Open AccessArticle

Potential and Evolution of Compressed Air Energy Storage: Energy and Exergy Analyses

Young-Min Kim

^1,*,

Jang-Hee Lee

¹,

Seok-Joon Kim

¹ and

Daniel Favrat

Department of Environmental and Energy Systems, Korea Institute of Machinery and Materials, 171 Jang-dong, Yuseong-gu, Daejeon 305-343, Korea

Industrial Energy System Laboratory, Swiss Federal Institute of Technology Lausanne (EPFL), Station 9, 1015 Lausanne, Switzerland

Author to whom correspondence should be addressed.

Entropy 2012, 14(8), 1501-1521; https://doi.org/10.3390/e14081501

Submission received: 25 June 2012 / Revised: 8 August 2012 / Accepted: 8 August 2012 / Published: 10 August 2012

(This article belongs to the Special Issue Exergy: Analysis and Applications)

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Abstract

Energy storage systems are increasingly gaining importance with regard to their role in achieving load levelling, especially for matching intermittent sources of renewable energy with customer demand, as well as for storing excess nuclear or thermal power during the daily cycle. Compressed air energy storage (CAES), with its high reliability, economic feasibility, and low environmental impact, is a promising method for large-scale energy storage. Although there are only two large-scale CAES plants in existence, recently, a number of CAES projects have been initiated around the world, and some innovative concepts of CAES have been proposed. Existing CAES plants have some disadvantages such as energy loss due to dissipation of heat of compression, use of fossil fuels, and dependence on geological formations. This paper reviews the main drawbacks of the existing CAES systems and presents some innovative concepts of CAES, such as adiabatic CAES, isothermal CAES, micro-CAES combined with air-cycle heating and cooling, and constant-pressure CAES combined with pumped hydro storage that can address such problems and widen the scope of CAES applications, by energy and exergy analyses. These analyses greatly help us to understand the characteristics of each CAES system and compare different CAES systems.

Keywords:

compressed air energy storage (CAES); exergy; adiabatic CAES; isothermal CAES; air cycle heating and cooling

1. Introduction

Interest in energy storage is currently on the rise, especially for storage that matches intermittent renewable energy with customer demand, as well as for storage of excess nuclear or thermal power during a daily cycle [1]. In the case of pumped hydro storage, its dependence on specific geological formations and environmental concerns associated with it make new development difficult. As an alternative to pumped hydro storage, compressed air energy storage (CAES), with its high reliability, economic feasibility, and low environmental impact, is a promising method of energy storage [2,3]. The idea of storage plants based on compressed air is not new. In 1978, the first CAES plant of 290-MW capacity was built at Huntorf in Germany. In 1991, another 110-MW plant was built in McIntosh, AL, USA. Both plants are still in operation [4,5].

However, the existing CAES plants have some disadvantages such as their energy loss due to dissipation of heat of compression, use of fossil fuels, and dependence on geological formations. Therefore, some innovative concepts of CAES have been recently proposed [6]. In the case of conventional diabatic CAES plants, because the heat of compression needs to be dissipated to prevent deterioration of the cavern and pressure drop of the stored air in the cavern by heat loss, natural gas is used to heat the compressed air during the discharging process in order to avoid extremely low temperature of turbine. But adiabatic CAES stores the heat of compression and reuses it to heat the compressed air during the discharging process. The efficiencies of several adiabatic CAES configurations are analyzed with the help of an energy balance [7,8]. Isothermal CAES can also minimize the energy loss that occurs during the charging and discharging processes by minimizing the temperature difference of the air with the environment [4,9]. Micro-CAES with an air cycle heating and cooling system can use the heat of compression and the cooling effect of expanding air with good efficiency as a multipurpose system [10]. Constant-pressure CAES combined with pumped hydro storage can eliminate throttling loss in the existing CAES plants with varying air storage pressure and reduce the volume of air storage [11,12].

This paper reviews the main drawbacks of the existing CAES systems and the advantages of innovative CAES concepts such as adiabatic CAES, isothermal CAES, micro-CAES combined with air-cycle heating and cooling, and constant-pressure CAES combined with pumped hydro storage by energy and exergy analyses. These analyses greatly help us to understand the characteristics of each CAES system and to compare different CAES systems.

2. Understanding CAES System Using Exergy Concept

CAES is not a simple energy storage system, like other batteries. It can be viewed as a hybrid of an energy storage and a gas turbine power plant. Unlike conventional gas turbines, which consume about two-thirds of their input fuel to compress the air at the time of power generation, CAES precompresses the air, using low-cost electricity from the power grid at off-peak times, and utilizes it with some gas fuel to generate electricity when required [13]. The compressed air is stored in appropriate underground caverns or aboveground air vessels. The schematic of a modern CAES facility is presented in Figure 1 [9].

Figure 1. Conventional CAES system: Schematic of the McIntosh plant in AL, USA.

Since the CAES system can be considered to be a combination of an energy storage system and power plant, and all processes are accompanied by a significant amount of heat transfer, understanding the electrical energy flow in the CAES system is very difficult using the first law of thermodynamics, which deals with heat and work equally; therefore, we can use exergy flow, which is based on the second law of thermodynamics, to better understand the characteristics of the CAES system. Exergy can be defined as the maximum useful work possible that is accomplished during a process that brings the system into ion equilibrium with the environment [14]. Assuming that potential and kinematic energy effects are negligible and no chemical reaction occurs, the exergy of an air stream can be expressed as [15]:

{\dot{E}}_{a} = {\dot{M}}_{a} [h - h_{0} - T_{0} (s - s_{0})]

(1)

where h and s are specific enthalpy and entropy, respectively, and the subscript 0 indicates that the properties are taken at the environmental temperature and pressure (T₀ = 20 °C, P₀= 1 bar).

In the case of perfect gas flow:

h - h_{0} = c_{p} (T - T_{0})

(2)

s - s_{0} = c_{p} \ln \frac{T}{T_{0}} - r \ln \frac{P}{P_{0}}

(3)

where c_p is isobaric specific heat at average temperature and r is the specific gas constant.

The exergy in Equation (1) can be split into two parts—the mechanical part and the thermal part—as follows [14]:

{\dot{E}}_{a} = {\dot{E}}_{a (M)} + {\dot{E}}_{a (T)}

(4)

{\dot{E}}_{a (M)} = {\dot{M}}_{a} r T_{0} \ln \frac{P}{P_{0}}

(5)

{\dot{E}}_{a (T)} = {\dot{M}}_{a} c_{p} (T - T_{0} - T_{0} \ln \frac{T}{T_{0}})

(6)

Figure 2 shows the energy and exergy flow of the simplified CAES system. The processes of the CAES system are compression (1–2), cooling (2–3), charging or discharging (3–4), heating (4–5), expansion (5–6), and recuperation (6–7).

Although the compression work varies according to various compression processes, e.g., isothermal, adiabatic compression, and two-, three-, and four-stage compression with intercooling, the compressed air is cooled and stored at the same environmental temperature (T₀) and storage pressure (P_s). This means that only the mechanical exergy of the compressed air is stored in the air storage, and the thermal exergy of the compressed air is dissipated by the cooler or can be stored in the thermal energy storage and reused during the discharging process.

Figure 2. Energy and exergy flow of simplified CAES system.

The isentropic efficiencies of the compressor and expander, η_c,s and η_e,s , respectively, are expressed as:

η_{c, s} = \frac{W_{c, s}^{+}}{W_{c}^{+}} = \frac{h_{out, s} - h_{in}}{h_{out} - h_{in}}

(7)

η_{e, s} = \frac{W_{e, s}^{+}}{W_{e}^{+}} = \frac{h_{in} - h_{out}}{h_{in} - h_{out, s}}

(8)

where the subscript s denotes an isentropic compression/expansion process.

The efficiencies of motor and generator, η_m and η_g, are expressed as:

η_{m} = \frac{W_{c}^{+}}{E_{c}^{+}}

(9)

η_{g} = \frac{E_{e}^{-}}{W_{e}^{-}}

(10)

In order to study the energy and exergy analyses of different types of CAES systems, we adopted the following assumptions and elements of inlet data:

(a): Each compression and expansion is assumed to occur at a steady state with a steady flow and constant-pressure air storage, have negligible potential and kinematic energy effects, and exhibit no chemical reaction;
(b): For simplicity, the pressure drop in all heat exchangers is neglected;
(c): Air pressure in the storage cavern (or vessel) is assumed to remain constant at 5 MPa by adoption of constant-pressure air storage [10,11]. The designed pressure ratios of the compressor and expander are 50, with isentropic (adiabatic) efficiencies of 85%. The air-storage pressure is optimized by energy density and efficiency of the system and the general value of air-releasing pressure for CAES gas turbine is around 5 MPa [10,11];
(d): The efficiencies of the motor and generator are assumed to be 95%.

For multistage compression, each stage was assumed to consist of an adiabatic compression process, and each stage had the same pressure ratio; the compressed air was cooled to the ambient temperature by intercooling. Moreover, the total compression work and heat rejection are the sums of individual values of these quantities at all stages. For the discharging process, the recuperator can be used for recovering the heat of the expanded hot gas.

3. Characteristics of Different Types of CAES Systems

3.1. Conventional Diabatic CAES System (with Fuel)

In the case of conventional CAES plants such as the one shown in Figure 1, in order to increase the overall efficiency of the system, it is customary to perform multistage compression with intercooling and multistage expansion with reheating, and for the discharging process, the compressed air is generally heated using gas fuel. Figure 3 shows the energy and exergy flow of the diabatic CAES system for the production of 1-kWh output.

Figure 3. Energy and exergy flow of the conventional CAES system.

The CAES system in Figure 3 is based on the McIntosh plant, which has four-stage compression with intercooling and an exhaust gas temperature of 130 °C. The heat input is 1.22 kWh to produce 1 kWh electric output, and the inlet temperatures of high pressure (HP) turbine with the inlet pressure of 50 bar and low pressure (LP) turbine with the inlet pressure of 15 bar are 537 °C and 871 °C, respectively. The electric power is 2.26 times higher than the exergy of the compressed air by the thermal exergy added by using fuel. The thermal exergy of 0.77 kWh in Figure 3 is not chemical exergy but a total thermal exergy added in form of heat during the multistage expansion with reheating. In general, the energy efficiency of the CAES system can be calculated by adding the heat input by natural gas, Q, to the electric input as follows [13,16,17]:

η_{e e} \equiv \frac{E_{out}}{E_{in} + Q}

(11)

But, this value may not be considered a useful measure of electrical storage efficiency, because the heat input is not equivalent to the electric input. Rather, it may be seen as a mixed efficiency of the electrical storage efficiency and thermal efficiency of a power plant.

Therefore, the net electrical storage efficiency of a CAES system can be calculated by adding the amount of electric energy generated by natural gas (or other fuels) to the electric input of the CAES system as follows [13,16,17]:

η_{s e} \equiv \frac{E_{out}}{E_{in} + Q_{η_{p}}}

(12)

where Q_{η_p} is the electric energy that would be produced if the amount of fuel consumed by the CAES system were burned in another power station (Q is the lower caloric value of the fuel and η_p is the efficiency of the conventional power plant).

If the standard thermal efficiency of the power plant η_p = 0.4 [18] is assumed, the net electrical storage efficiency of the CAES system shown in Figure 3 is 89%. However, if the thermal efficiency of a conventional power plant, η_p = 0.5, is used as the standard, the net electrical storage efficiency of the CAES system is 81%. Therefore, the net electrical efficiency of the CAES system, defined in Equation (12), depends significantly on the value of η_p used. Further, when the heat is obtained from waste heat or solar power, the net electrical storage efficiency of a CAES system becomes more ambiguous. Figure 4 shows a new configuration of diabatic CAES configuration, one that uses a conventional gas turbine and the exhaust heat from the gas turbine to heat the compressed air before it reaches the expander, as a CAES bottoming cycle [19].

Figure 4. Configuration of CAES system as a bottoming cycle.

Therefore, in this paper, a new expression for the electrical storage efficiency of the CAES system, based on the exergy analysis, has been proposed. It is given as:

η_{s e} \equiv \frac{E_{out}}{E_{in} + E_{a (T)}}

(13)

whereE_a(T) is the thermal exergy of compressed air added by heat sources.

The new electrical storage efficiency of the CAES system in Figure 3 is 71%. Unlike the conventional gas turbine system, in the case of the CAES system, there is a very little exergy loss of exhaust gas. This advantage can compensate for the exergy loss of heat of compression. Although the heat of compression is dissipated in existing CAES plants, it is possible for this dissipated heat to be used for residential heating through cogeneration, which can contribute to improved energy efficiency. Moreover, although existing CAES plants use fossil fuel, waste heat and several other types of renewable energies such as solar, biomass, and biogas can be used as heat sources in the CAES system. SolarCAT Inc. has developed an energy storage technology using compressed air energy storage and concentrating solar power (CSP) design concepts. The company’s design replaces the CAES facility’s expander train with multiple expanders integrated with parabolic dish solar collectors, which reflect and concentrate incident sunlight onto their focal receivers to heat the compressed air fed to the collectors from storage [4].

3.2. Adiabatic CAES System

One of the drawbacks of existing CAES systems is the use of fuel. Adiabatic CAES uses no fuel to heat the compressed air for the expansion process, representing an emission-free, pure storage technology with high storage efficiency [4]. The basic idea of the adiabatic CAES concept is the use of heat storage as the central element of the plant, as shown in Figure 5 [4,20,21]. This implies that the heat needed to heat the compressed air for the expansion process is recovered from the compression and stored in a thermal energy storage (TES) unit to eliminate the need for a combustor [13].

Figure 5. Diagram of an adiabatic CAES system in single-stage configuration.

Figure 6 shows the energy and exergy flow of the adiabatic CAES system in single-stage configuration for the production of 1 kWh output.

If the air is compressed up to 50 bar adiabatically, the outlet air temperature of compressor is about 685 °C. The thermal exergy of the compressed air

{\dot{E}}_{a (T)}

is roughly equivalent to the mechanical exergy of the compressed air

{\dot{E}}_{a (M)}

. During the charging process, the heat is extracted from the compressed air and stored. When the grid demands electric power, the compressed air is heated using the thermal energy storage up to 622 °C and expanded through an air turbine. It was assumed that the efficiency of TES (the ratio of heat input to the compressed air to the heat output from the compressed air) is 90%. Then, the electrical storage efficiency of the adiabatic CAES system without any external thermal input is 68%. The adiabatic CAES can be considered a combination of CAES and TES, because a substantial portion of the exergy is stored in the form of thermal energy.

Figure 6. Energy and exergy flow of the adiabatic CAES system in single-stage configuration.

Adiabatic CAES technology was evaluated previously in the European research project. The resulting conceptual designs of the four main plant components (compressor, heat storage, cavern, and air turbine) helped to identify some key technical risks as well as a substantial need for further development efforts, particularly for the adiabatic compression and the heat storage device. The outlet temperature of the compressor is maintained above 600 °C, and the corresponding compression heat is stored in the TES consisting of an arrangement of solid materials, typically ceramic bricks or natural stones [4,21].

Another configuration of adiabatic CAES is shown in Figure 7, using cold and hot oil as the TES [7,8]. During charging process, the oil is flowing from a cold tank to a hot tank to intercool the compressed air. Inversely, during discharging process, the oil is flowing from the hot tank to the cold tank to heat the compressed air for power production. The design is based on using standard, industry-proven equipment components.

Figure 7. Diagram of an adiabatic CAES system in two-stage configuration.

Figure 8 shows the energy and exergy flow of the adiabatic CAES system in two-stage configuration for the production of 1 kWh output.

Figure 8. Energy and exergy flow of the adiabatic CAES system in two-stage configuration.

If the air is compressed up to 50 bar in two stages, the outlet air temperature of compressor is about 275 °C. The thermal exergy of the compressed air,

{\dot{E}}_{a (T)}

, is less than half of the mechanical exergy of the compressed air,

{\dot{E}}_{a (M)}

. During the charge period, the heat is extracted from the compressed air and stored by the flowing oil. When the grid demands electric power, the compressed air is heated using thermal energy storage up to 250 °C and expanded through an air turbine. The efficiency of TES is assumed to be 90%, as in the previous adiabatic CAES system in single-stage configuration. Then, the electrical storage efficiency of the adiabatic CAES system without any external thermal input is 67%. This adiabatic CAES configuration needs greater air storage than does the prior one, because its TES exergy storage is much smaller than the prior one, due to the lower temperature of TES.

3.3. Isothermal CAES System

Isothermal CAES is an alternative CAES system which eliminates the need for fuel and high temperature thermal energy storage. Isothermal CAES can minimize the compression work and maximize the expansion work done through isothermal compression/expansion by means of effective heat transfer with the vessel’s surroundings, which involves slow gas pressure change by liquid piston [4,9]. The CAES systems of SustainX Inc. and Enairys Powertech Ltd. use hydraulic pumps to isothermally compress air at rates that allow the high-pressure air to exchange heat with its surroundings, as shown in Figure 9. During isothermal expansion, the gas is able to do more work by absorbing heat from its surroundings. The expanding air in the isothermal CAES system drives a hydraulic motor, which in turn drives an electric generator. The use of hydraulic pumps and motors enables precise compression and expansion of air, heat transfer with the surroundings, and a high level of thermal and overall system efficiency [4,9].

Figure 9. Function diagram of an isothermal CAES system (Source: SustainX Inc., Seabrook, NH, USA).

Figure 10 shows the energy and exergy flow of the isothermal CAES system for the production of 1 kWh output. The air is compressed up to 50 bar isothermally and stored; then, the compressed air is expanded isothermally. The ideal isothermal compression and expansion work,

W_{c, t}^{+}

and

W_{e, t}^{-}

, respectively, can be obtained as follows:

W_{c, t}^{+} = M_{a} (q_{c, t}^{-} + Δ h) = M_{a} (- T_{c} Δ s + Δ h)

(14)

W_{e, t}^{-} = M_{a} (q_{e, t}^{+} - Δ h) = M_{a} (T_{e} Δ s - Δ h)

(15)

where the working fluid is assumed to be real gas then Δh is very small but not equal to zero.

Figure 10. Energy and exergy flow of the isothermal CAES system.

The isothermal efficiencies of compression and expansion, η_c,t and η_e,t, respectively, are expressed as:

η_{c, t} = \frac{W_{c, t}^{+}}{W_{c}^{+}}

(16)

η_{e, t} = \frac{W_{e}^{-}}{W_{e, t}^{-}}

(17)

where

W_{c}^{+}

and

W_{e}^{-}

are the actual compression work and expansion work considering a loss of mechanical work by internal dissipation and a small temperature deviations from isothermal process.

It was assumed that the isothermal efficiencies of compression and expansion were 90%, considering the high efficiency of the hydraulic pump/motor and the effective heat transfer with its surroundings; the isentropic effciencies of hydraulic water pump/motor are 92%~94% [9] and it was repoted that the temperature deviation during the expansion (or compression) process from 1 bar to 200 bar is less than 12 °C by water injection, which means that the work by integrating the pressure-volume curve is 96% of isothermal work (source: SustainX Inc.).

Although there is much heat transfer between the system and its surroundings for the compression and expansion processes, the thermal exergy of the air

{\dot{E}}_{a (T)}

is nearly equal to zero, because the temperature change of the air is very small. Although the isothermal CAES system requires about twice the volume of air storage in comparison with the conventional (diabatic) and adiabatic CAES systems, because no thermal exergy is added to the compressed air for the discharging process, the use of high pressure (from 1 bar to 200 bar) reduces the storage volume required. The electrical storage efficiency of the isothermal CAES system without external thermal input is 73%.

3.4. Trigeneration Micro-CAES System

Large-scale CAES is very dependent on appropriate geological formations for air storage. Micro-CAES with subsurface or aboveground pressure vessels is a more adaptable solution, especially for distributed generation [22,23,24]. Also compressed air is a commonly used utility across most manufacturing and processing industries as its production and handling are safe and easy [25]. Micro-CAES systems can be used as a multipurpose system, as a combination of energy storage and air cycle heating and cooling. In general, air cycle refrigeration consists of one or more compressors (fan), turbines (expanders), and heat exchangers; the setup is very similar to the CAES system except for the air storage vessels. Air cycle heating and cooling has many advantages, including high reliability, ease of maintenance, flexibility of temperature, and heating and cooling capacities. In addition, it employs a natural refrigerant, which is environmentally benign [26,27,28,29]. The air cycle approach is one of the most promising long-term alternatives for refrigeration machines, air conditioners, and heat pumps [26]. Air cycle is widely used in industrial freezing with a very low temperature (below −50 °C) and transport refrigeration. In the case of conventional refrigeration and air conditioning, the air cycle approach suffers from low energy efficiency and so is not competitive with vapor compression cycles [27]. But, air cycles have been studied for HVAC in office buildings within the framework of European research projects, since they have advantages in applications that require both heating and cooling [26,29] and because of the potential of highly efficient turbo machinery that is used [27,28].

The micro-CAES system combined with air cycle heating and cooling could be a very good solution because it would then be possible to improve the energy efficiency and economics of the system as a multipurpose system. Transportable CAES was proposed as a solution to provide power and energy for desalination of brackish water or seawater for an island by utilizing the superchilled air as a by-product for the freeze-crystallizing process [30]. A new CAES refrigeration system was proposed for electrical power load shifting—one that employs a combination of an air cycle refrigeration cycle and a vapor compression cycle, in which the cooling effect of expanding air is used and the expansion power is used to drive a compressor of the vapor compression cycle [31]. This paper focuses on a micro-CAES system for energy storage and air cycle heating and cooling for HVAC of a building. Because the pressure ratio of CAES is much higher than that of conventional air cycle refrigeration to reduce the volume of air storage, multiple-stage compression and expansion is needed to achieve high efficiency for the system; this is effected by matching the temperature of compressed and expanded air to the required temperature of heating and cooling load. Otherwise, quasi-isothermal compression and expansion by liquid injection can be used for a high efficiency micro-CAES and air cycle heating and cooling system [10]. To achieve quasi-isothermal compression and expansion, a large amount of atomized water is injected during both processes, as shown Figure 11.

Figure 11. Trigeneration micro-CAES system: (1) mixer, (2) compressor, (3) separator, (4) hydraulic motor, (5), (6), and (7) heat exchanger, (8) high pressure vessel, (9) mixer, (10) expander, (11) separator, (13) pump, and (12), (14), and (15) heat exchanger [10].

The concept is the same as that of a liquid-flooded compressor and expander in an Ericsson cycle cooler proposed by Hugenroth et al. [32]. Water (or liquid) is discharged together with compressed air; then it is separated, cooled, and recirculated. Compressed air is cooled to the ambient temperature by water circulation through a cooler, and it is then stored in vessels. Hot water separated after the compression and hot water from the cooler can be used to satisfy the heating load. To achieve quasi-isothermal expansion, as in the compression process, liquid can be injected into the expander, separated, used to supply the cooling load, and pressurized by a pump for injection. In the course of the analyses, additional compression work owing to liquid during the compression process or pumping work for liquid injection during the expansion process was neglected, because either kind of work supplies only a small percent (2%–3%) of the work of gas, and the additional work input owing to liquid can be recovered by hydraulic motor during the compression process or by expander during the expansion process.

The quasi-isothermal compression or expansion process can be modeled as a polytropic process (Pvⁿ = const). The temperature change of gas during the polytropic process can be obtained as follows:

\frac{T_{o u t}}{T_{i n}} = {[\frac{P_{o u t}}{P_{i n}}]}^{\frac{n - 1}{n}}

(18)

In the case of quasi-isothermal compression or expansion, it is possible to match the temperature after compression to the heating temperature required or the temperature after expansion to the cooling temperature required by controlling the mass flow rate of injected liquid, i.e., by changing the polytropic index n.

The ideal compression and expansion work can be obtained as follows:

w_{c, i d e a l}^{+} = \frac{r n}{n - 1} (T_{o u t} - T_{i n})

(19)

w_{e, i d e a l}^{-} = \frac{r n}{n - 1} (T_{i n} - T_{o u t})

(20)

Actual compression and expansion work can be obtained using an isentropic efficiency defined, respectively, as:

η_{c} \equiv \frac{w_{c, i d e a l}^{+}}{w_{c}^{+}}

(21)

η_{e} \equiv \frac{w_{e}^{-}}{w_{e, i d e a l}^{-}}

(22)

Heat transfer from the gas to the liquid during the compression process and from the liquid to the gas during the expansion process can be obtained as follows:

Q_{c}^{-} = M_{a} ⌊ w_{c}^{+} - (h_{o u t} - h_{i n}) ⌋

(23)

Q_{e}^{+} = M_{a} ⌊ w_{e}^{-} - (h_{i n} - h_{o u t}) ⌋

(24)

Figure 12 shows the energy and exergy flow of the trigeneration micro-CAES system for the production of 1 kWh output. The case of one stage of quasi-isothermal compression with (n = 1.05) and expansion (n = 1.025) with liquid injection was considered. It was assumed that the isentropic efficiencies of the compressor and expander are 85%, the efficiencies of the motor and generator are 95%, and we can use 90% of the heat of compression and cooling effect of expanding air. The electrical storage efficiency of the micro-CAES system without any external thermal input is 57%. In addition, hot and cold water accompanied by a significant amount of heat transfer are available, in which the COP of the heat pump (COP_HP = Q_hot/E_net) is equivalent to 2.0 and the COP of refrigeration (COP_R = Q_cold/E_net) is equivalent to 1.3. Considering the thermal exergy of the hot and cold water, the second law efficiency of the trigeneration micro-CAES system (η_II) is 68%.

Figure 12. Energy and exergy flow of trigeneration micro-CAES system.

To obtain increased electric power without use of the cooling effect, a heater (or combustor) can be used to heat the compressed air. Figure 13 shows the energy and exergy flow of the micro-CAES system with fuel, as in the conventional CAES system.

Figure 13. Energy and exergy flow of micro-CAES system with the fuel.

3.5. Constant-Pressure CAES System Combined with Pumped Hydro Storage

Conventional CAES systems are most commonly operated under constant volume conditions with a fixed, rigid reservoir operating over an appropriate pressure range [15,20]. These varying pressure ratios can degrade the efficiencies of compression and expansion due to deviation from design points. Existing CAES plants were designed to throttle the cavern air to a designed pressure despite the throttling loss. The exergy loss of compressed air by throttling is about 5%–8% in existing CAES systems [11]. Although it is possible to increase the storage volume to reduce the operating pressure range, doing so results in low energy density and high construction costs. Therefore, in order to resolve such problems, a new constant-pressure CAES system combined with pumped hydro storage was proposed [11,12]. The system combines constant-pressure air storage and hydraulic energy storage, as shown in Figure 14. During the charging process, the water in an air storage vessel (left) is transferred to a hydraulic accumulator (right) by a pump to maintain a constant pressure of air storage, consuming power. During the discharging process, the water in the hydraulic accumulator is returned to the air storage vessel through a water turbine to maintain a constant pressure of air storage, producing power.

The compression/expansion process of the enclosed air in the right tank is assumed to be a isothermal process (PV = const) that results from sufficient heat transfer with the environment considering that the pressure ratio of the sealed air, P₂/P₁, is low and the compression/expansion process is a very slow process over the charging/discharging process. The exergy of compressed air part (E_a) and hydraulic part (E_h) can be expressed, respectively, as [11]:

E_{a} = P_{s} (V_{1} - V_{2}) \ln \frac{P_{s}}{P_{0}}

(25)

E_{h} = P_{1} V_{1} \ln \frac{V_{1}}{V_{2}} - P_{s} (V_{1} - V_{2})

(26)

where V₁ and V₂ are the volumes of air in the hydraulic accumulator at the start and end of the charging process, respectively; P₁ is the pressure of air in the hydraulic accumulator at the start of charging process; and P₀ and P_S are ambient pressure and constant pressure of air storage, respectively.

Figure 14. Constant-pressure CAES system combined with pumped hydro storage (PHS) [11].

This concept can be applied to both small-scale CAES using manmade air vessels and large-scale CAES using salt caverns or lined rock caverns. In the case of small-scale CAES systems, a commercial hydraulic motor/pump can be used because the machines exhibit exceptional energy conversion performances and are easily reversible (can operate as motor and as pump) [9]. In the case of micro-CAES, it is very important to increase the energy density and reduce the volume of the storage tank at a feasible cost, because of the high cost and space of the storage tank. Recently, a CAES system of the Electric Power Research Institute Inc. with aboveground air vessels throttled the incoming air to 55 bar (operating between 55 bar and 103 bar), despite the big throttle loss. The constant-pressure CAES system combined with pumped hydro storage can be applied in the micro-CAES system with a manmade air vessel to increase the energy density and efficiency of the system.

If it is assumed that the compression volume ratio (V₁/V₂) is 4 and the constant pressure of air storage (P_S) and initial pressure of air in the hydraulic accumulator (P₁) are about 50 bar, then approximately 80% exergy is stored in the compressed air part and 20% exergy is stored in the hydraulic part. Figure 15 and Figure 16 show the energy and exergy flow of the previous micro-CAES system applied by the constant-pressure CAES system combined with pumped hydro storage. The exergy efficiencies of the water pump and water turbine were assumed to be 0.9.

Figure 15. Energy and exergy flow of constant-pressure trigeneration micro-CAES system.

Figure 16. Energy and exergy flow of constant-pressure micro-CAES system with the fuel.

In the case of a large-scale CAES system, it is very important to build storage caverns economically using natural geological formations such as salt domes or hard rocks. The constant-pressure CAES system combined with pumped hydro storage can be considered a combination of CAES and a new type of underground pumped storage. Underground pumped storage has been studied as an alternative to conventional aboveground pumped storage, requiring available topography and consideration of environmental impact. The underground pumped storage can be constructed by setting the upper reservoir aboveground and the lower reservoir and powerhouse underground [33,34]. In the case of conventional underground pumped storage, the unit cost of the excavation increases with depth, a deep borehole was drilled into the rock strata below the mine where the powerhouse would be located. Also, the excavation for the power facilities and installations would add a major cost to the project and therefore significantly increase the construction cost [34].

The advantages of the constant-pressure CAES system combined with pumped hydro storage are that it is not dependent on depth; the powerhouse can be installed aboveground and there is no need of an upper reservoir aboveground, as shown in Figure 17. Hydraulic energy storage in the system has many advantages over the conventional CAES system, including quick start-up, the ability to provide “spinning reserve,” and voltage and frequency regulation to stabilize the associated power grid [35,36].

Figure 17. Constant-pressure CAES system combined with PHS (aboveground power house).

Table 1. Energy and exergy analyses of different types of CAES systems [units:

E_{c}^{+}

Q_{c}^{-}

E_{a (T)}^{-}

, E_a(M),

Q_{e}^{+}

E_{a (T)}^{+}

E_{e}^{-}

(kWh); T_c, T_e (°C); V_a (m³)].

**Table 1.** Energy and exergy analyses of different types of CAES systems [units: $E_{c}^{+}$ , $Q_{c}^{-}$ , $E_{a (T)}^{-}$ , E_a(M), $Q_{e}^{+}$ , $E_{a (T)}^{+}$ , $E_{e}^{-}$ (kWh); T_c, T_e (°C); V_a (m³)].
Type	Charging			Storage		Discharging			η_se
Type	$E_{c}^{+}$	$Q_{c}^{-}$ (T_c)	$E_{a (T)}^{-}$	E_a(M)	V_a	$Q_{e}^{+}$ (T_e)	$E_{a (T)}^{+}$	$E_{e}^{-}$	η_se
Diabatic	0.63	0.62 (115)	0.09	0.44	0.081	1.22 (537,871)	0.77	1.00	0.71
Adiabatic 1-stage	1.48	1.43 (685)	0.69	0.65	0.119	1.28 (622)	0.59	1.00	0.68
Adiabatic 2-stages	1.50	1.45 (275)	0.41	0.90	0.164	1.20 (250)	0.34	1.00	0.67
Isothermal	1.37	1.34 (20)	0.00	1.17	0.213	1.09 (20)	0.00	1.00	0.73
Trigen Micro	1.77	1.55 (80)	0.15	1.29	0.236	0.99 (−6)	0.05	1.00	0.57
Trigen Micro	COP_HP = 2.0, COP_R = 1.3, η_II = 0.68
Micro with fuel	0.60	0.53 (20)	0.05	0.44	0.081	1.22 (537,871)	0.77	1.00	0.73

4. Conclusions

Exergy analysis was used to provide an understanding of the drawbacks of the current CAES method and the advantages of innovative CAES concepts such as adiabatic CAES, isothermal CAES, micro-CAES combined with air-cycle heating and cooling, and constant-pressure CAES combined with pumped hydro storage. The results of exergy analyses of different types of CAES systems are summarized in Table 1.

Although existing CAES plants use natural gas as fuel, waste heat and renewable energies such as solar, biomass, and biogas can be used as heat sources for the CAES system. Adiabatic CAES traps the heat of compression and reuses it for expansion; hence, it can be considered a combination of CAES and thermal energy storage (TES), because a substantial portion of the exergy is stored in the form of thermal energy. Isothermal CAES can minimize the compression work and maximize the expansion work done through isothermal compression/expansion with effective heat transfer with the system’s surroundings and without the use of fuel or high temperature thermal storage. The micro-CAES system combined with air cycle heating and cooling can be a very effective system for distributed power networks, because it provides energy storage, generates electric power using various heat sources, and incorporates an air cycle heating and cooling system. Constant-pressure CAES combined with pumped hydro storage can reduce the throttling loss during expansion in the existing CAES plants; this method requires a small cavern (or vessel) whose storage volume is only half of that required for existing CAES plants.

The existing CAES systems have a few drawbacks, but these can be addressed by employing some innovative CAES concepts. Compressed air energy storage can be combined with power generation using various heat sources, thermal energy storage, air cycle heating and cooling, and pumped hydro storage; such combinations have great synergistic effects.

Nomenclature

c	specific heat (kJ/K)
COP	coefficient of performance
E	exergy (kJ)
E+	exergy to the system (kW)
E−	exergy from the system (kW)
h	specific enthalpy (kJ/kg)
M	mass (kg)
n	polytropic exponent
P	pressure (kPa)
Q	heat (kJ)
q	specific heat (kJ/kg)
r	specific gas constant (kJ/kgK)
s	specific entropy (kJ/kgK)
T	temperature (K)
V	volume (m³)
v	specific volume (m³/kg)
W	work (kJ)
w	specific work (kJ/kg)

Greek Symbols

η	efficiency (dimensionless)
ρ	density (kg/m³)

Subscripts

a	air
ac	after compression
ae	after expansion
a(M)	mechanical exergy of air
a(T)	thermal exergy of air
c	compression
cold	cold water
e	expansion
ee	energy efficiency
exh	exhaust gas
g	generator
h	hydraulic part
hot	hot water
HP	heat pump
ideal	ideal process
in	input to the system
m	motor
net	net (output minus input)
out	output from the system
p	conventional power plant
R	refrigeration
S	storage
s	isentropic
se	electrical storage efficiency
t	isothermal
II	second law efficiency
0	dead state (ambient)
1	start state of charging process
2	end state of charging process

Superscripts

+	input
−	output

References

Lund, H.; Salgi, G.; Elmegaard, B.; Andersen, A.N. Optimal operation strategies of compressed air energy storage (CAES) on electricity spot markets with fluctuating prices. Appl. Therm. Eng. 2009, 29, 893–904. [Google Scholar] [CrossRef]
Cavallo, A. Controllable and affordable utility-scale electricity from intermittent wind resources and compressed air energy storage (CAES). Energy 2009, 32, 120–127. [Google Scholar] [CrossRef]
Lund, H.; Salgi, G. The role of compressed air energy storage (CAES) in future sustainable energy systems. Energ. Convers. Manage. 2009, 50, 1172–1179. [Google Scholar] [CrossRef]
Eckard, R. CAES Compressed Air Energy Storage Worldwide; SBI Energy: Rockville, MD, USA, 2010. [Google Scholar]
Crotogino, F.; Mohmeyer, K.-U.; Scharf, R. Huntorf CAES: More than 20 Years of Successful Operation. In Proceedings of SMRI Spring Meeting, Orlando, FL, USA, 15–18 April, 2001.
Kim, Y.M.; Shin, D.G.; Kim, C.G. Potential and Evolution of Compressed Air Energy Storage for Future Power Networks. In World Engineers’ Convention, Geneva, Switzerland, 4–9 September, 2011.
Grazzini, G.; Milazzo, A. A thermodynamic analysis of multistage adiabatic CAES. Proc. IEEE 2012, 100, 461–472. [Google Scholar] [CrossRef]
Hartmann, N.; Vohringer, O.; Kruck, C.; Eltrop, L. Simulation and analysis of different adiabatic compressed air energy storage plant configurations. Appl. Energ. 2012, 93, 541–548. [Google Scholar] [CrossRef]
Lemofouet, S. Investigation and Optimization of Hybrid Electricity Storage Systems Based on Compressed Air and Supercapacitors. Ph.D. Thesis, EPFL, Lausanne, Switzerland, 2006. [Google Scholar]
Kim, Y.M.; Favrat, D. Energy and exergy analysis of a micro compressed air energy storage and air cycle heating and cooling system. Energy 2010, 35, 213–220. [Google Scholar] [CrossRef]
Kim, Y.M.; Shin, D.G.; Favrat, D. Operating characteristics of constant-pressure compressed air energy storage (CAES) system combined with pumped hydro storage based on energy and exergy analysis. Energy 2011, 36, 6220–6233. [Google Scholar] [CrossRef]
Kim, Y.M.; Favrat, D.; Shin, D.G.; Cho, K.B. Compressed-Air-Storing Electricity Generating System and Electricity Generating Method Using the Same. U.S. Patent 7,663,255, 16 August 2007. [Google Scholar]
Inage, S.I. Prospects for Large-Scale Energy Storage in Decarbonized Power Grids; International energy agency working paper series; OECD/IEA, International Energy Agency (IEA): Paris, France, 2009. [Google Scholar]
Tsatsaronis, G. Definition and nomenclature in exergy analysis and exergoeconomics. Energy 2007, 32, 249–253. [Google Scholar] [CrossRef]
Borel, L.; Favrat, D. Thermodynamics and Energy Systems Analysis; Presses Polytechniques Universitaires Romandes: Lausanne, Switzerland, 2010; pp. 399–490. [Google Scholar]
Succar, S.; Williams, R.H. Compressed Air Energy Storage: Theory, Resources, and Applications for Wind Power. Princeton Environmental Institute Report, 8 April 2008. Available online: http://www.princeton.edu/pei/energy/publications/texts/SuccarWilliams_PEI_CAES_2008April8.pdf (accessed on 8 August, 2012).
Elmegaard, B.; Brix, W. Efficiency of Compressed Air Energy Storage. In International Conference on Efficiency, Cost, Optimization, Simulation and Environmental Impact of Energy Systems, Novi Sad, Serbia, 4–7 July, 2011.
Kondoh, J.; Ishii, I.; Yamaguchi, H.; Murata, A.; Ontai, K.; Sakuta, K. Electrical energy storage systems for energy networks. Energ. Convers. Manage. 2000, 41, 1863–1874. [Google Scholar] [CrossRef]
Nakhamkin, M.; Chiruvolu, M.; Daniel, C. Available Compressed Air Energy Storage (CAES) Plant Concepts. Available online: http://espcinc.com/library/PowerGen_2007_paper.pdf (accessed on 8 August, 2012).
Ter-Gazarian, A. Energy Storage for Power Systems; The Institution of Engineering and Technology: London, UK, 2008. [Google Scholar]
Bullough, C.; Gatzen, C.; Jakiel, C.; Koller, M.; Nowi, A.; Zunft, S. Advanced Adiabatic Compressed Air Energy Storage for the Integration of Wind Energy. In European Wind Energy Conference EWEC 2004, London, UK, 2004.
Swanbarton Limited. Status of Electrical Energy Storage Systems; DTI Report No. 04/1878; Department of Trade and Industry (DTI): London, UK, 2004. [Google Scholar]
Denholm, P.; Kulcinski, G.L. Life cycle energy requirements and greenhouse gas emissions from large-scale energy storage systems. Energ. Convers. Manage. 2004, 45, 2153–2172. [Google Scholar] [CrossRef]
TENI Services Limited. An Appraisal of New and Renewable Generation Technologies as Transmission Upgrade Alternatives; NZ Electricity Commission Report P5NZ01; New Zealand Electricity Commission: Wellington, New Zealand, 2005. [Google Scholar]
Bahadori, A. Prediction of compressed air transport properties at elevated pressures and high temperatures using simple method. Appl. Energ. 2011, 88, 1434–1440. [Google Scholar] [CrossRef]
Verschoor, M.J.E. (Ed.) Guidelines for the Application and Design of Air Cycle Systems for Heating, Ventilating and Air Conditioning in Buildings; TNOMEP: Apeldoorn, The Netherlands, 2001.
Shengjun, L.; Zhenying, Z.; Lili, T. Thermodynamics analysis of the actual air cycle refrigeration system. Syst. Eng. Proc. 2011, 1, 112–116. [Google Scholar] [CrossRef]
Foster, A.M.; Brown, T.; Gigiel, A.J.; Alford, A.; Evans, J.A. Air cycle combined heating and cooling for the food industry. Int. J. Refrig. 2011, 34, 1296–1304. [Google Scholar] [CrossRef]
Spence, S.W.T.; Doran, W.J.; Artt, D.W.; McCullough, G. Performance analysis of a feasible air-cycle refrigeration system for road transport. Int. J. Refrig. 2005, 28, 381–382. [Google Scholar] [CrossRef]
Enis, B.; Lieberman, P.; Rubin, I.; Linden, S. Wind Turbine Generator and Compressed Air Energy Storage System for Production of Electric Power and Co-Generation for Chilled Air for Desalination. In International Conference on Efficiency, Cost, Optimization, Simulation and Environmental Impact of Energy Systems, Padova, Italy, 25–28 June, 2007.
Wang, S.; Chen, G.; Fang, M.; Wang, Q. A new compressed air energy storage refrigeration system. Energ. Convers. Manage. 2006, 47, 3408–3416. [Google Scholar] [CrossRef]
Hugenroth, J.; Braun, J.; Groll, E.; King, G. Liquid-Flooded Ericsson Cycle Cooler: Part 1—Thermodynamic Analysis. In International Refrigeration and Air Conditioning Conference at Purdue, West Lafayette, IN, 2006; p. R168.
Wong, I.H. An underground pumped storage scheme in the Bukit Timah granite of Singapore. Tunn. Undergr. Space Technol. 1996, 11, 485–489. [Google Scholar] [CrossRef]
Uddin, N.; Asce, M. Preliminary design of an underground reservoir for pumped storage. Geotechnic. Geologic. Eng. 2003, 21, 331–355. [Google Scholar] [CrossRef]
UCC Sustainable Energy Research Group. Study of Electricity Storage Technologies and Their Potential to Address Wind Energy Intermittency in Ireland; University College Cork Final Report RE/HC/103/001; Univerity College Cork (UCC): Cork, Ireland, 2004. [Google Scholar]
Cole, S.; van Hertem, D.; Meeus, L.; Belmans, R. SWOT Analysis of Utility Side Energy Storage Technologies. In Proceedings of the 5th WSEAS/IASME International Conference on Electric Power Systems, High Voltages, Electric Machines, Tenerife, Spain, 16–18 December, 2005; pp. 446–451.

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Kim, Y.-M.; Lee, J.-H.; Kim, S.-J.; Favrat, D. Potential and Evolution of Compressed Air Energy Storage: Energy and Exergy Analyses. Entropy 2012, 14, 1501-1521. https://doi.org/10.3390/e14081501

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Kim Y-M, Lee J-H, Kim S-J, Favrat D. Potential and Evolution of Compressed Air Energy Storage: Energy and Exergy Analyses. Entropy. 2012; 14(8):1501-1521. https://doi.org/10.3390/e14081501

Chicago/Turabian Style

Kim, Young-Min, Jang-Hee Lee, Seok-Joon Kim, and Daniel Favrat. 2012. "Potential and Evolution of Compressed Air Energy Storage: Energy and Exergy Analyses" Entropy 14, no. 8: 1501-1521. https://doi.org/10.3390/e14081501

APA Style

Kim, Y. -M., Lee, J. -H., Kim, S. -J., & Favrat, D. (2012). Potential and Evolution of Compressed Air Energy Storage: Energy and Exergy Analyses. Entropy, 14(8), 1501-1521. https://doi.org/10.3390/e14081501

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