energy and exergy analysis of simple and regenerative gas turbines inlet air ooling using absorption refrigeration, Journal of Applied Sienes, vol. 9, no. 1, pp , 9. [6] J. Maria, and Y. Jinyue, Humidified gas turbines a review of proposed and implemented yles, Energy, vol., pp , 5. [7] P.A. Dellenbak, Improved gas turbine effiieny through alternative regenerator onfiguration, Journal of Engineering for Gas Turbines and Power, vol. 14, pp ,. [8] A.F. Al-Sayed, Airraft Propulsion and Gas Turbine Engines, Boa Raton: Taylor & Franis, 8. [9] R.K. Naradasu, R.K. Konijeti, and V.R. Alluru, Thermodynami analysis of heat reovery steam generator in ombined yle power plant, Thermal Siene, vol. 11, no. 4, pp , 7. [1] P.A. Dellenbak, A reassessment of the alternative regeneration yle, Journal of Engineering for Gas Turbines and Power, vol. 18, pp , Turbine Inlet temperature (k) Fig.16. Effet of turbine inlet temperature and ompression ratio on speifi fuel onsumption. 816

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