MEV


 

 

J. Mechatron. Electr. Power Veh. Technol. 06 (2015) 97-104 

 

Journal of Mechatronics, Electrical Power, 

and Vehicular Technology 
 

e-ISSN: 2088-6985 

p-ISSN: 2087-3379 
 

 

 

www.mevjournal.com 
 

© 2015 RCEPM - LIPI All rights reserved. Open access under CC BY-NC-SA license. Accreditation Number: 633/AU/P2MI-LIPI/03/2015. 

doi: 10.14203/j.mev.2015.v6.97-104 

STUDY ON PERFORMANCE IMPROVEMENT AND ECONOMICAL 

ASPECT OF GAS TURBINE POWER PLANT USING  

EVAPORATIVE COOLING SYSTEM 
 

Hilman Syaeful Alam a, *, John Sasso b, Imam Djunaedi c 
aTechnical Implementation Unit for Instrumentation Development, Indonesian Institute of Sciences  

Jl. Sangkuriang Komplek LIPI Gedung 30 Bandung, 40135, Indonesia 
bRRT Sigma Engineering, One Huntington Quadrangle 3S-01 

Melville, New York, 11747, USA 
cResearch Center for Physics, Indonesian Institute of Sciences 

Jl. Sangkuriang Komplek LIPI Gedung 80 Lantai 2 Bandung, 40135, Indonesia 

 
Received 5 May 2015; received in revised form 26 August 2015; accepted 17 September 2015 

Published online 30 December 2015 

 

Abstract 
The study is intended to improve the performance of gas turbine engines in order to meet both electrical power 

demand and peak load in the power plant. In this paper, evaporative cooling system had been applied to improve the 

performance of gas turbine in Pesanggaran power plant in southern Bali Island, Indonesia. Moreover, the economic 

analysis was conducted to determine the capacity cost, operating cost and payback period due to the investment cost 

of the system. Based on the evaluation results, the power improvement for the three gas turbine units (GT1, GT2 and 

GT3) are 2.09%, 1.38%, and 1.28%, respectively. These results were not very significant when compared to the 

previous studies as well as on the aspects of SFC (Specific Fuel Consumption), heat rate and thermal efficiency. 

Based on the evaluation of the economic aspects, the reduction of production costs due to the application of 

evaporative cooling system was not economical, because it could not compensate the investment cost of the system 

and it resulted a very long payback period. These unsatisfactory results could be caused by the high relative 

humidity. Therefore, further studies are needed to investigate the other alternative technologies which are more 

suitable to the climate conditions in Indonesia. 

 

Keywords: performance improvement; economic analysis; evaporative cooling; gas turbine; power plant. 

 

I. INTRODUCTION 
Gas turbines are the constant volume 

machines which always move the same volume 

of air at the given shaft speed. Since the 

combusted air is taken directly from the 

environment, their performance is strongly 

affected by ambient temperature. The power 

output of a gas turbine depends on the flow of 

mass through it. In hot days when air is less 

dense, power output falls off. A rise of 1°C 

temperature of inlet air decreases the power 

output by 1% [1]. The simplest way to overcome 

the problem is to decrease the temperature of the 

inlet air. Inlet air cooling is considered the most 

effective technique to increase the power output 

as well as thermal efficiency of industrial gas 

turbines. In general, the inlet air cooling 

technology on the gas turbine system can be 

classified into three types: evaporative cooling, 

chiling and fogging. Evaporative cooling is the 

most widely used method for power 

augmentation of gas turbine because it remains a 

most costs-efficient method for temperature 

control of the gas turbine inlet air supply [2]. 

Several studies have been done related to the 

issue of power augmentation, for simple cycle 

and combined cycle gas turbine using 

evaporative cooling technique [2-9]. Hamdan et 

al. [2] conducted a study on the performance 

improvement of a simple cycle gas turbine with a 

nominal rating of 250 MW. This engine is 

operated at Shuaiba Power Plant in Kuwait. The 

obtained results shows that the system appears to 
*Corresponding Author. Tel: +62-22-2503053 
E-mail: alam_hilman@yahoo.com 

 

http://dx.doi.org/10.14203/j.mev.2015.v6.97-104


H.S. Alam et al. / J. Mechatron. Electr. Power Veh. Technol. 06 (2015) 97-104 

 
98 

be capable of boosting generated power for about 

11.07%. Santos et al. [3] did the same study but 

applied to non-commercial gas turbine in 

Brazilian sites with increased power reached 

9.65%. Hosseini et al. [4] resulted in an increased 

output power of up to 13.3% which was applied 

to the combined cycle gas turbine power plant in 

Fars, Iran. 

In this study, performance improvement of a 

simple cycle gas turbine using evaporative 

cooling system will be analyzed according to the 

different climatic conditions with previous 

studies. The case study was conducted in 

Pesanggaran power plant which owned and 

operated by Indonesia Power. This power plant is 

located in southern Bali Island, Indonesia, the 

load peaks occur during the early and late 

evening when the tourist hotels demand the most 

electricity. Moreover, the economic analysis was 

conducted to determine the capacity cost, 

operating cost and payback period due to the 

investment cost of the evaporative cooling 

system on the gas turbine. 

 

II. MATERIALS AND METHODS 
 

A. Basic of Gas Turbine Cycle 
The basic of gas turbine operating cycle 

which also called Brayton cycle is depicted in 

Figure 1. It consists of a compression stage, a 

heat addition (combustion) stage and an 

expansion stage (turbine). 

According to Santos et al. [3] and Oyedepo et 

al. [5], the following is the thermodynamic 

calculation for an open simple gas turbine cycle. 

In the existing condition or without a cooling 

system, the compressor inlet temperature is equal 

to ambient temperature, thus the inlet pressure is 

given by 

𝑃0 = 𝑃03 (1) 

where P0 is inlet pressure, and P03 is ambient 

pressure. 

The air and combustion products are assumed 

as ideal gases. The pressure of the air leaving the 

compressor (𝑃04) is calculated as: 

𝑃04 = 𝑟 𝑃03 (2) 

where r is the compression ratio. 

Assuming an ideal gas for state 04, the total 

temperature of the fluid leaving the compressor 

(𝑇04) can be evaluated using ideal gas relations: 

𝑇04 =
𝑇03

𝜂𝑐
[(

𝑃04

𝑃03
)

𝛾−1

𝛾
− 1] + 𝑇03 (3) 

where T03 is ambient temperature, 𝜂𝑐  is the 

compressor efficiency and γ is the specific heat 

ratio. 
The compressor work (�̇�𝐶 ) is calculated from 

the mass flow rate and enthalpy change across 

the compressor as follows: 

�̇�𝐶 = �̇�𝑎 𝐶𝑝𝑎(𝑇04 − 𝑇03) (4) 

where �̇�𝑎 is the air-mass flow rate and 𝐶𝑝𝑎 is the 

specific heat capacity of air at constant pressure. 

The turbine inlet pressure ( 𝑃05 ) can be 
calculated as: 

𝑃05 = 𝑃04(1 − 𝛥𝑃𝑐𝑐 ) (5) 

where 𝑃05 is the turbine entry level pressure, 𝑃04 
is the combustion chamber inlet pressure, and 

𝛥𝑃𝑐𝑐 is pressure drop across the combustion 

chamber. 

The heat delivered by the combustion 

chamber (�̇�𝑖𝑛 )  is determined from energy 

balance: 

�̇�𝑖𝑛 = 𝐶𝑝𝑔 (𝑇05 − 𝑇04) (6) 

where 𝐶𝑝𝑔  is the specific heat capacity of 

combustion products and T05 is the turbine inlet 

temperature. 

By knowing lower heating value (𝐿𝐻𝑉) of the 

fuel gas, the mass flow rate of fuel (�̇�𝑓 )  is 

computed as: 

�̇�𝑓 =
�̇�𝑖𝑛

𝐿𝐻𝑉 𝜂𝑐𝑜𝑚
 (7) 

where 𝜂𝑐𝑜𝑚 is combustor efficiency. 
The exhaust temperature of the gas that leaves 

the turbine (𝑇06) can be written as: 

𝑇06 = 𝑇05 {1 − 𝜂𝑇 [1 − ((
𝑃05

𝑃06
)

1−𝛾𝑔

𝛾𝑔
)]} (8) 

where 𝜂𝑇  is the turbine isentropic efficiency and 

𝑃06 is the ambient pressure.  
Hence, the turbine power (�̇�𝑇 ) is equal to: 

�̇�𝑇 = �̇�𝑔𝑐𝑝𝑔 (𝑇05 − 𝑇06) (9) 

where �̇�𝑔 is the total mass flow rate of flue gas. 

It is composed of fuel and air mass flow rate(�̇�𝑔) and 

given by 

�̇�𝑔 = �̇�𝑎 + �̇�𝑓 (10) 

 

 
Figure 1. Schematic of the standard gas turbine cycle 



H.S. Alam et al. / J. Mechatron. Electr. Power Veh. Technol. 06 (2015) 97-104 

 
99 

The net power obtained from the gas turbine 

(�̇�𝑁𝑒𝑡 ) is given by: 

�̇�𝑁𝑒𝑡 = �̇�𝑇 − �̇�𝑐 (11) 

The specific fuel consumption (SFC) 

compares the ratio of the fuel used by an engine 

to a characteristic power such as the amount of 

power produced by the engine [5]. SFC is 

determined by equation: 

𝑆𝐹𝐶 =
3600 �̇�𝑓

�̇�𝑁𝑒𝑡
 (12) 

Another important gas turbine parameter is 

the heat rate (HR) of a gas turbine cycle 

determined by: 

𝐻𝑅 = 𝑆𝐹𝐶 𝑥 𝐿𝐻𝑉 (13) 

Therefore, the thermal efficiency of the gas 

turbine (𝜂𝑡ℎ ) is calculated as: 

𝜂𝑡ℎ =
�̇�𝑁𝑒𝑡

�̇�𝑓 𝐿𝐻𝑉
 (14) 

 

B. Evaporative Cooling System 
Figure 2 shows a schematic diagram of a gas 

turbine cycle with evaporative cooling system 

that is placed in the inlet compressor. 

Evaporative cooling is a passive process which 

the schematic can be seen in Figure 3. In the 

evaporative cooling system, a wet media is 

installed in the cross-section of the gas turbine 

filter house. The media is kept wet using high 

quality water, such as that from a reverse osmosis 

unit. The air entering the filter house passes over 

the saturated media, and the water contained in 

the media evaporates into the air stream on its 

way to the gas turbine [10]. 

The extent of the evaporation and the 

decreased of temperature is inversely 

proportional to the percentage of a humidity in 

the air stream [5], as shown in the saturation 

process in the psychrometric chart in Figure 4. 

According to Santos et al. [3], the inlet air 

temperature after the cooling process (𝑇03)  in 
Figure 2 can be calculated as: 

𝑇03 = 𝑇𝑏02 − 𝜀(𝑇𝑏02 − 𝑇𝑤02) (15) 

where 𝑇𝑏02 is the dry-bulb temperature, 𝑇𝑤02 is 
the wet-bulb temperature and 𝜀  is the cooling 
effectiveness. 

The evaporated water mass flow associated 

with the evaporative cooling (�̇�𝑤) is given by: 

�̇�𝑤 = �̇�𝑎 (𝜔02 − 𝜔03) (16) 

where �̇�𝑎 is the air mass flow rate and 𝜔02 and 
𝜔03 is the specific humidity in the inlet and outlet 

of the evaporative system respectively. 

The cooling load due to evaporative cooling 

system (�̇�𝐶𝐿 ) can be calculated by [5]: 

�̇�𝐶𝐿 = �̇�𝑎 𝐶𝑝𝑎,𝑎𝑣𝑔 (𝑇02 − 𝑇03) (17) 

where 𝐶𝑝𝑎,𝑎𝑣𝑔  is the specific heat of dry air at 

constant pressure, determined as a function of the 

average temperature across the evaporative 

system. 

 

C. Existing Performance Data 
Table 1 summarizes the three gas turbines, 

manufacturer, years of commissioning and design 

capacity that are located at the Pesanggaran site. 

The existing performance of the three gas 

turbines is based on the latest plant performance 

test results which are shown in Table 2. 

 

Figure 2. Schematic diagram of the gas turbine cycle with 

cooling system 

 

 
Figure 3. Schematic diagram of evaporative cooler 

 
Figure 4. Saturation process in the psychrometric chart 



H.S. Alam et al. / J. Mechatron. Electr. Power Veh. Technol. 06 (2015) 97-104 

 
100 

D. Evaluation Methodology 
GTPro, a power cycle thermodynamic 

computer modeling software, was utilized to 

conduct the performance evaluation of the 

addition of evaporative cooling system on the 

three unit of gas turbine in Pesanggaran site.  

The first step of evaluation is to replicate the 

New and Clean (N&C) performance of each gas 

turbine at the design ambient conditions when the 

unit was installed. Site specific conditions are 

entered such as generator voltage, line voltage, 

site specific fuel composition, GT starter 

mechanism, and others. Using GTPro, the model 

is run at the ambient conditions of the latest 

performance test provided by the plant. 

Degradation factor can be calculated by 

comparing the corrected performance divided by 

the N&C performance. Each GT is then modelled 

in GTPro with each of the performance 

improvements under consideration. The analysis 

is focused on power output, fuel consumption, 

heat rate, and thermal efficiency. 

An estimation of the cost to install the gas 

turbine in current year dollars is determined using 

the GTPro capital cost estimating segment of the 

computer program (PEACE). It is assumed to use 

the default cost multipliers for Indonesia 

provided in GTPro for commodities, equipment, 

labor and materials which can be seen in Table 3. 

The evaluation was focused to determine the 

capacity cost, operating cost and payback period 

due to the investment cost of the evaporative 

cooling system on the gas turbine. 

III. RESULTS & DISCUSSIONS 
Based on the evaluation methodology, the 

performance of gas turbine (GT) was analyzed 

using GTPro simulation. The initial step in the 

simulation is to analyze the effect of operating 

hours to the performance of New and Clean 

(N&C) condition, therefore the results of 

evaluation before and after the addition of 

evaporative cooling system can be corrected by 

the degradation factor.  

The simulation results for the N&C 

performance of GT unit 2 (GT2) can be seen in 

Figure 5, while the result for the latest 

performance test can be seen in Figure 6. Based 

on these results, the degradation factor for the 

GT2 can be estimated at 2.4%, the value is 

derived from the net amount of power based on 

the performance test divided by net power based 

on the N&C performance. Degradation factors 

then are taken into account in the analysis of base 

and new performance by adding evaporative 

cooling system.  

The simulation results of the base 

performance with degradation factor for GT2 can 

be seen in Figure 7, while the simulation results 

of new performance for GT2 by entering the 

degradation factor and cooling system is shown 

in Figure 8. Evaporative cooling process is 

designed with an increase in relative humidity 

approaching 100% saturation point where the 

ambient air conditions that were used as a 

reference in the analysis is the condition at the 

latest of the performance test. The ambient 

conditions in GT2 due to cooling process can be 

shown in the psychrometric chart in Figure 9. 

The ambient conditions before cooling are 

pressure at 14.69 psia, temperature at 80.6oF and 

relative humidity (RH) at 83%. After passing 

through the evaporative cooling system, an 

increase in relative humidity reaches 98.04%, 

which resulted in a decrease in temperature at the 

Table 1.  

Pesanggaran gas turbine installation summary 

GT OEM Model Yr Cap. [MW] Tamb (oC) 

1 GE  MS-500-L 1993 20.10 (B) 23.05 (P) 30 

2 Siemens CW-251-B11 1994 42.07 27 

3 Siemens CW-251-B11 1994 42.07 27 

 

Table 2. 

Gas turbine performance summary 

GT Last capacity test date  Test results (MW) Aux. loads (kW) Tamb (°C) 

1  15/01/14 (7pm-8pm) 16.30 220 30 

2  06/01/14 (7pm-8pm) 39.80  161 30 

3 19/01/14 (7pm-8pm)  35.40    98 30 

 

Table 3. 

Cost factors GTPro recommended for Indonesia 

Category  Factor for Indonesia  

Specialized Equipment  1.05 

Other Equipment  0.75 

Commodities 0.65 

Labor  0.54 
 



H.S. Alam et al. / J. Mechatron. Electr. Power Veh. Technol. 06 (2015) 97-104 

 
101 

compressor inlet into 76.61oF (dropped 4.95%) 

and pressure at 14.51 psia (dropped 1.23%). A 

decrease in temperature at the compressor inlet 

impact on the performance improvement of the 

gas turbine.  

Summary performance improvement of gas 

turbine in Pesanggaran power plant for unit 1 

(GT1), unit 2 (GT2), and unit 3 (GT3) can be 

seen in Table 4, whereas the comparison between 

new three GT performance against the base 

performance can be seen in Figure 10. An 

increased power in the gas turbine as a result of 

the addition of evaporative cooling system can be 

referred to the additional net power which is 

calculated from the new power reduced by base 

power and parasitic load. Parasitic load is the 

extra power needed to run the cooling system that 

reduces the net power output of the gas turbine. 

Based on simulation results, the power 

improvement for the three gas turbine units (GT1, 

GT2, and GT3) respectively are 2.09%, 1.38%, 

and 1.28%. Based on the aspect of fuel 

consumption per power generated (SFC), there 

has been a decrease in incremental of SFC for 

 

Figure 5. The simulation results of GT 2 for New & Clean performance 

 

Figure 6. The simulation results of GT 2 for the latest performance test 

 

Figure 7. The simulation results of GT 2 for the base performance with degradation factor 

 

Figure 8. Simulation result of new GT performance with degradation factor and evaporative cooling 



H.S. Alam et al. / J. Mechatron. Electr. Power Veh. Technol. 06 (2015) 97-104 

 
102 

GT1 and GT 3 for about 0.93% and 0.40%, so the 

fuel consumption is lower than existing 

conditions respectively.  

However on GT2, incremental of SFC against 

existing conditions is increased up to 0.20%, this 

is because the degradation factor on GT 2 is 2.4% 

which is smaller than GT1 and GT3 that has the 

same degradation factor of 13.2%. Therefore the 

application of evaporative cooling system on 

GT2 which has a performance similar to the 

N&C conditions is considered not economical to 

be applied. 

This applies also to the value of incremental 

heat rate which is equal to the incremental SFC 

as a function of the same parameters. The 

incremental value for GT1, GT2, and GT3 

respectively are ˗0.93%, 0.20%, and ˗0.40%. 

Based on the aspects of thermal efficiency, the 

improvement occurred in GT1 and GT3 with the 

efficiency improvement from the existing 

condition respectively are 0.23% and 0.12%, 

while in GT2 the decrease in thermal efficiency 

is 0.06%. The addition of evaporative cooling 

system on gas turbine has an impact on the 

additional cost, i.e. the investment or capacity 

cost. The calculation results of capacity cost 

using PEACE due to the addition of evaporative 

cooling system can be shown in Table 5. The 

investment costs are estimated based on the costs 

required for new plant with the addition of 

cooling system and the demineralized water plant 

reduced by the cost of base plant. If divided by 

the additional energy generated from addition of 

evaporative cooling system, the incremental 

capacity cost for GT1, GT2 and GT3 are 1,358.0, 

1,023.1, and 1,244.1 USD/kWh, respectively. 

The incremental cost of capacity should 

ideally be balanced with a decrease in production 

costs due to the addition evaporative cooling 

system, so the payback period of the investment 

can be estimated. Assuming the gas turbine 

operated for 2000 hours in a year and fuel costs 

 
Figure 9. Psychrometric chart of GT inlet air after cooling process 

 

 
Figure 10. Performance comparison between three GT units after using evaporative cooling system against the base 

performance 



H.S. Alam et al. / J. Mechatron. Electr. Power Veh. Technol. 06 (2015) 97-104 

 
103 

of 0.88 USD/liter [11], the annual production cost 

can be shown in Table 6. The ratio between the 

cost of fuel and energy produced can generate 

average power cost in one year. The difference in 

fuel consumption between the existing conditions 

(base) and after the application of cooling system 

(new) can be expressed as the incremental 

average power cost in USD/kWh per year. An 

average power cost reduction for GT1 and GT3 

of one year respectively are 0.0032 USD/kWh 

and 0.0011 USD/kWh, however for GT2 

increases at 0.0005 USD/kWh, so the evaporative 

cooling system on GT2 is not economical. If the 

decrease in annual production costs on the GT1 

and GT3 is compared to the investment cost of 

the cooling system, the fastest payback period 

can reach until 544 years. 

 

IV. CONCLUSION 
Performance of improvement analysis of gas 

turbine in Pesanggaran power plant due to the 

addition of the evaporative cooling system is 

focused on increasing power, specific fuel 

consumption (SFC), heat rate and thermal 

efficiency. Based on the evaluation results, the 

power improvement for the three gas turbine 

Table 4. 

Performance of the three unit of gas turbine (GT) in Pesanggaran plant 

Parameter GT 1 GT 2 GT 3 

Base power, kW 16,203 40,743 36,249 

New power, kW 16,548 41,316 36,722 

New parasitic load, kW 7 10 10 

Additional net power, kW 338 563 463 

Base heat rate, BTU/kWh 13695.0 11004.0 11423.0 

New heat rate, BTU/kWh 13567.0 11026.0 11377.0 

Incremental heat rate, BTU/kWh -128.0 22.000 -46.000 

Base specific fuel consumption, liter/kWh 0.387 0.311 0.323 

New specific fuel consumption, liter/kWh 0.383 0.311 0.321 

Incremental specific fuel consumption, liter/kWh -0.00362 0.00062 -0.00130 

Base thermal efficiency 24.92% 31.01% 29.87% 

New thermal efficiency 25.15% 30.95% 29.99% 

Incremental thermal efficiency 0.23% -0.06% 0.12% 

 

Table 5.  

Capacity cost evaluation results for the three unit of gas turbine (GT) in Pesanggaran plant 

Parameter GT 1 GT 2 GT 3 

Additional net power due to cooling sytem, kW 338 563 463 

Cost base plant, kUSD 22,232 33,379 33,379 

Cost new plant, kUSD 22,656 33,905 33,905 

Cost Demin/RO plant, kUSD 35 50 50 

Estimated cost of cooling system, kUSD 459 576 576 

Capacity cost of cooling system, USD/kWh 1,358.0 1,023.1 1,244.1 

 

Table 6.  

Operating cost evaluation results for the three unit of gas turbine (GT) in Pesanggaran plant for one year (2000 hr) 

Parameter GT 1 GT 2 GT 3 

Base Electric Energy Generated, MWh 32,406.0 81,486.0 72,498.0 

New Electric Energy Generated, MWh 33,082.0 82,612.0 73,424.0 

Base Annual total fuel consumption, kilter 12,535.9 25,328.1 23,392.5 

New Annual total fuel consumption, kilter 12,677.8 25,729.5 23,595.8 

Base Annual Fuel Cost, kUSD 11,031.6 22,288.8 20,585.4 

New Annual Fuel Cost, kUSD 11,156.5 22,641.9 20,764.3 

Base Average power cost, USD/kWh 0.3404 0.2735 0.2839 

New Average power cost, USD/kWh 0.3372 0.2741 0.2828 

Incremental Average power cost, USD/kWh -0.0032 0.0005 -0.0011 

 



H.S. Alam et al. / J. Mechatron. Electr. Power Veh. Technol. 06 (2015) 97-104 

 
104 

units (GT1, GT2, and GT3) respectively are 

2.09 %, 1.38 %, and 1.28%. These results are not 

very significant compared to the previous studies 

with the enhancement of power ranges between 

5-13.3%. These apply also to the SFC, heat rate 

and thermal efficiency, where the influence of 

evaporative cooling system does not have a 

significant impact to the performance of the gas 

turbine. This could be caused by the high relative 

humidity in Pesanggaran site so that a decrease in 

turbine inlet temperature from the existing 

conditions is less effective only around 4.95%, 

whereas in previous studies could reach between 

30-35%. Based on the evaluation of the economic 

aspects, capacity costs which are calculated from 

the investment cost of the evaporative cooling 

system and demineralized water plan for GT1, 

GT2 and GT3, respectively are 1,358.0, 1,023.1 

and 1,244.1 USD/kWh. These capacity costs 

should be balanced with a decrease in the 

production cost. However the production costs 

reduction due to the evaporative cooling system 

application on the three units of gas turbine was 

not economical because it could not compensate 

the investment cost of the system and it resulted a 

very long payback period. Further studies are 

needed to investigate the other alternative 

technologies which are more suitable to the 

climate conditions in Indonesia. 

 

ACKNOWLEDGEMENT 
This research is motivated by a memorandum 

of understanding (MoU) which has been 

implemented by the Indonesian Institute of 

Sciences (LIPI) and PT. Indonesia Power in the 

fields of research and development of electricity 

on November 7, 2011 with the MoU Number: 

8.MOU/2/IP/2011 and 10/KS/LIPI/IX/2011. 

 

REFERENCES 
[1] Thamir K. Ibrahim et al., “Improvement of 

gas turbine performance based on inlet air 

cooling systems: A technical review,” 

International Journal of Physical Sciences, 

Vol. 6(4), 18 February, 2011, pp. 620-627.  

[2] O. R. AL-Hamdan and A. A. Saker, 

“Studying the Role Played by Evaporative 

Cooler on the Performance of GE Gas 

Turbine Existed in Shuaiba North Electric 

Generator Power Plant, ” Energy and Power 

Engineering, Vol. 5, 2013, pp. 391-400.  

[3] A. P. Santos and C. R. Andrade, “Analysis 

of Gas Turbine Performance with Inlet Air 

Cooling Techniques Applied to Brazilian 

Sites,” J. Aerospace. Technol. Manag., 

Vol.4, No 3, Jul.-Sep., 2012, pp. 341-353.  

[4] R. Hosseini et al., “Performance 

improvement of gas turbines of Fars (Iran) 

combined cycle power plant by intake air 

cooling using a media evaporative cooler,” 

Energy Conversion and Management, Vol. 

48, 2007, pp. 1055–1064. 

[5] S. O. Oyedepo and O. Kilanko, 

“Thermodynamic Analysis of a Gas Turbine 

Power Plant Modeled with an Evaporative 

Cooler,” International Journal of 

Thermodynamics, Vol. 17, No. 1, 2014, pp. 

14-20. 

[6] S. Agarwal et al., “Performance 

Improvement of a Regenerative Gas 

Turbine Cycle Through Integrated Inlet Air 

Evaporative Cooling and Steam Injection,” 

International Journal of Emerging 

Technology and Advanced Engineering, Vol. 

2, Issue 12, December 2012, pp. 354-363. 

[7] E. Farvaresh et al., “Investigation of Gas 

Turbine Intake Air Cooling via Evaporative 

Media and Its Effects on Cartridge Filters 

Pressures Drop,” International Journal of 

Occupational Hygiene, Vol. 6, No. 2, 2014, 

pp. 75-80. 

[8] A. D. Pascale et al., “Analysis of Inlet Air 

Cooling for IGCC Power Augmentation,” 

Energy Procedia, Vol. 45, 2014, pp. 1265-

1274. 

[9] R. Espanani et al., “Efficiency Improvement 

Methods of Gas Turbine,” Energy and 

Environmental Engineering, Vol. 1(2), 2013, 

pp. 36-54. 

[10] Technical Report, Evaluation of Gas 

Turbine Performance Improvement 

Alternatives for Indonesia Power, Power 

Phase LLC and Indonesian Institute of 

Sciences, No. 1246-001-01, January 28, 

2015. 

[11] Indonesia Diesel prices, liter, available at: 

http://www.globalpetrolprices.com/Indonesi

a/diesel_prices/. 

 

http://www.globalpetrolprices.com/Indonesia/diesel_prices/
http://www.globalpetrolprices.com/Indonesia/diesel_prices/