Exergy and Thermoeconomic Analysis for an Underground Train Station Air-Conditioning Cooling System

The necessity of air-conditioning causes the enormous energy use of underground train stations. Exergy and thermoeconomic analysis is applied to the annual operation of the air-conditioning system of a large underground train station in Taiwan. The current installation and the monitored data are taken to be the base case, which is then compared to three different optimized designs. The total revenue requirement levelized cost rate and the total exergy destruction rate are used to evaluate the merits. The results show that the cost optimization objective would obtain a lower total revenue requirement levelized cost rate, but at the expense of a higher total exergy destruction rate. Optimization of thermodynamic efficiency, however, leads to a lower total exergy destruction rate, but would increase the total revenue requirement levelized cost rate significantly. It has been shown that multi-objective optimization would result in a small marginal increase in total revenue requirement levelized cost rate, but achieve a significantly lower total exergy destruction rate. Results in terms of the normalized total revenue requirement levelized cost rate and the normalized total exergy destruction rate are also presented. It has been shown by second law analysis when applied to underground train stations that lower annual energy use and lower CO2 emissions can be achieved.


Introduction
The necessity of air-conditioning and also long operation hours is a major cause of the enormous amount of energy use for an underground train station.In this study, exergy and thermoeconomic analysis is applied to an underground train station that was constructed in Taiwan in recent years.The current status of the station is taken as the base case.Exergy indicates both the quality and the quantity in the energy conversion.Exergy destruction in reverse is the indicator of energy loss in terms of quality and quantity.Exergy is in fact indicative of thermodynamic second law efficiency.For the practical concerns of cost and economy, the total revenue requirement levelized cost rate can be used to evaluate the merit [1].
Some research literature can be found in the field of exergy and thermoeconomic analysis.However, only some is on the optimization of air-conditioning systems.Moreover, in some of the literature, only one of the exergetic or thermoeconomic criteria is considered.The exergetic criteria were discussed in many articles.Kodala et al. [2] studied the irreversibility of the thermoeconomic performance of refrigerators and heat pumps.Kodala et al. [3] investigated the thermoeconomic optimization of a two-stage combined heat pump system.Yumrutas et al. [4] performed exergy analysis on vapor compression refrigeration systems.Rezaie et al. [5] used exergy analysis for residential buildings' assessment.Lu et al. [6] studied the patterns of domestic energy consumption using exergy analysis.Marletta et al. [7] applied exergy analysis to assess different constructions of air-conditioning systems.
In the field of thermal systems, Yilmaz et al. [8] applied second law analysis to evaluate the performance of heat exchangers.Bejan [9] analyzed the optimized geometry of engineering flow in terms of thermodynamics.Bisio and Rubatto [10] studied different aspects of irreversible processes in closed and steady-state open systems.Chen et al. [11] studied the optimal performance of an irreversible absorption refrigerator.Wall and Gong [12] presented the concept of exergy in sustainable development.Abhilash et al. [13] applied exergy efficiency to evaluate the inlet air cooling system for a centrifugal compressor.
There are several studies on thermoeconomic criteria.Sciubba [14] presented the concept of extended exergy accounting for the design of thermal systems.Li et al. [15] studied the economic benefits of automated fault detection and diagnosis for rooftop air-conditioners.Sivasakthivel et al. [16] discussed the optimized operating parameters for ground source heat pump systems.Liu and Niu [17] developed an optimal design analysis for heat recovery devices in buildings.Piacentino and Talama [18] proposed an improved thermoeconomic approach to the increase the reliability of the refrigeration system.The above studies show that multi-objective optimization can be applied to deal with different and competing objectives.
Multi-objective optimization of energy systems has attracted some attention in the related fields of research in recent years.Multi-objective optimization was used by Sayyadi and Nejatolahi [19] for a cooling tower-assisted refrigeration system.The total revenue requirement method and the total exergy destruction of the system were applied in their study.Sayyadi and Nejatolahi [20] also carried out multi-objective optimization for a cooling tower-assisted ground source heat pump.Three optimized objectives were included in their study.Sun et al. [21] investigated the relationship between the economic cost and the reliability of city electric supply.
More published literature on multi-objective optimization can be found recently.Rosen [22] discussed the economic benefits of applying the concept of exergy.In the area of thermal systems, published literature on multi-objective optimization can be found for CO 2 /NH 3 refrigeration, integrated molten carbonate fuel cells, the organic Rankine cycle, combined gas turbines and solar energy [23][24][25][26][27].
Performance models of chillers and pumps for air-conditioning systems can be found in the research literature [28][29][30][31].For dynamic energy saving control, Ma et al. [32] presented a real-time supervisory control strategy for building cooling water systems.
In the area of increasing the energy efficiency of air-conditioning, Du et al. [33] present a control-perfect index based on exergy analysis.They use the index to evaluate the control of an air-conditioning system.A novel cascade air-conditioning system of a 100-kW capacity of a sample building was proposed by Hojjat Mohammadi and Ameri [34].Zagoet et al. [35] analyzed different combinations of heating systems and evaluated the primary energy efficiency for residential buildings in northern Italy.
In summary, most of the research on exergy and thermoeconomic analysis for air-conditioning systems has been of simple systems and at fixed state conditions.However, for an underground station, the air-conditioning operation is dynamic, also with the variation in ambient temperature.The energy use would be enormous when the underground train station is situated in a subtropical region, like Taiwan.Design analysis to balance the construction cost and energy efficiency is of upmost importance.This study considers the operation and maintenance cost due to the selection of systems that were overlooked in most of the published literature.In this study, the objective functions are the total revenue requirement levelized cost rate of the system .C TRRL and the total exergy destruction rate .I tot .The monitored operation of the present system was taken to be the base case, against different cases of optimization.The results presented are based on an actual underground train station.

The Underground Train Station and Its Air-Conditioning System
The underground train station is located in Taipei, Taiwan, which began operation in 2011.The station building has dimensions of 330 m in length, 24 m in width and 21 m underground.The floor plan of the station includes the U-2F (2 floors underground) platform area, the U-1F (1 floor underground) concourse area, the G + 1F (ground level) lobby and retail and the G + 2F (second floor) retail store area.The G + 2F retail store area has a separate air-conditioning system and is metered separately; therefore, it was not included in this study.The floor plan of the station and the different zones served by a general and a 24-h system are shown in Figure 1.Zones enclosed by blue lines were served by the general system, and those enclosed by green lines were served by the 24-h system.

The Underground Train Station and Its Air-Conditioning System
The underground train station is located in Taipei, Taiwan, which began operation in 2011.The station building has dimensions of 330 m in length, 24 m in width and 21 m underground.The floor plan of the station includes the U-2F (2 floors underground) platform area, the U-1F (1 floor underground) concourse area, the G + 1F (ground level) lobby and retail and the G + 2F (second floor) retail store area.The G + 2F retail store area has a separate air-conditioning system and is metered separately; therefore, it was not included in this study.The floor plan of the station and the different zones served by a general and a 24-hour system are shown in Figure 1.Zones enclosed by blue lines were served by the general system, and those enclosed by green lines were served by the 24-hour system.The 24-h air-conditioning system serves specific areas, including the central control room, the telecom room, the UPS room, the main power station, the power relay room and also the ticket area.The rest of the station is served by the general air-conditioning system, such as the G + 1F lobby and retail area, the U-1F concourse area and the U-2F platform area, as shown in Figure 2.
Entropy 2016, 18, 86 4 of 20 The 24-hour air-conditioning system serves specific areas, including the central control room, the telecom room, the UPS room, the main power station, the power relay room and also the ticket area.The rest of the station is served by the general air-conditioning system, such as the G + 1F lobby and retail area, the U-1F concourse area and the U-2F platform area, as shown in Figure 2.

Energy Exergy and Thermoeconomic Analysis
The hourly monitored data used for the base case (BC) were collected from the building automation system (BAS), supplemented by information from the equipment suppliers, the Central Weather Bureau of Taiwan and also the local power company for the year 2012.

Energy Analysis
The cooling capacity (kW) of a chiller can be calculated as: In Equation (1), is the chilled water flowrate.and are the chilled water temperatures flowing in and out through the evaporator, respectively.The specific heat capacity of

Energy Exergy and Thermoeconomic Analysis
The hourly monitored data used for the base case (BC) were collected from the building automation system (BAS), supplemented by information from the equipment suppliers, the Central Weather Bureau of Taiwan and also the local power company for the year 2012.

Energy Analysis
The cooling capacity .Q(kW) of a chiller can be calculated as: .Q " .m we c p pT ei ´Teo q (1) In Equation ( 1), .
m we is the chilled water flowrate.T ei and T eo are the chilled water temperatures flowing in and out through the evaporator, respectively.The specific heat capacity of water C P = 4.186 kJ¨kg ´1¨K ´1. Figure 2 shows that there is more than one chiller for each system.The average coefficient of performance COP avg of the chillers for either the general or the 24-h systems can be calculated using Equation (2): m we,kj c p pT ei,kj ´Teo,kj qs{ In Equation ( 2), k is the number of chillers, and j is each of the operating hour in a year.
. W ac,kj is the compressor of the acting chiller in the hour.In times of lower cooling demand, only one chiller would be operating.
The operating power (kW) of a pump, either for a chilled water pump or a condensing water pump, can be calculated by using Equation (3): .
ν is the volume flow rate m 3 ¨s´1 and ∆ p is the pressure jump (Pa) though the pump.The total power consumption of an air-conditioning system can be calculated as in Equation ( 4 In Equation ( 4 W CT are respectively the power load of chilled water pumps, condensing water pumps, air handling units (AHU) or fan coils (FC), chillers and cooling towers.In this study, a system performance factor (SPF) for the entire system can be expressed as Equation (5): W tot (5) .Q e is the cooling capacity of the air-conditioning system.

Exergy Analysis
Kummel [36] relates the second law to economics.Exergy can be taken as the flow availability of a system that performs the maximum reversible work.Regarding the scope of this study, the kinetic and the potential work can be neglected.Hence, exergy can be expressed as H ´H0 ´T0 (S ´S0 ), where H is the enthalpy and S is the entropy of the respective states.T 0 (S ´S0 ) is the entropy generation term or exergy destruction against the dead state.Sayyaadi and Neiatolahi [19] stated that a more convenient form of the exergy of a flowing system consists of a temperature component and a pressure component Ex = Ex T + Ex P .In this study the pressure component is neglected.The exergy of an air-conditioning system can be defined to be the maximum useful work attainable from a heat transfer process.Lu and Wu [6] mentioned that in differential form, exergy can be expressed as in Equation ( 6): Integrating from the given state (T ei , T eo ) to the dead state (T 0 ), which is the ambient condition in this study, a general equation for calculating exergy rate .
Q e is the refrigeration effect (kW), T 0 is the outdoor temperature (the reference environment temperature), T ei is inlet chiller water temperature and T eo is the outlet chiller water temperature.The thermodynamic second law efficiency (exergy efficiency) can be expressed as Equation ( 8): In this study, the total exergy destruction rate is the sum of the general and the 24-h systems, as expressed in Equation ( 9): . I tot,gen are the exergy destruction rate for the total, the 24-h system and the general air-conditioning system, respectively.

Thermoeconomic Analysis
The thermoeconomic analysis has to consider the construction cost, amortization, maintenance and electricity consumption.In this study, the total revenue requirement levelization (TRRL) method was applied.In this study, the TRRL method takes into account the estimated total carrying charge, along with assumptions for economic, financial and market input parameters calculated on a yearly basis.Moreover, the non-uniform annual monetary values of the carrying charges, maintenance cost and electricity cost are levelized and converted to an equivalent series of constant payments (annuities) [37].
TRRL can be computed as in Equation ( 10): In Equation (10), CRF is the capital recovery factor.TRR j is the total revenue requirement in the j-th year of system operation, and i e f f is the interest rate (%).In applying Equation (10), each monetary transaction is assumed to occur at year end.The capital recovery factor CRF is calculated by Equation (11): In Equation (11), n is the economic lifetime in years.The series of payments of the annual electrical cost EC j can be calculated using Equation ( 12): In Equation ( 12), r EC is the constant escalation.The levelized value EC L can then be determined multiplying the first year electricity cost EC 0 (NT) by the constant escalation levelization factor (CELF) as Equation ( 13): In Equation ( 13), k EC " p1 `rEC q{p1 `ieff q.The terms r EC and CRF are respectively the annual escalation rate of electricity cost and the capital recovery factor.EC 0 can be computed by Equation ( 14): In Equation ( 14), C elect is the electricity price per kWh in Taiwan taken as 3.1 NT/kWh.The total annual electric consumption (kWh) includes that of the chiller water pump (E pu, ch ), condensing water pumps (E pu, cd ), air side equipment (E AHU, FC ), such as air handling units (AHU) and fan coils (FC), water chillers (E ch ) and cooling towers (E CT ).
The levelized annual operating and maintenance costs OMC L are given in Equation ( 15): where k OMC " 1 `rOMC 1 `ie f f , and the term r OMC is a constant representing the nominal escalation rate for the operating and maintenance costs.
The economic operating lifetime of the system is taken to be 15 years.Therefore, the magnitude of the economic constant, such as i e f f , r OMC and r EC are taken to be 0.02, 0.03 and 0.03, respectively, in the analysis.
For the air-conditioning system, the annual total revenue requirement levelization (TRRL) is equal to the sum of the carrying charge levelization (CCL), electricity costs levelization (ECL) and operating and maintenance cost levelization (OML), as shown in Equation ( 16): The levelized cost rate of the total revenue requirement can be calculated by Equation ( 17): . C TRRL " .
C TRRL is the hourly cost of the total revenue requirement levelization.The hourly rates of CCL and ECL are to be calculated separately for the general and the 24-h systems.The annual operating hours of the 24-h and the general systems, m 24h and m gen , are 8784 h and 4870 h, respectively, according to the actual operation of the train station.
In this study, the reduction of carbon dioxide (CO 2 ) emissions due to energy saving was estimated.The emission of carbon dioxide per kWh of electricity used given by Taipower [38] for the year of 2012 was 0.522 kg/kWh.

Empirically-Based Performance Models of Equipment
The energy performance models of chillers refer to Lee et al. [29] and Jiang and Reddy [30].The regression models of the chillers and pumps are fitted using data provided by equipment suppliers.These models are used in thermoeconomic and exergy analysis in this study.
In Equation (18), the regression constants β1-β4 are determined by regressing the performance data provided by equipment suppliers.
Similarly, the power consumption of chilled water pumps and condensing water pumps .
W pu can be expressed in regression form, as shown in Equation ( 19): The independent variable is only the volumetric flow rate .V, whether of the chilled water or the condensing water.The regression constants α 1 -α 3 are determined by regressing the performance data provided by equipment suppliers.

Multi-Objective Optimization
The two objective functions studied are the economic and thermodynamic objective functions shown in Equation (20) and Equation ( 21 The multi-objective optimization refers to the method of the Pareto optimal frontier [39].In Equations ( 20) and ( 21 I tot would lies between 0 and 1.In this study, the decision variables of selecting chillers are: (1) Using screw or centrifugal compressors, constant or variable speed drive.
Similarly, the decision variables of selecting pumps are: (1) Pumps with constant speed drive or variable speed drive.
(3) The pump pressure and water volumetric flow rate (m ´3¨s ´1).(4) The cost of pumps.
Three optimization cases are compared to the base case, with the operating parameters described in Tables 1 and 2. The three cases are namely cost consideration (CC), thermodynamic efficiency (TE) and multiple objectives of efficiency and cost (MO).The operation constraints of the 24-h and the general air-conditioning systems are listed in Tables 1 and 2. Constraints of these decision variables are partly the limitations emanating from the technical data of equipment suppliers.For the general system, the total chilled water flow rate is 4032 kg/min (equivalent to liters per minute (lpm) for water) and is 1210 kg/min for the 24-h system.It is noted that the variable frequency drive (VFD) is applied to the chillers and pumps in Case TE and Case MO.VFD systems general cost more, but it would better match the cooling demand and the overall operation of the system.

Electricity Consumption and Electricity Cost of the Underground Train Station
The electricity use of an underground train station is vastly different from a commercial building.The train station studied would begin operation at 4:30 A.M. with the general air-conditioning system started at about 6:30 A.M. The hourly monitored power use of the station (the base case (BC)) is presented in Figure 3. Figure 3 shows that for summer months, the peak power occurs in the afternoon of the day.The monthly electricity cost of the underground station is presented in Figure 4, which clearly indicates that the peak power use of air-conditioning happens in the summer months.It is then obvious that air-conditioning constituted a significant part of the total electricity cost of the underground train station and is also the major cause of the peak power load.
the summer months.It is then obvious that air-conditioning constituted a significant part of the total electricity cost of the underground train station and is also the major cause of the peak power load.

Refrigerating Energy and Exergy of Underground Train Station
The hourly refrigerating capacity of the air-conditioning system is calculated using Equation (1) for each operating hour.The daily cooling load is shown in Figure 5.The 24-hour air-conditioning system appears to have an almost constant load through the year.The general system has high peak demand in summer months.The daily refrigeration exergy is determined from Equation (7).The computed results are shown in Figure 6.The chilled water temperature Te in Equation ( 6) is from the monitored data of the station.The ambient temperature T0 was obtained from the Central Weather Bureau of Taiwan [40].
Comparing the results in Figures 5 and 6, it is noted that exergy is about one tenth of the refrigeration effect indicating that the ideal COP of a chiller would be larger than 10, significantly higher than commercial products.The chiller's performance used in this study is presented in Tables 1 and 2. the summer months.It is then obvious that air-conditioning constituted a significant part of the total electricity cost of the underground train station and is also the major cause of the peak power load.

Refrigerating Energy and Exergy of Underground Train Station
The hourly refrigerating capacity of the air-conditioning system is calculated using Equation (1) for each operating hour.The daily cooling load is shown in Figure 5.The 24-hour air-conditioning system appears to have an almost constant load through the year.The general system has high peak demand in summer months.The daily refrigeration exergy is determined from Equation (7).The computed results are shown in Figure 6.The chilled water temperature Te in Equation ( 6) is from the monitored data of the station.The ambient temperature T0 was obtained from the Central Weather Bureau of Taiwan [40].
Comparing the results in Figures 5 and 6, it is noted that exergy is about one tenth of the refrigeration effect indicating that the ideal COP of a chiller would be larger than 10, significantly higher than commercial products.The chiller's performance used in this study is presented in Tables 1 and 2.

Refrigerating Energy and Exergy of Underground Train Station
The hourly refrigerating capacity of the air-conditioning system is calculated using Equation (1) for each operating hour.The daily cooling load is shown in Figure 5.The 24-h air-conditioning system appears to have an almost constant load through the year.The general system has high peak demand in summer months.The daily refrigeration exergy is determined from Equation (7).The computed results are shown in Figure 6.The chilled water temperature T e in Equation ( 6) is from the monitored data of the station.The ambient temperature T 0 was obtained from the Central Weather Bureau of Taiwan [40].
Comparing the results in Figures 5 and 6 it is noted that exergy is about one tenth of the refrigeration effect indicating that the ideal COP of a chiller would be larger than 10, significantly higher than commercial products.The chiller's performance used in this study is presented in Tables 1 and 2.  The monthly average COP of the chillers computed is shown in Figure 7. Chillers of the general air-conditioning system are shown to have higher COP.Larger capacity centrifugal chillers normally are more energy efficient.However, the average COP is significantly less than that obtained from the above exergy analysis.It is also noted that Case TE has the highest average COP followed by Case MO, with Case CC having the lowest average COP.The monthly average COP of the chillers computed is shown in Figure 7. Chillers of the general air-conditioning system are shown to have higher COP.Larger capacity centrifugal chillers normally are more energy efficient.However, the average COP is significantly less than that obtained from the above exergy analysis.It is also noted that Case TE has the highest average COP followed by Case MO, with Case CC having the lowest average COP.The monthly average COP of the chillers computed is shown in Figure 7. Chillers of the general air-conditioning system are shown to have higher COP.Larger capacity centrifugal chillers normally are more energy efficient.However, the average COP is significantly less than that obtained from the above exergy analysis.It is also noted that Case TE has the highest average COP followed by Case MO, with Case CC having the lowest average COP.
The annual energy consumption of pumps calculated from the performance models is shown in Tables 3 and 4. The performance models for each of the optimization cases are based on the pump energy efficiency shown in Tables 1 and 2. Case TE has the lowest pump energy consumption followed by Case MO.Case CC has the highest energy consumption as lower energy efficiency pumps are used.The annual energy consumption of pumps calculated from the performance models is shown in Tables 3 and 4. The performance models for each of the optimization cases are based on the pump energy efficiency shown in Tables 1 and 2. Case TE has the lowest pump energy consumption followed by Case MO.Case CC has the highest energy consumption as lower energy efficiency pumps are used.Table 5 shows the annual energy use of the air-conditioning systems.Pump energy is the second largest item of energy use.This is the characteristics of an underground train station as long pipelines are needed to deliver chilled water and condensing water.The air side equipment, such as AHU and FC, are not optimized in this study, nor are the cooling towers.It is also noted in Table 5 that chillers make up about half of the total energy use.The monthly average SPF and the second law efficiency of the air-conditioning system are shown in Figure 8.The results are computed using the monitored data of the underground train station in 2012.It can be seen in Figure 8 that SPF is higher than 2.5 for most of the months.The results indicate one unit of energy input would have more than 2.5 units of refrigeration effect.SPF is calculated using Equation (5).The second law efficiency of the system was evaluated using Equation (8).

Multi-Objective Optimization
In this study, the multi-objective functions are the normalized total revenue requirement  6.The second law efficiency (efficiency of exergy) is evaluated against the maximum useful work.Therefore, the second law efficiency has a maximum value of 1.0.It can be seen in Figure 8 that the second law efficiency is lower than 0.3.In related works found in the research literature, the second law efficiency was evaluated for each component of the air-conditioning system and mostly calculated for ideal cycle operation.In this study, the actual operation of the entire system is evaluated for either SPF or the second law efficiency.

Multi-Objective Optimization
In this study, the multi-objective functions are the normalized total revenue requirement  6.

Energy Exergy and Thermoeconomic Analysis
The results presented in Table 7 are reevaluated for an economic lifetime of 15 years.For the Case CC, in order to lower the initial construction cost, lower energy efficiency equipment is selected.Consequently, Case CC has the highest electricity cost, the lowest exergy efficiency, the lowest system performance factor (SPF) and the highest CO2 emission.At the same time, Case CC has the lowest carrying charge rate and the lowest total revenue requirement levelized rate.In comparison, when thermodynamic efficiency is the sole concern (Case TE), the highest system performance and exergy efficiency are obtained.However, Case TE has the highest total revenue requirement levelized rate.For the case of multi-objective optimization (Case MO), a balance of cost

Energy Exergy and Thermoeconomic Analysis
The results presented in Table 7 are reevaluated for an economic lifetime of 15 years.For the Case CC, in order to lower the initial construction cost, lower energy efficiency equipment is selected.Consequently, Case CC has the highest electricity cost, the lowest exergy efficiency, the lowest system performance factor (SPF) and the highest CO 2 emission.At the same time, Case CC has the lowest carrying charge rate and the lowest total revenue requirement levelized rate.In comparison, when thermodynamic efficiency is the sole concern (Case TE), the highest system performance and exergy efficiency are obtained.However, Case TE has the highest total revenue requirement levelized rate.For the case of multi-objective optimization (Case MO), a balance of cost and efficiency is the concern.The results show that the construction cost of MO is slightly higher than the base case (BC), but would result in a system performance factor (SPF) and second law efficiency (exergy efficiency) next to Case TE.It is also noted that Case BC, compared to Case TE and Case MO, has higher electricity consumption, lower SPF and higher annual CO 2 emission.It is known that Case BC was designed for energy saving.However, when exergy and thermodynamic analysis is applied for further analysis, BC is not an optimal design.The comparison of the exergy destruction .
I tot for the components of the air-conditioning system is shown in Figure 10.The chiller is the largest item of exergy destruction, followed by pumps and air side equipment.As the air side components are not included in the analysis, the exergy destruction of AHU and FC is the same for the four cases.The main reason that air side equipment is not included in the evaluation is due to the uncertainty in the monitored data.When the entire system is concerned, Case CC has exergy destruction significantly higher than all other cases.When cost and energy saving are both considered, Case MO is superior to Case BC in terms of exergy destruction.
Entropy 2016, 18, 86 16 of 20 exergy destruction of AHU and FC is the same for the four cases.The main reason that air side equipment is not included in the evaluation is due to the uncertainty in the monitored data.When the entire system is concerned, Case CC has exergy destruction significantly higher than all other cases.When cost and energy saving are both considered, Case MO is superior to Case BC in terms of exergy destruction.The comparison of the levelized cost rate is shown in Figure 11.Case CC has the lowest carrying charge cost rate due to the lower construction cost, but has significantly higher electricity cost over the other cases.When the total revenue requirement levelized cost rate is compared, Case CC is less than Case BC by 33 NT/h.Case MO has a total revenue requirement levelized cost The comparison of the levelized cost rate is shown in Figure 11.Case CC has the lowest carrying charge cost rate due to the lower construction cost, but has significantly higher electricity cost over the other cases.When the total revenue requirement levelized cost rate is compared, Case CC is less than Case BC by 33 NT/h.Case MO has a total revenue requirement levelized cost rate slightly higher than Case BC, but has a lower electricity cost rate.In comparison, Case TE has the highest total revenue requirement levelized cost rate.The comparison of the levelized cost rate is shown in Figure 11.Case CC has the lowest carrying charge cost rate due to the lower construction cost, but has significantly higher electricity cost over the other cases.When the total revenue requirement levelized cost rate is compared, Case CC is less than Case BC by 33 NT/h.Case MO has a total revenue requirement levelized cost rate slightly higher than Case BC, but has a lower electricity cost rate.In comparison, Case TE has the highest total revenue requirement levelized cost rate.Figure 12 shows the percentage comparison of construction cost, total exergy destruction rate, total revenue requirement levelized cost rate and CO2 emission.Case BC is taken to be 100% in all of the items.The construction cost of Case CC is 95.7%, but is 99.24% in terms of TRRL C  .The result Figure 12 shows the percentage comparison of construction cost, total exergy destruction rate, total revenue requirement levelized cost rate and CO 2 emission.Case BC is taken to be 100% in all of the items.The construction cost of Case CC is 95.7%, but is 99.24% in terms of .C TRRL .The result shows that Case CC may not be a good selection.Case TE is the best selection in terms of reducing CO 2 emission and low exergy destruction.However, Case TE has .C TRRL 2.76% higher than that of Case BC.The comparison shows that Case TE is a good selection when reducing CO 2 emission is a prime concern.Case MO has .C TRRL almost as an equal percentage as for Case BC, but has lower exergy destruction and lower CO 2 emission.Case MO appears to be a superior selection when economics and second law efficiency are both a concern.

Discussion
The above results show that applying exergy and thermoeconomic analysis to the air-conditioning system design would be of practical importance.It is also noted that when the total revenue requirement levelized cost rate is evaluated, a lower construction cost may not result in

Discussion
The above results show that applying exergy and thermoeconomic analysis to the air-conditioning system design would be of practical importance.It is also noted that when the total revenue requirement levelized cost rate is evaluated, a lower construction cost may not result in good economics.Optimization of multiple objectives would provide a balanced consideration of both energy efficiency and investment return.Case MO has a total revenue requirement levelized cost rate comparable to Case BC, but performs better in reducing CO 2 emission and low exergy destruction.
The results obtained also show that both the system performance factor (SPF) and second law efficiency can be applied to the entire air-conditioning system.The results of exergy efficiency analysis as given in Table 7 show that system exergy efficiency is lower than 0.2 in all four cases.The results indicate high potential for further improvement in equipment efficiency.SPF is an effective indicator of the system performance.For Case TE, SPF equals about 3.0; this means one unit of electrical energy input would result in about three units of refrigeration effect in energy terms.

Conclusions
It has been shown that thermoeconomic and exergy analysis can be used to improve the energy performance and cost savings of the air-conditioning system of an underground train station.It is also shown that lower initial construction cost may have only a marginal benefit when the total revenue requirement levelized rate is evaluated.Optimization of thermodynamic efficiency would bring the benefits of a lower exergy destruction rate and lower energy use.The results also show that multi-objective optimization has the benefit of a lower total revenue requirement levelized rate, but performs well in reducing CO 2 emission and low exergy destruction.The annual system exergy efficiency obtained is lower than 0.2, which points to high potential in equipment efficiency improvement.A system performance factor is introduced to evaluate the efficiency of the entire air-conditioning system.In summary, this study shows that thermoeconomic and exergy analysis can be applied in an annual analysis, so as to achieve optimized hourly operation of an air-conditioning system in general and for an underground train station in particular.Moreover, it has been shown that a higher system performance factor (SPF) can be achieved along with lower annual CO 2 emission.

Figure 1 .
Figure 1.Station floor plan and zones served by a general and a 24-hour AC system.(a) The ground floor plan; (b) the underground U-1 floor plan; (c) the underground U-2 floor plan.

Figure 1 .
Figure 1.Station floor plan and zones served by a general and a 24-h AC system.(a) The ground floor plan; (b) the underground U-1 floor plan; (c) the underground U-2 floor plan.

Figure 2 .
Figure 2. The schematics of the 24-hour and the general air-conditioning systems.(a) The schematics of the 24-hour air-conditioning system; (b) the schematics of the general air-conditioning system.AHU, air handling unit; FC, fan coils.

Figure 2 .
Figure 2. The schematics of the 24-h and the general air-conditioning systems.(a) The schematics of the 24-h air-conditioning system; (b) the schematics of the general air-conditioning system.AHU, air handling unit; FC, fan coils.
Prediction of chiller COP refers to the modified Gordon-Ng universal model proposed by Jiang and Reddy [30].The model considers the refrigerant flow rate that may change the internal entropy production in the compressor.The independent variables of chiller COP are then the cooling load ratio .Q e { .Q epmaxq , evaporator outlet temperature T eo and condenser inlet water temperature T ci .The functional form of the model is shown in Equation (18): ): .C TRRL " .C TRRL ´.C TRRL,min .C TRRL,max ´.C TRRL,min (20) .I tot " .I tot ´.I tot,min .I tot,max ´.I tot,min ), .C TRRL,min and .C TRRL,max are the minimum and maximum values of .C TRRL in the Pareto frontier, similarly for .I tot,min and .I tot,max . .C TRRL = .C TRRL,min and .I tot = .I tot,min correspond to the limits of economic and thermodynamic optimization.When Equations (20) and (21) are separately used in single objective optimization, .C TRRL and .

Figure 3 .
Figure 3. Hourly electricity consumption of the underground train station in 2012.

Figure 4 .
Figure 4. Monthly electricity cost of the underground train station in 2012.

Figure 3 .
Figure 3. Hourly electricity consumption of the underground train station in 2012.

Figure 3 .
Figure 3. Hourly electricity consumption of the underground train station in 2012.

Figure 4 .
Figure 4. Monthly electricity cost of the underground train station in 2012.

Figure 4 .
Figure 4. Monthly electricity cost of the underground train station in 2012.

Figure 5 .
Figure 5. Daily cooling load of the underground train station under study.

Figure 6 .
Figure 6.Daily refrigerating exergy of the underground train station under study in 2012.

Figure 5 .
Figure 5. Daily cooling load of the underground train station under study.

Figure 6 .
Figure 6.Daily refrigerating exergy of the underground train station under study in 2012.

Figure 6 .
Figure 6.Daily refrigerating exergy of the underground train station under study in 2012.

Figure 7 .
Figure 7.The monthly average COP of the chillers.(a) The 24-hour air-conditioning system; (b) the general air-conditioning system.

Figure 7 .
Figure 7.The monthly average COP of the chillers.(a) The 24-h air-conditioning system; (b) the general air-conditioning system.
are shown in Table

Figure 8 .
Figure 8.The monthly system performance factor and second law efficiency.

C
levelization .TRRL and the normalized exergy destruction .I tot .The method of the Pareto optimal frontier [39] is applied to obtain the normalized .C TRRL and .I tot .The normalized .C TRRL and .I tot of the four cases are shown in Table

Figure 9
Figure 9 presents the normalized form of the Pareto optimal frontier in the multi-objective optimization (MO).In Figure 9, multi-objective optimization is at the lowest point of the root mean squares of .C TRRL and .I tot .For Case MO optimal .C TRRL is calculated to be about 0.27 and .I tot at about

Figure 10 .
Figure 10.Exergy destruction of the air-conditioning system.

Figure 10 .
Figure 10.Exergy destruction of the air-conditioning system.

Figure 10 .
Figure 10.Exergy destruction of the air-conditioning system.

Figure 11 .
Figure 11.Levelized costs rate for the four cases.

Figure 11 .
Figure 11.Levelized costs rate for the four cases.

Figure 12 .
Figure 12.Percentage comparison of the four cases.

Table 2 .
Operating range of the general air-conditioning system.
Daily cooling load of the underground train station under study.

Table 3 .
Energy consumption of the pumps for the 24-hour system.

Table 3 .
Energy consumption of the pumps for the 24-h system.

Table 4 .
Energy consumption of pumps for the general system.

Table 5 .
Annual energy use of the major components of the air-conditioning system.

Table 7 .
Energy exergy and thermoeconomic analysis of the air-conditioning system.