Thermodynamic modeling and Exergy Analysis of Gas Turbine Cycle for Different Boundary conditions

International Journal of Power Electronics and Drive System (IJPEDS)
Vol. 6, No. 2, June 2015, pp. 205~215
ISSN: 2088-8694  205
Journal homepage: http://iaesjournal.com/online/index.php/IJPEDS
Thermodynamic modeling and Exergy Analysis of Gas Turbine
Cycle for Different Boundary conditions
Lalatendu Pattanayak
Steag Energy Services India Pvt. Ltd, A-29, Sector-16, Noida, UP, India
Article Info ABSTRACT
Article history:
Received Oct 29, 2014
Revised Dec 15, 2014
Accepted Feb 20, 2015
In this study an exergy analysis of 88.71 MW 13D2 gas turbine (GT) topping
cycle is carried out. Exergy analysis based on second law was applied to the
gas cycle and individual components through a modeling approach. The
analysis shows that the highest exergy destruction occurs in the combustion
chamber (CC). In addition, the effects of the gas turbine load and
performance variations with ambient temperature, compression ratio and
turbine inlet temperature (TIT) are investigated to analyse the change in
system behavior. The analysis shows that the gas turbine is significantly
affected by the ambient temperature and with increase there is decrease in
GT power output. The results of the load variation of the gas turbine show
that a reduction in gas turbine load results in a decrease in the exergy
efficiency of the cycle as well as all the components. The compressor has the
largest exergy efficiency of 92.84% compared to the other component of the
GT and combustion chamber is the highest source of exergy destruction of
109.89 MW at 100 % load condition. With increase in ambient temperature
both exergy destruction rate and exergy efficiency decreases.
Keyword:
Ambient temperature
Combined cycle power plant
Compression ratio
Efficiency
Exergy
TIT
Copyright © 2015 Institute of Advanced Engineering and Science.
All rights reserved.
Corresponding Author:
Lalatendu Pattanayak,
Departement of System Technologies,
Steag Energy Services India Pvt. Ltd,
A-29, Sector-16, Noida, UP, 201301, India.
Email: lala_tendu@rediffmail.com
1. INTRODUCTION
Concept of exergy analysis involves both laws of thermodynamics (first and second laws) is an
analysis technique applied on energy systems to identify and quantify the amount of thermodynamic
adversity involved in the processes and or energy systems. This technique is used as a potential tool to
evaluate the thermal performance and efficiency of system and components involve in energy process during
design as well as in operation phase. By definition exergy is the amount of maximum work potential for an
energy system in relation to its environment through reversible processes [1]. Exergy analysis quantitatively
detects and evaluates the thermodynamic inefficiencies of the process under consideration [2], [3].
In recent years many studies have been performed by researchers to evaluate the performance of
combined cycle power plants (CCPPs) and its subsystems based on concept of energy and exergy [4]-[14].
Boksteen et al. [15] performed the second law based analysis with steady state thermodynamic model for
KA26 gas turbine combined cycle plant to improve its operational efficiency. A concept of exergy was used
by I.S. Ertesvag et al. [16] to investigate the CO2 capture in a gas turbine plant. Also the study investigates
the effects of change in natural gas composition and ambient temperature. Akbari et al. [17] conducted a
parametric study with design parameters to evaluate the performance of CCPP using energy and exergy
concept. Ali and Ameri [18] evaluate the system performance of gas turbine power plant for different load
and ambient temperature based on energy, exergy and exergoeconomic analysis. Ebadi and Gorji-Bandpy
[19] performed the exergy analysis of a 116 MW gas turbine power plant based on varying TIT. The

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IJPEDS Vol. 6, No. 2, June 2015 : 205 – 215
206
application of exergy analysis to determine the irreversibility of CCPP was presented by Ameri et al. [20].
Ghazikhani et al. [21] investigate the performance of gas turbine air bottoming combined cycle based on
exergy analysis. The result shows that the second law efficiency of gas turbine with air bottoming cycle is 6
% more that the second law efficiency of simple gas turbine keeping same intake air temperature for both the
cycle. An advanced exergy analysis is performed by Soltani et al. [22] for a CCPP configuration of an
externally fired system, integrated with biomass gasification. They concluded that the performance of the
cycle can be improved by improving the performance of heat exchanger though the maximum rate of exergy
destruction occurs at the combustion chamber. Wang and Lv [23] investigate the M701F gas turbine based
combined cycle plant to improve the service life of hot end components using equivalent operation time
analysis method. Al-Doori [24] performed an exergetic analysis for a Baiji plant gas turbine of capacity 159
MW with effect of cycle temperature. The result shows that the TIT has an impact on both exergetic
efficiency and exergy destruction of the plant. Egware and Obanor [25] presented the use of exergy analysis
for evaluating the performance of Omotosho Phase I gas thermal power plant. Results obtained show that the
gas turbine had the largest exergy efficiency of 96.17%, while that of the total plant was 41.83%, the
combustion chamber had the largest exergy destruction of 54.15% while that of the total plant was 58.17%.
In this study the exergetic analysis is performed for a 88.71 MW GT cycle through a modeling
approach. Exergy analysis for the gas cycle is carried out to assess the performance of different component
and find out areas of exergy destruction at design and off design condition. Exergy destruction of the
combined cycle plant component is quantified and the effect of boundary conditions like ambient
temperature, compression ratio and TIT on the performance of gas turbine cycle is investigated.
2. DESCRIPTION OF GAS TURBINE CYCLE
Figure 1 shows a schematic diagram of GT 13D2 machine with 100% output (88.71 MW) at
ambient temperature of 27 o
C and air pressure at compressor inlet 1.003 ata. The conversion of heat released
by burning fuel into mechanical energy in a gas turbine is achieved by first compressing air in an air
compressor, then injecting and burning fuel at (ideally) constant pressure, and then expanding the hot gas in
the gas turbine. Combustion product enters the GT at temperature of 1005 o
C and pressure of 11.66 ata. At
full load the GT produce 88.71 MW. The waste heat in flue gas exit from GT at temperature of 507.8o
C.The
turbine provides the necessary power to operate the compressor. Whatever power is left is used as the
mechanical output of the engine. This thermodynamic cycle is called as topping cycle. To represent the
physical parameters of working fluid at different state is marked as 1, 2, 3…7 as shown in Figure 1. Basic
assumption is that the system under study is in steady state and the mechanical efficiency of the GT and
compressor is 99%.
Figure 1. Schematic diagram of Gas turbine cycle
3. EXERGY ANALYSIS
Exergy analysis is a method that is used for analysis, design and performance improvement of
energy and other systems. Furthermore it can be used as a tool for analyzing the efficient use of energy
resource and also to determine the types and magnitude of wastes and losses occurring in the systems [26],
[27]. According to the literature, total exergy of a system can be divided into four components. The two

IJPEDS ISSN: 2088-8694 
Thermodynamic modeling and Exergy Analysis of Gas Turbine Cycle for Different … (Lalatendu P.)
207
important are the physical exergy and chemical exergy. The physical exergy is the maximum work obtainable
by a system from its initial state through reversible process while interacting with an equilibrium state. The
chemical exergy is the maximum work that can be obtainable with the departure of chemical composition of
the system from its chemical equilibrium. The chemical exergy plays an important role of exergy analysis in
the combustion process. In this study, the two other components i,e kinetic exergy and potential exergy are
assumed to be negligible.
Applying the first and second laws of thermodynamics, the exergy balance equation for steady state
flow of stream [28]-[31] is given in (1).
∑ 1 Q ∑ m e W ∑ m e E (1)
where ∑ 1 is the rate of exergy transfer at temperature T, and the subscripts and denote
inlets and outlets, respectively. is the work rate excluding the flow work. The exergy transfer rates at
inlets and outlets are denoted respectively as, and .
The total exergy, physical exergy, specific exergy and chemical exergy are evaluated using (2), (3), (4) and
(5) respectively.
E E E (2)
E m e = m h h T s s (3)
e = specific exergy = h h T s s (4)
where and denote the specific enthalpy and specific entropy respectively. The subscript ‘0’
denotes the refernce state. Reference pressure (Pref) and temperature (Tref) are taken respectively as 1.003
ata and 27 o
C.
E m e (5)
where is specific chemical exergy (mixture) [4] and can be evaluated using (6),
e ∑ X e RT ∑ X lnX G (6)
where is Gibbs free energy which is a negligible quantity in a gas mixture operated at low
pressure. So for the calculation of fuel exergy, the expression in (6) does not hold good. Thus, the fule exergy
can be calculated using (7) as the ratio of fuel exergy to lower heating value of fuel (LHV) [4], [20], [32].
φ (7)

where is fuel exergy. For the majority of gaseous fuel, the value of is normally close to 1. For
the fuel like methane, fallowing relationship can be used as given by Kotas [4]:
φ 1.06
φ 0.985
For gaseous fuel with composition , the ratio can be calculated using (8) [4], [13].
φ 1.033 0.0169
.
(8)
The exergetic efficiency can be evaluated using the relationship of both product and fuel for the
system. The product exergy represents the desired result produced by the system and the fuel exergy
represents the resources expended to generate the product. Thus the exergetic efficiency is the ratio between
product exergy and fuel exergy [28], [33], [34] as given in (9). The exergy efficiency and exergy destruction
of all other individual components of gas cycle are shown in Table 1.
Ɛ

(9)

 ISSN: 2088-8694
208
where is the rate at which fuel is supplied and is the product generated.
Table 1. The exergy destruction rate and exergy efficiency equations for GT components
Component Exergy destruction ( ) Exergy efficiency (Ɛ )

4. RESULTS AND DISCUSSION
Exergy analysis of a GT topping cycle is presented in this section. The effects of ambient
temperature, compression ratio and TIT on power output, exergy destruction rate and exergy efficiency are
obtained from the exergy (second law) analysis. Figure 2 shows the effect of ambient temperature on exergy
destruction rate of gas cycle component at 100 % load condition of GT. With increase in ambient temperature
from 0 o
C to 50 o
C the exergy destruction rate of compressor, combustion chamber and gas turbine decreases.
The maximum exergy destruction takes place in combustion chamber followed by gas turbine.
Figure 2. Variation of exergy destruction rate of components at different ambient temperature for 100 % load.
Figure 3 presents the variation of exergy efficiency of components with change in ambient
temperature at 100 % load. There is a significant change in exergy efficiency of combustion chamber with
0
20
40
60
80
100
120
Compressor Combustion chamber Gas turbine
Exergydestruction(MW)
Tamb= 0°C Tamb=10°C Tamb= 20°C
Tamb= 30°C Tamb= 40°C Tamb= 50°C

209
temperature. As the ambient temperature increases the exergy efficiency decreases. This is due to with rise in
temperature the fuel flow rate decreases and thus the total fuel exergy also reduces. Thus the overall exergy
destruction and exergy efficiency of combustion chamber reduces with rise in temperature. At the same time
the exergy efficiency of gas turbine increase with rise in ambient temperature from 0 o
C to 30 o
C from 92.76
% to 92.92 % and thereafter by further increase in temperature efficiency reduces as the gas turbine load
reduce with rise in temperature from the rated capacity. The exergy destruction rate of the gas turbine reduces
with rise in ambient temperature. As the temperature rise the gas turbine load reduces and the turbine exit
temperature increases. Total exergy at gas turbine inlet and outlet reduces, resulting reduce in gas turbine
exergy destruction rate.
Figure 3. Variation of exergy efficiency of components at different ambient temperature for GT load 100 %.
Figure 4 depicts the effect of ambient temperature on exergy destruction rate and exergy efficiency
of GT cycle. With increase in ambient temperature both exergy destruction rate and exergy efficiency of GT
cycle decreases. Exergy efficiency decreases continuously up to ambient temperature of 27 o
C and from 27
o
C to 30 o
C it increases by maintaining the rated load of 88. 71MW and further decreases with increase in
temperature. This indicates that the best performance of the gas cycle can be achieved in between the
temperature range of 27 o
C to 30 o
C.
0
10
20
30
40
50
60
70
80
90
100
Exergyefficiency(%)

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Figure 4. Variation of exergy efficiency and exergy destruction of gas cycle with ambient temperature
Though the gas turbine produces maximum power at low ambient temperature but at the same time
the rate of exergy destruction is high at lower ambient temperature. The high temperature air leaving from
compressor becomes hotter with the high ambient temperature entering into the combustion chamber while
gases leaving from combustion chamber are also at higher temperature thereby reducing the irreversibility.
Figure 5 shows the corresponding temperature-entropy(t-s) diagram of the gas turbine cycle at different
ambient temperature. With rise in ambient temperature the compression outlet temperature rises this is due to
reduction in air flow.
Figure 5. T-S diagram of gas turbine cycle at different ambient temperature
130
132
134
136
138
140
142
144
146
26.5
27
27.5
28
28.5
29
29.5
30
30.5
0 10 20 30 40 50 60
Exergyefficiency(%)
Tamb (°C)
Exergy efficiency (%) Exergy destruction (MW)

211
The exergy destruction and exergy efficiency of various plant components are shown in Figure 6
and Figure 7 for various gas turbine load at refernce temperature (Tref) of 27o
C and pressure (Pref) of 1.003
ata. The result shows that the compressor has the largest exergy efficiency of 92.84% compared to the other
component of the GT and combustion chamber is the highest source of exergy destruction of 109.89 MW at
100 % load condition. It is also shown that the exergy destruction rate increases with increase in load form 50
% to 100 %.
Figure 6. Exergy destruction of components at various load
Figure 7. Exergy efficiency of components at various load
Figure 8 shows the effect of ambient temperature on gas cycle power output and exergy efficiency at
various load. The efficiency of gas turbine cycle decreases with increase in ambient temperature as the power
output of the gas turbine cycle decreases with increase in ambient temperature. This may be due to increase
in compressor work at high temperature and the mass flow rate reduces.
0
20
40
60
80
100
120
Load 50%
Load 75%
Load 100%
0
10
20
30
40
50
60
70
80
90
100
Exergyefficiency(%)
Load 50% Load 75% Load 100%

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Figure 8. Variation of gas cycle exergy efficiency with ambient temperature and load
The effect of TIT and compression ratio on power output and over all exergy efficiency of gas cycle
is depicts in Figure 9 at reference temperature of 27 o
C. Exergy efficiency and power output of gas cycle
increases with increase in TIT and decreases with decrease in compression ratio. An increase in the TIT leads
to an increase in the GT exergy efficiency due to the fact that the GT turbine work output increases. As the
load increases thus leads to reduction in exergy destruction. Therefore, it can be concluded that TIT is the
most important parameter in designing the gas turbine cycle due to the decrease in exergy destruction and
increase in cycle exergy efficiency.
Figure 9. Effect of TIT and compression ratio on gas turbine power out and gas cycle exergy efficiency
20
30
40
50
60
70
80
90
100
110
0
5
10
15
20
25
30
35
0 10 20 30 40 50 60
Poweroutput(MW)
Exergyefficiency(%)
Tamb (°C)
Load 50 % Load 75 % Load 100%
Exergy efficiency
Power output
0
20
40
60
80
100
120
15
20
25
30
35
40
700 800 900 1000 1100 1200 1300 1400 1500
Power output (MW)
Exergy efficiency (%)
TIT (°C)
CR=8 CR=10 CR=12 CR=14 CR=16 CR=18
Exergy efficiency
Power output

213
5. CONCLUSION
An exergy analysis applied to a process or to total plant gives quantitative information that how
much work potential, or exergy input to the system under study has been consumed by the process or plant
components. The exergy analysis (loss of exergy, or irreversibility) provides quantitative information of the
system and process inefficiency. In this study the exergetic analysis is performed for a 13D2 GT machine.
The effect of ambient temperature, compression ratio and TIT on the exergy efficiency and exergy
destruction of gas turbine cycle and on individual component is analyzed. The results evident that
considerable amount of exergy destruction occur in the combustion chamber. This may be due to higher fuel
exergy and chemical reactions of fuel with air, and heat transfer takes place inside the combustion chamber.
The exergy efficiency of gas turbine increase with rise in ambient temperature from 0 o
C to 30 o
C from 92.76
% to 92.92 % and thereafter by further increase in temperature efficiency reduces as the gas turbine load
reduce with rise in temperature from the rated capacity. The best performance of the gas cycle can be
achieved in between the temperature range of 27 to 30 o
C.
REFERENCES
[1] H. Kurt, Z. Recebli and E. Gredik, “Performance analysis of open cycle gas turbines”, Int J Energy Res, vol. 33, no.
2, pp. 285–94, 2009.
[2] A. Cihan, O. Hacıhafızoglu and K. Kahveci, “Energy–exergy analysis and modernization suggestions for a
combined-cycle power plant”, Int J Energy Res, vol. 30, pp. 115–126, 2006.
[3] M. Ameri, P. Ahmadi and A. Hamidi, “Energy, exergy and exergoeconomic analysis of a steam power plant (a case
study)”, Int J Energy Res, vol. 33, pp. 499–512, 2009.
[4] T. Kotas, The exergy method of thermal plant analysis, in Butterworths, London, 1985.
[5] M. Moran and H. Shapiro, Fundamentals of Engineering Thermodynamics (4th edn), New York: Wiley, 2000.
[6] D. Sue and C. Chuang, “Engineering Design and Exergy Analysis for Combustion Gas Turbine Based
PowerGeneration System”, Energy, vol. 29, pp. 1183-1205, 2004.
[7] T.K. Ibrahim and M. Rahman, “Effective Parameters on Performance of Multipressure Combined Cycle Power
Plants”, Advances in Mechanical Engineering, pp. 1-13, 2014.
[8] S. Kaushika, V. Reddya and S.K. Tyagi, “Energy and exergy analyses of thermal power plants: A review”, Renew.
Sust. Energ. Rev., vol. 15, pp. 1857–1872, 2011.
[9] T.K. Ibrahim, M. Rahman and A.N. Abdalla, “Optimum Gas Turbine Configuration for Improving the performance
of Combined Cycle Power Plant”, Procedia Engineering, vol. 15, pp. 4216-4223, 2011.
[10] S. Boonnasa and P. Namprakai, "Sensitivity analysis for the capacity improvement of a combined cycle power
plant(100-600MW)," Applied Thermal Engineering, vol. 28, no. 14-15, pp. 1865–1874, 2008.
[11] T. Srinivas, A.V.S.S.K.S. Gupta and B.V. Reddy, “Thermodynamic modeling and optimization of multi-pressure
heat recovery steam generator in combined power cycle”, Journal of Scientific and Industrial Research, vol. 67, no.
10, pp. 827–834, 2008.
[12] V.S. Reddy, S.C. Kaushik, S.K. Tyagi and N.L. Panwar, “An Approach to Analyse Energy and Exergy Analysis of
Thermal Power Plants: A Review”, Smart Grid and Renewable Energy, vol. 1, pp. 143-152, 2010.
[13] P. Ahmadi and I. Dincer, “Thermodynamic analysis and thermoeconomic optimization of a dual pressure combined
cycle power plant with a supplementary firing unit”, Energy Conversion and Management, vol. 52, p. 2296–2308,
2011.
[14] Laila M. Farag, “Energy and Exergy Analyses of Egyptian Cement Kiln Plant With Complete Kiln Gas Diversion
through by Pass”, International Journal of Advances in Applied Sciences(IJAAS), vol. 1, no. 1, pp. 35-44, 2012.
[15] S.Z. Boksteen, J.P. Buijtenen and D.v.d. Vecht. A Holistic Approach to GTCC Operational Efficiency Improvement
Studies. in Proceedings of ASME Turbo Expo 2014: Turbine Technical Conference and Exposition, Düsseldorf,
Germany, 2014.
[16] I.S. Ertesvag, H.M. Kvamsdal and O. Bolland, “Exergy analysis of a gas-turbine combined-cycle power plant with
precombustion CO2 capture”, Energy, vol. 30 , pp. 5–39, 2005.
[17] M. Akbari, S.M.S. Mahmoudi, M. Yari and M.A. Rosen, “Energy and Exergy Analyses of a New Combined Cycle
for Producing Electricity and Desalinated Water Using Geothermal Energy”, Sustainability, vol. 6, pp. 1796-1820,
2014.
[18] A. Mousafarash and M. Ameri, “Exergy and exergo-economic based analysis of a gas turbine powergeneration
system”, Journal of Power Technologies, vol. 93, no. 1, pp. 44-51, 2013.
[19] M.J. Ebadi and M. Gorji-Bandpy, “Exergetic analysis of gas turbine plants”, Int. J. Exergy, vol. 2, no. 1, pp. 31-39,
2005.
[20] M. Ameri, P. Ahmadi and S. Khanmohammadi, “Exergy analysis of a 420MW combined cycle power plant”, Int J
Energy Res, vol. 32, pp. 175–83, 2008.
[21] M. Ghazikhani, H. Takdehghan and M.A. Shayegh. Exergy Analysis of Gas Turbine Air- Bottoming Combined
Cycle for Different Environment Air Temperature. in Proceedings of 3rd International Energy, Exergy and
Environment Symposium, Portugal, 2007.
[22] S. Soltani, M. Yari, S. Mahmoudi, T. Morosuk and M. Rosen, “Advanced exergy analysis applied to an externally-
fired combined-cycle power plant integrated with a biomass gasification unit”, Energy, vol. 59, pp. 775–780, 2013.

 ISSN: 2088-8694
214
[23] Taixing Wang and Xiaoqing Lv, “Analysis on Service Life of Hot-end Components of Gas Turbine Using
Equivalent Operation”, TELKOMNIKA, vol. 11, no. 3, pp. 1473–1477, 2013.
[24] W.H.A.R. Al- Doori, “Exergy Analysis of a Gas Turbine Performance With Effect Cycle Temperatures”, IJRRAS,
vol. 13, no. 2, pp. 549-556, 2012.
[25] E.H. Okechukwu and O.A. Imuentinyan, “Exergy Analysis of Omotosho Phase 1 Gas Thermal Power Plant”,
International Journal of Energy and Power Engineering, vol. 2, no. 5, pp. 197-203, 2013.
[26] Y.S. Najjar and S. Al-Absi, “Exergy analysis for greener gas turbine engine arrangements”, Journal of Engineering
Thermophysics, vol. 22, no. 3, pp. 247-256, 2013.
[27] I. Dincer and M. Rosen, “Exergy: energy, environment and sustainable development”, Elsevier, 2007.
[28] A. Bejan and E. Mamut. Thermodynamic Optimization of Complex Energy Systems. in Proceedings of the NATO
Advanced Study Institute, 1998.
[29] A. Bejan, G. Tsatsaronis and M. Moran. Thermal design and optimization. in Wiley , New York, 1996.
[30] M. Kanoglu, I. Dincer and M. Rosen, “Understanding energy and exergy efficiencies for improved energy
management in power plants”, Energy Policy, vol. 35, pp. 3967–78., 2007.
[31] P. Ahmadi. Exergy concepts and exergy analysis of combined cycle power plants (a case study in Iran). B.Sc.
Thesis, Energy Engineering Department,Power & Water University of Technology (PWUT), Tehran, Iran, 2006.
[32] I. Dincer and H. Al-Muslim, “Thermodynamic analysis of reheats cycle steam power plants”, Int J Energy Res ,
vol. 25, pp. 727–39, 2001.
[33] M. Lozano and A. Valero, “Theory of the exergetic cost”, Energy , vol. 18, pp. 939-60, 1993.
[34] G. Tsatsaronis and M. Winhold, “Exergoeconomic Analysis and Optimization of Energy Conversion Plants. Part I:
A New General Methodology; Part II: Analysis of a Coal – Fired Steam Power Plant”, Energy, vol. 10, no. 1, pp.
69-94, 1985.
Nomenclature
e specific exergy (kJ/kg)
E total exergy (kJ/kg)
h enthalpy (kJ/kg)
LHV lower heating value (kJ/kg)
ṁ mass flow rate (kg/s)
p pressure (ata)
Q heat transfer rate (MW)
s entropy (kJ/kgK)
T temperature (o
C)
W rate of work (MW)
Greek Symbol
ratio of fuel exergy to lower heating value
Ɛ exergy efficiency (%)
Subscripts and superscripts
a air
amb ambient
c compressor
ch chemical
D destruction
outlet
F fuel
inlet
ph physical
P product
0 reference state
1-7 state points on the schematic flow sheet
Abbreviation
CC combustion chamber
GT gas turbine
TIT turbine inlet temperature

215
BIOGRAPHY OF AUTHOR
Lalatendu Pattanayak received his B.E degree in Mechanical Engineering from Berahmpur
University, MTech in Environmental Science and Engineering from Jamia Millia Islamia (New
Delhi, India) and PGDip in Thermal power plant Engineering from NPTI (Badarpur) India. He is
currently working as DGM (System Technology dept.) at Steag Energy Services India Pvt. Ltd.
and his research interest covers topics in energy engineering including energy efficiency, energy
auditing, energy conservation, life cycle assessment, exergy analysis and modeling & simulation.

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