# Exergy and Environmental Impact Assessment between Solar Powered Gas Turbine and Conventional Gas Turbine Power Plant

Authors: Ali Rajaei; Hasan Barzegar Avval; Elmira Eslami
Journal: International Journal of Chemical Engineering
 (2016)

---

## Abstract

Recuperator is a heat exchanger that is used in gas turbine power plants to recover energy from outlet hot gases to heat up the air entering the combustion chamber. Similarly, the combustion chamber inlet air can be heated up to temperatures up to 1000 (°C) by solar power tower (SPT) as a renewable and environmentally benign energy source. In this study, comprehensive comparison between these two systems in terms of energy, exergy, and environmental impacts is carried out. Thermodynamic simulation of both cycles is conducted using a developed program in MATLAB environment. Exergetic performances of both cycles and their emissions are compared and parametric study is carried out. A new parameter (renewable factor) is proposed to evaluate resources quality and measure how green an exergy loss or destruction or a system as a whole is. Nonrenewable exergy destruction and loss are reduced compared to GT with recuperator cycle by 34.89% and 47.41%, respectively. Reductions in CO2, N
O
x, and CO compared to GT with recuperator cycle by 49.92%, 66.14%, and 39.77%, respectively, are in line with renewable factor value of around 55.7 which proves the ability of the proposed green measure to evaluate and compare the cycles performances.


---

## Body

## 1. Introduction

Recuperation as one of the conventional optimization enhancements in gas turbine cycles by preheating inlet air entering combustor which decreases fuel consumption rate dramatically leads to less greenhouse gas emissions. The other way refers to hybridizing gas cycle with solar power. Advantages of combining solar thermal power with power generation systems are reviewed by Jamel et al. [1]. Renewable sources integration with power cycles with the aim of increasing total exergy efficiency based on different scenarios is performed by them.Several studies are conducted on energy and exergy analysis of hybrid solar gas cycles [2]. Solar power tower as a central receiver system recently has been built in both demonstrational and commercial projects all over the world [3]. Schwarzbözl et al. [4] using advanced software tools carried out design optimization and performance prediction of the solar tower gas turbine power plants. Their project proved feasibility of solar tower integration with conventional gas turbine power plant. It is proved that hybrid solar gas turbine cycles are more efficient in terms of CO2 emission prevention compared to conventional gas cycle with recuperator.Comparing energy systems often is performed through measuring environmental characteristics and performance in terms of energy and exergy analysis [2]. Thermodynamic modeling, second-law based thermodynamic analysis, and multiobjective optimization of a gas turbine power plant with and without recuperator are conducted [5, 6].In this paper, two scenarios are defined based on different heat sources to preheat the air inlet to combustor. First is a conventional gas turbine cycle with recuperator and the second is a solar power tower coupled with a gas turbine where central receiver plays the same role as the recuperator. In order to find inefficiencies in both cycles, exergy analysis is performed by simulating the cycles using MATLAB program.Exergoenvironmental analysis tool by predicting emissions rate helps designing a more sustainable cycle. Environmental impacts including CO2, N
O
x, and CO are measured through the developed code. SOx which is prevented by preoperations in all gas cycles is considered negligible in modeling.This analysis is aimed at quantitatively addressing the impact of renewable and nonrenewable sources on environment by introducing renewable factor. In research studies to the authors’ knowledge, all sources are considered the same. Losses and destructions from various sources are equivalent in common exergy analysis. However, losses and destructions from renewable resources are different from nonrenewable resources since all exergy flows have impacts on environment. In the present work, a new measure is introduced and renewable and nonrenewable loss and destructions are calculated to show the real effect of using renewable resources in environmental impacts reduction.The Present study highlights exergy and exergoenvironmental analysis of both mentioned cycles by measuring their exergy destructions throughout the cycle and comparing their total exergy efficiencies in order to reach a better insight:(i)
To model a new arrangement of new hybrid gas cycle.
(ii)
To conduct exergy and exergoenvironmental analysis in order to find inefficiencies.
(iii)
To propose renewable factor which helps in comparing renewable and nonrenewable sources quantitatively and more accurately.


## 2. System Description and Assumptions

In this research paper, two scenarios are presented. The first one includes heliostat solar field, central receiver, and power generation system while the second one comprises a recuperator instead of prime solar system.Figure1(a) demonstrates SPT cycle designed similarly based on SOLGATE project cycle [4] in which the solar hybrid gas turbine system functions by first concentrating solar energy from a heliostat field (solar field) to a receiver mounted on top of a tower acting as a convective/radiative heat exchanger. These irradiations are converted into heat absorbed by the air coming from compressor. Preheated air enters combustor in order to be mixed with the fuel where the combustion chamber closes the temperature gap between the receiver outlet temperature (800–1000°C at design point) and the turbine inlet temperature (950–1300°C) and provides constant turbine inlet conditions despite fluctuating solar input. The solar power tower technology is used with concentration ratios up to 1000 suns to achieve the high receiver temperatures. More detailed information about the receiver development and test results with receiver temperatures up to 960°C can be found in [7].Figure 1
Schematic diagram of (a) GT-solar cycle and (b) GT-recuperator cycle.
(a)
(b)To model and compare two cycles, thermodynamic modeling of both systems is carried out. Systems are analyzed at their design point using provided data and average yearly DNI for solar system. Then exergy analysis and emission calculations are carried out and systems’ performances are compared.In the second scenario recuperator is used as a replacement of mentioned solar part in first cycle. Several assumptions are made in order to render the analyses in a traceable way considered to model the cycles in the present study which are listed below:(1)
All the processes are assumed to work under steady-state condition.
(2)
Combustion products and air stream are considered ideal gas.
(3)
Natural gas enters combustor as fuel.
(4)
Dead state isP
0
=
1.01 bar and T
0
=
293.15 K.


## 3. Formulation

The present study performed exergy and exergoenvironmental analysis both on each cycle where in the first one solar receiver, as external source, and in the second one recuperator, as internal source, are considered.


### 3.1. Recuperator

The energy balance equation for recuperator which is shown in Figure1 is as follows:(1)
m
˙
a
i
r
h
3
-
h
2
=
m
˙
h
5
-
h
6
η
r
e
c
u
p
.Recuperator efficiency is usually 95–97% and in many cases is considered 100%. Here 97% percent is assumed based on an average value in similar GT cycles [5]:(2)
P
3
P
2
=
1
-
Δ
P
r
e
c
u
p
,where pressure drop through the recuperator is considered 3% of the inlet pressure for both flow streams and through the combustion chamber is 3% of the inlet pressure [5].


### 3.2. Solar System

As shown in Figure1, central receiver has two input streams, solar irradiations and compressed air which gets warmer by absorbing the heat coming from solar rays. In this analysis Q
˙ is the transferred heat rate as(3)
Q
˙
=
H
o
u
t
-
H
i
n
η
r
e
c
,where H
o
u
t and H
i
n are outlet and inlet stream enthalpy:(4)
Q
˙
r
e
c
=
Q
˙
∗
m
˙
a
i
r
,
S
o
l
a
r
s
h
a
r
e
=
Q
˙
r
e
c
m
˙
F
∗
L
H
V
+
Q
˙
r
e
c
.Solar share shows renewable heat source contribution into conventional fossil fuel cycles and is defined as below:(5)
S
o
l
a
r
s
h
a
r
e
=
Q
˙
r
e
c
Q
˙
n
a
t
u
r
a
l
g
a
s
+
Q
˙
r
e
c
∗
100
,where Q
˙
n
a
t
u
r
a
l
g
a
s is the supplied heat by fuel:(6)
Q
˙
n
a
t
u
r
a
l
g
a
s
=
m
F
˙
L
H
V
.And Q
˙
r
e
c is the heat released from irradiations into central receiver:(7)
Q
˙
r
e
c
=
η
f
i
e
l
d
η
r
e
c
Q
˙
s
o
l
,
t
o
t
a
l
.One can write(8)
Q
˙
s
o
l
,
t
o
t
a
l
=
A
∗
D
N
I
.DNI is defined as direct normal irradiance which varies related to the geographical situation and a constant annual average value for a certain location is assumed.


### 3.3. Exergy Analysis

Exergy analysis is a powerful tool in referring exergy destructions in a power cycle while these wastes cannot be seen through energy analysis [8].It is worth mentioning that four concepts are demonstrated in the present study.E
x
F and E
x
P are the fuel and product exergy rate, respectively, and also the exergy loss (E
x
L) is defined as the useful exergy which is wasted to the environment with no converting to the work and exergy destruction (E
x
D) due to irreversibilities.To find the appropriate relation between these concepts, one may write(9)
E
x
F
=
E
x
P
+
E
x
D
.This should be written for all components as shown schematically in Table 1 to calculate the exergy balance in each of them. Considering if the component is assumed adiabatic, the exergy loss would be zero.Table 1
Components exergy balance.
Component
E
x
F
E
x
P
E
x
D
E
x
1
+
Q
r
e
c
η
f
i
e
l
d
1
-
T
0
T
s
u
n
E
x
2
E
x
D
=
E
x
F
-
E
x
P
-
Q
1
-
T
s
u
n
T
0
E
x
l
o
s
s
=
Q
1
-
T
T
0
η
e
x
=
E
x
P
E
x
F
E
x
1
+
W
2
E
x
2
E
x
D
=
E
x
2
-
E
x
1
-
W
2
η
e
x
=
E
x
2
E
x
1
+
W
2
E
x
1
-
E
x
2
E
x
4
-
E
x
1
E
x
D
=
E
x
F
-
E
x
P
=
Q
1
-
T
T
0
η
e
x
=
E
x
P
E
x
F
E
x
F
+
E
x
1
E
x
2
E
x
D
=
E
x
F
-
E
x
P
-
Q
1
-
T
T
0
E
x
l
o
s
s
=
Q
1
-
T
T
0
η
e
x
=
E
x
P
E
x
F
E
x
1
-
E
x
2
W
˙
T
E
x
D
=
E
x
1
+
E
x
2
-
W
˙
T
η
e
x
=
W
˙
T
E
x
1
+
E
x
2In this research study, input exergy is supplied from two different sources shown in Figure1. The solar input exergy is defined as below:(10)
E
x
s
o
l
=
Q
r
e
c
η
f
i
e
l
d
1
-
T
0
T
s
u
n
.


### 3.4. Exergoenvironmental Analysis

Although many studies in the literature are conducted based on integration methods between solar power and conventional power plants which mainly are focused on energy and exergy analysis, there is no attention to environmental issues. The present study highlights greenhouse gas emissions reduction through exergoenvironmental analysis which is conducted on both scenarios. It is considered that CO andN
O
x are pollutant emissions in grams per kilogram. The appropriate equations for these pollutants are as follows [9]:(11)
m
˙
N
O
x
=
0.15
E
16
τ
0.5
exp
⁡
-
71100
/
T
p
z
P
3
0.05
Δ
P
3
/
P
3
,
m
˙
C
O
=
0.179
E
99
exp
⁡
7800
/
T
p
z
P
3
2
τ
Δ
P
3
/
P
3
,where τ is the residence time in combustion zone (it is assumed constant and is equal to 0.002 s), T
p
z is the primary zone combustion temperature, P
3 is the combustor inlet pressure, and Δ
P
3
/
P
3 is the nondimensional pressure drop in the combustion chamber.Accordingly CO2 is calculated as below [6]:(12)
ε
=
m
˙
C
O
2
W
˙
n
e
t
.


## 3.1. Recuperator

The energy balance equation for recuperator which is shown in Figure1 is as follows:(1)
m
˙
a
i
r
h
3
-
h
2
=
m
˙
h
5
-
h
6
η
r
e
c
u
p
.Recuperator efficiency is usually 95–97% and in many cases is considered 100%. Here 97% percent is assumed based on an average value in similar GT cycles [5]:(2)
P
3
P
2
=
1
-
Δ
P
r
e
c
u
p
,where pressure drop through the recuperator is considered 3% of the inlet pressure for both flow streams and through the combustion chamber is 3% of the inlet pressure [5].


## 3.2. Solar System

As shown in Figure1, central receiver has two input streams, solar irradiations and compressed air which gets warmer by absorbing the heat coming from solar rays. In this analysis Q
˙ is the transferred heat rate as(3)
Q
˙
=
H
o
u
t
-
H
i
n
η
r
e
c
,where H
o
u
t and H
i
n are outlet and inlet stream enthalpy:(4)
Q
˙
r
e
c
=
Q
˙
∗
m
˙
a
i
r
,
S
o
l
a
r
s
h
a
r
e
=
Q
˙
r
e
c
m
˙
F
∗
L
H
V
+
Q
˙
r
e
c
.Solar share shows renewable heat source contribution into conventional fossil fuel cycles and is defined as below:(5)
S
o
l
a
r
s
h
a
r
e
=
Q
˙
r
e
c
Q
˙
n
a
t
u
r
a
l
g
a
s
+
Q
˙
r
e
c
∗
100
,where Q
˙
n
a
t
u
r
a
l
g
a
s is the supplied heat by fuel:(6)
Q
˙
n
a
t
u
r
a
l
g
a
s
=
m
F
˙
L
H
V
.And Q
˙
r
e
c is the heat released from irradiations into central receiver:(7)
Q
˙
r
e
c
=
η
f
i
e
l
d
η
r
e
c
Q
˙
s
o
l
,
t
o
t
a
l
.One can write(8)
Q
˙
s
o
l
,
t
o
t
a
l
=
A
∗
D
N
I
.DNI is defined as direct normal irradiance which varies related to the geographical situation and a constant annual average value for a certain location is assumed.


## 3.3. Exergy Analysis

Exergy analysis is a powerful tool in referring exergy destructions in a power cycle while these wastes cannot be seen through energy analysis [8].It is worth mentioning that four concepts are demonstrated in the present study.E
x
F and E
x
P are the fuel and product exergy rate, respectively, and also the exergy loss (E
x
L) is defined as the useful exergy which is wasted to the environment with no converting to the work and exergy destruction (E
x
D) due to irreversibilities.To find the appropriate relation between these concepts, one may write(9)
E
x
F
=
E
x
P
+
E
x
D
.This should be written for all components as shown schematically in Table 1 to calculate the exergy balance in each of them. Considering if the component is assumed adiabatic, the exergy loss would be zero.Table 1
Components exergy balance.
Component
E
x
F
E
x
P
E
x
D
E
x
1
+
Q
r
e
c
η
f
i
e
l
d
1
-
T
0
T
s
u
n
E
x
2
E
x
D
=
E
x
F
-
E
x
P
-
Q
1
-
T
s
u
n
T
0
E
x
l
o
s
s
=
Q
1
-
T
T
0
η
e
x
=
E
x
P
E
x
F
E
x
1
+
W
2
E
x
2
E
x
D
=
E
x
2
-
E
x
1
-
W
2
η
e
x
=
E
x
2
E
x
1
+
W
2
E
x
1
-
E
x
2
E
x
4
-
E
x
1
E
x
D
=
E
x
F
-
E
x
P
=
Q
1
-
T
T
0
η
e
x
=
E
x
P
E
x
F
E
x
F
+
E
x
1
E
x
2
E
x
D
=
E
x
F
-
E
x
P
-
Q
1
-
T
T
0
E
x
l
o
s
s
=
Q
1
-
T
T
0
η
e
x
=
E
x
P
E
x
F
E
x
1
-
E
x
2
W
˙
T
E
x
D
=
E
x
1
+
E
x
2
-
W
˙
T
η
e
x
=
W
˙
T
E
x
1
+
E
x
2In this research study, input exergy is supplied from two different sources shown in Figure1. The solar input exergy is defined as below:(10)
E
x
s
o
l
=
Q
r
e
c
η
f
i
e
l
d
1
-
T
0
T
s
u
n
.


## 3.4. Exergoenvironmental Analysis

Although many studies in the literature are conducted based on integration methods between solar power and conventional power plants which mainly are focused on energy and exergy analysis, there is no attention to environmental issues. The present study highlights greenhouse gas emissions reduction through exergoenvironmental analysis which is conducted on both scenarios. It is considered that CO andN
O
x are pollutant emissions in grams per kilogram. The appropriate equations for these pollutants are as follows [9]:(11)
m
˙
N
O
x
=
0.15
E
16
τ
0.5
exp
⁡
-
71100
/
T
p
z
P
3
0.05
Δ
P
3
/
P
3
,
m
˙
C
O
=
0.179
E
99
exp
⁡
7800
/
T
p
z
P
3
2
τ
Δ
P
3
/
P
3
,where τ is the residence time in combustion zone (it is assumed constant and is equal to 0.002 s), T
p
z is the primary zone combustion temperature, P
3 is the combustor inlet pressure, and Δ
P
3
/
P
3 is the nondimensional pressure drop in the combustion chamber.Accordingly CO2 is calculated as below [6]:(12)
ε
=
m
˙
C
O
2
W
˙
n
e
t
.


## 4. Results and Discussion

### 4.1. Single GT, GT-Recuperator, and GT-Solar Performance Comparison

In terms of exergy and environmental impacts, three mentioned cycles are compared. Exergy efficiency and CO2 emission for three mentioned cycles are presented in Figure 2. Exergy efficiency for the GT-solar is the least and for the recuperator is the most. It is a clear result of efficiency definition and the vast difference between solar input exergy and fuel exergy. Solar exergy due to high temperature value of its resource is much higher in comparison to fuel exergy. However, solar energy implementation reduces the natural gas consumption rate dramatically and so the emission for this cycle is about half the size of the conventional cycles. Due to higher efficiency in recuperator relative to single GT cycle, emission and fuel flow rate are lower. For cycle with single sources of exergy or energy, efficiency and CO2 emission are often correlated inversely.Figure 2
Efficiency-emission for different scenarios.Exergy flow in these three different cycles shows similar behavior. In Figure3 exergy destruction rates in single GT are shown. As it is presented combustor is the greatest exergy destructor by 77 percent of overall destruction rate. Similarly in GT-recuperator cycle, it is also presented the same trend.Figure 3
Exergy destruction distribution in GT cycle.67 percent of overall exergy destruction is related to combustor in GT-recuperator. 10 percent reduction in destruction is due to higher temperature inlet to the combustor which reduced the combustion rate. If we consider the recuperator as another internal source of exergy, the overall destruction rate in cycle resources is 71 percent in GT-recuperator cycle which is shown in Figure4.Figure 4
Exergy destruction distribution in GT-recuperator cycle.GT-solar has shown a similar trend by 71 percent of exergy destruction in solar part (from sun to air flow) and 23 percent in combustor. In fact 94 percent of exergy destruction is related to exergy or energy resources conversion parts which has the highest value among other cycles. Figure5 shows destruction distribution in GT-solar cycle.Figure 5
Total exergy destruction distribution in GT-solar cycle.Energy resources destruction percentages of total in three cycles are presented and compared in Figure6 and show the same trend as exergy efficiency. So one may conclude that the cycle with the less exergy destruction in energy resources is the most efficient cycle.Figure 6
Contribution of exergy destruction in resource conversion components in different cycles.


### 4.2. Renewable Resources versus Nonrenewable Resources

In terms of exergy, GT-solar hybrid is the worst cycle. Exergy definition by itself does not provide an insight into the resources types.The earth receives solar energy daily and continuously and it is absorbed, transformed, rejected, and stored in various types of energy or phenomena. On the other hand, fossil fuels are not energy resources on the plant except for human being. In fact what we are using as fossil fuels are out of the earth, usually ecology, and are the only human being impact or footprint on the environment. So any destruction or losses due to fossil fuels can be considered as pollution or impacts on environment.Here, to give our resources a meaning in destruction, we define renewable and nonrenewable exergy destruction and losses. Exergy losses are important due to the fact that streams with exergy can potentially cause changes in environment because of their exergy. Both single GT and GT-recuperator cycles are purely nonrenewable. However, in GT-solar cycle sources are different. To calculate the renewable and nonrenewable exergy destruction and losses rates in GT-solar cycle, we use the following method.Exergy comes from two different sources, sun and natural gas. We define resource distribution factor as follows:(13)
f
r
e
n
e
w
a
b
l
e
=
Δ
E
x
a
i
r
r
e
c
Δ
E
x
a
i
r
r
e
c
+
Δ
E
x
f
l
u
e
g
a
s
c
o
m
b
.Then we assume that exergy of working fluid is the algebraic combination of various resources. Now we can provide the following equations for exergy destruction and losses:(14)
E
x
L
non-renwable
=
1
-
f
r
e
n
e
w
a
b
l
e
E
x
L
t
o
t
a
l
,
E
x
d
i
non-renwable
=
1
-
f
r
e
n
e
w
a
b
l
e
i
E
x
d
i
t
o
t
a
l
.Furthermore, exergy destruction in solar system is considered purely renewable and destruction in combustor is considered purely nonrenewable. Implementing equations and definitions presented above, nonrenewable destruction distribution is presented in Figure 7.Figure 7
Nonrenewable exergy destruction distribution in GT-solar cycle (kW).Figure8 shows the value of nonrenewable destruction and losses in different cycles. Implementing nonrenewable losses and destructions, the main advantage of the GT-solar cycle is quantitatively measured. Nonrenewable losses which are impacts of human beings activities on environment have their least value in GT-solar cycle.Figure 8
Nonrenewable exergy destruction and losses in different cycles.GT-solar cycle parameters are summarized in Table2. In this table, parameters like solar share, exergy inputs, efficiency, and destruction of different components are presented. Data are assumed based on project SOLGATE [4].Table 2
Performance parameters of GT-solar cycle.
Parameter
Value
Pressure ratio
14
TIT (°C)
1080
η
c
o
m
p (%)
0.835
η
G
T (%)
0.93
Combustor inlet temperature (°C)
800
Receiver efficiency (%)
0.94
Field efficiency (%)
0.55
Receiver pressure drop
0.03
η
r
e
c
u
p (%)
0.97
Exergy efficiencies
Compressor (%)
0.93
Combustor (%)
0.86
Gas turbine (%)
0.97
Receiver (%)
0.41
Exergy destruction rates
Compressor (kW)
908.53
Combustor (kW)
4973.28
Gas turbine (kW)
504.89
Receiver (kW)
15374.38
Overall cycle parameters
Solar share (%)
0.56
f
r
e
n
e
w
a
b
l
e
.557
Total exergy loss (kW)
7310
Total exergy efficiency (%)
0.268
Total exergy destruction (kW)
21761.09
Solar input exergy (kW)
26200
Fuel flow rate (kg/s)
0.264
Air flow rate (kg/s)
33.63
PredictedN
O
x emission (kg/s)
1.27
E
-
10
PredictedC
O emission (kg/s)
0.0108In addition to mentioned analysis,N
O
x and CO emission are predicted for different cycles. Results are tabulated in Table 3. Due to lowest fuel flow rate in GT-solar cycle, emissions are lowest values. N
O
x in GT-recuperator is higher than GT cycle because of higher combustor inlet temperature. CO emission shows an opposite trend.Table 3
N
O
x and C
O emissions.
N
O
x (kg/s)
C
O (kg/s)
GT
3.5478
E
-
10
0.02
GT-REC
3.7395
E
-
10
0.0179
GT-SOL
1.2663
E
-
10
0.0108


## 4.1. Single GT, GT-Recuperator, and GT-Solar Performance Comparison

In terms of exergy and environmental impacts, three mentioned cycles are compared. Exergy efficiency and CO2 emission for three mentioned cycles are presented in Figure 2. Exergy efficiency for the GT-solar is the least and for the recuperator is the most. It is a clear result of efficiency definition and the vast difference between solar input exergy and fuel exergy. Solar exergy due to high temperature value of its resource is much higher in comparison to fuel exergy. However, solar energy implementation reduces the natural gas consumption rate dramatically and so the emission for this cycle is about half the size of the conventional cycles. Due to higher efficiency in recuperator relative to single GT cycle, emission and fuel flow rate are lower. For cycle with single sources of exergy or energy, efficiency and CO2 emission are often correlated inversely.Figure 2
Efficiency-emission for different scenarios.Exergy flow in these three different cycles shows similar behavior. In Figure3 exergy destruction rates in single GT are shown. As it is presented combustor is the greatest exergy destructor by 77 percent of overall destruction rate. Similarly in GT-recuperator cycle, it is also presented the same trend.Figure 3
Exergy destruction distribution in GT cycle.67 percent of overall exergy destruction is related to combustor in GT-recuperator. 10 percent reduction in destruction is due to higher temperature inlet to the combustor which reduced the combustion rate. If we consider the recuperator as another internal source of exergy, the overall destruction rate in cycle resources is 71 percent in GT-recuperator cycle which is shown in Figure4.Figure 4
Exergy destruction distribution in GT-recuperator cycle.GT-solar has shown a similar trend by 71 percent of exergy destruction in solar part (from sun to air flow) and 23 percent in combustor. In fact 94 percent of exergy destruction is related to exergy or energy resources conversion parts which has the highest value among other cycles. Figure5 shows destruction distribution in GT-solar cycle.Figure 5
Total exergy destruction distribution in GT-solar cycle.Energy resources destruction percentages of total in three cycles are presented and compared in Figure6 and show the same trend as exergy efficiency. So one may conclude that the cycle with the less exergy destruction in energy resources is the most efficient cycle.Figure 6
Contribution of exergy destruction in resource conversion components in different cycles.


## 4.2. Renewable Resources versus Nonrenewable Resources

In terms of exergy, GT-solar hybrid is the worst cycle. Exergy definition by itself does not provide an insight into the resources types.The earth receives solar energy daily and continuously and it is absorbed, transformed, rejected, and stored in various types of energy or phenomena. On the other hand, fossil fuels are not energy resources on the plant except for human being. In fact what we are using as fossil fuels are out of the earth, usually ecology, and are the only human being impact or footprint on the environment. So any destruction or losses due to fossil fuels can be considered as pollution or impacts on environment.Here, to give our resources a meaning in destruction, we define renewable and nonrenewable exergy destruction and losses. Exergy losses are important due to the fact that streams with exergy can potentially cause changes in environment because of their exergy. Both single GT and GT-recuperator cycles are purely nonrenewable. However, in GT-solar cycle sources are different. To calculate the renewable and nonrenewable exergy destruction and losses rates in GT-solar cycle, we use the following method.Exergy comes from two different sources, sun and natural gas. We define resource distribution factor as follows:(13)
f
r
e
n
e
w
a
b
l
e
=
Δ
E
x
a
i
r
r
e
c
Δ
E
x
a
i
r
r
e
c
+
Δ
E
x
f
l
u
e
g
a
s
c
o
m
b
.Then we assume that exergy of working fluid is the algebraic combination of various resources. Now we can provide the following equations for exergy destruction and losses:(14)
E
x
L
non-renwable
=
1
-
f
r
e
n
e
w
a
b
l
e
E
x
L
t
o
t
a
l
,
E
x
d
i
non-renwable
=
1
-
f
r
e
n
e
w
a
b
l
e
i
E
x
d
i
t
o
t
a
l
.Furthermore, exergy destruction in solar system is considered purely renewable and destruction in combustor is considered purely nonrenewable. Implementing equations and definitions presented above, nonrenewable destruction distribution is presented in Figure 7.Figure 7
Nonrenewable exergy destruction distribution in GT-solar cycle (kW).Figure8 shows the value of nonrenewable destruction and losses in different cycles. Implementing nonrenewable losses and destructions, the main advantage of the GT-solar cycle is quantitatively measured. Nonrenewable losses which are impacts of human beings activities on environment have their least value in GT-solar cycle.Figure 8
Nonrenewable exergy destruction and losses in different cycles.GT-solar cycle parameters are summarized in Table2. In this table, parameters like solar share, exergy inputs, efficiency, and destruction of different components are presented. Data are assumed based on project SOLGATE [4].Table 2
Performance parameters of GT-solar cycle.
Parameter
Value
Pressure ratio
14
TIT (°C)
1080
η
c
o
m
p (%)
0.835
η
G
T (%)
0.93
Combustor inlet temperature (°C)
800
Receiver efficiency (%)
0.94
Field efficiency (%)
0.55
Receiver pressure drop
0.03
η
r
e
c
u
p (%)
0.97
Exergy efficiencies
Compressor (%)
0.93
Combustor (%)
0.86
Gas turbine (%)
0.97
Receiver (%)
0.41
Exergy destruction rates
Compressor (kW)
908.53
Combustor (kW)
4973.28
Gas turbine (kW)
504.89
Receiver (kW)
15374.38
Overall cycle parameters
Solar share (%)
0.56
f
r
e
n
e
w
a
b
l
e
.557
Total exergy loss (kW)
7310
Total exergy efficiency (%)
0.268
Total exergy destruction (kW)
21761.09
Solar input exergy (kW)
26200
Fuel flow rate (kg/s)
0.264
Air flow rate (kg/s)
33.63
PredictedN
O
x emission (kg/s)
1.27
E
-
10
PredictedC
O emission (kg/s)
0.0108In addition to mentioned analysis,N
O
x and CO emission are predicted for different cycles. Results are tabulated in Table 3. Due to lowest fuel flow rate in GT-solar cycle, emissions are lowest values. N
O
x in GT-recuperator is higher than GT cycle because of higher combustor inlet temperature. CO emission shows an opposite trend.Table 3
N
O
x and C
O emissions.
N
O
x (kg/s)
C
O (kg/s)
GT
3.5478
E
-
10
0.02
GT-REC
3.7395
E
-
10
0.0179
GT-SOL
1.2663
E
-
10
0.0108


## 5. Conclusions

Different cycles are presented and compared according to exergy and environmental analyzing tools. Although GT-solar cycle is the worst according to exergy analysis, its main advantages over other conventional cycles is highlighted when resource valued exergy analysis is used.In addition, the above analysis shows that resource conversion processes are the most destructive ones in the cycle. Furthermore, the cycle exergy efficiency is directly correlated to resource destruction contribution in the cycle.Total exergy destruction in GT-solar cycle is higher than other cycles. However, nonrenewable destruction is the lowest for GT-solar among different scenarios. As nonrenewable destructions and losses have significant impacts on the environment, the best advantage of renewable resources and hybrid GT-solar cycle is minimizing the impacts on the environment.N
O
x, CO, and CO2 emissions are also reduced significantly by using solar hybrid cycle.



---

*Source: 8323859-2016-05-23.xml*