25, American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc. (www.ashrae.org). Reprinted by permission from ASHRAE Journal, (Vol. 47, No. 9, September 25). This article may not be copied nor distributed in either paper or digital form without ASHRAE s permission. Solar Refrigeration By Sanford A. Klein, Ph.D., Fellow ASHRAE, and Douglas T. Reindl, Ph.D., Member ASHRAE Refrigeration systems that use environment-friendly refrigerants provide a sustainability advantage when compared to other refrigerant selections. However, the energy use associated with refrigeration system operation and the environmental impacts associated with its generation and distribution often outweigh the choice of refrigerant. To minimize environmental impacts associated with refrigeration system operation, it is reasonable to evaluate the prospects of a clean source of energy. From a sustainability perspective, directly using solar as a primary energy source is attractive because of its universal availability, low environmental impact, and low or no ongoing fuel cost. Research has demonstrated that solar energy is an ideal source for lowtemperature heating applications such as space and domestic hot water heating. Solar heating applications are intuitive since, when solar energy is absorbed on a surface, the surface temperature rises, providing a heating potential. The use of solar energy to provide refrigeration is less intuitive. In this article, we review three approaches that use solar energy to provide refrigeration at temperatures below C (32 F). In addition to reviewing the potential technologies, we compare their operating characteristics. We conclude that only one of the three technologies, About the Authors Sanford A. Klein, Ph.D., and Douglas T. Reindl, Ph.D., are professors at the Solar Energy Laboratory and Industrial Refrigeration Consortium, University of Wisconsin-Madison, Madison, Wis. S 2 6 B u i l d i n g f o r t h e F u t u r e A S u p p l e m e n t t o A S H R A E J o u r n a l S e p t e m b e r 2 5
Research has demonstrated that solar energy is an ideal source for low-temperature heating applications such as space and domestic hot water heating. photovoltaic-based vapor compression, is presently a viable solar refrigeration technology. Vapor Compression Refrigeration Prior to discussing how solar energy could potentially provide refrigeration, it is appropriate to review the basic principles of operation for vapor compression refrigeration cycles that form the foundation for nearly all conventional refrigeration. A schematic of the vapor compression cycle is shown in Figure 1a and a corresponding enthalpy-pressure diagram for the refrigerant is shown in Figure 1b. In the vapor compression cycle, cooling is provided in the evaporator as low temperature refrigerant entering the evaporator as a mixture of liquid and vapor at State 4 is vaporized by thermal input from the load. The remaining equipment in the system reclaims the refrigerant and restores it to a condition in which it can be used again to provide cooling. The vapor exiting the evaporator at State 1 in a saturated (1a) or slightly superheated (1b) condition enters a compressor that raises the pressure and, consequently, the temperature of the refrigerant. The high pressure hot refrigerant at State 2 enters a condenser heat exchanger that uses ambient air or water to cool the refrigerant to its saturation temperature prior to fully condensing to a liquid at State 3. The high-pressure liquid is then throttled to a lower pressure, which causes some of the refrigerant to vaporize as its temperature is reduced. The low temperature liquid that remains is available to produce useful refrigeration. The major energy input to a vapor compression refrigeration system is the mechanical power needed to drive the compressor. The minimum compressor power is given in Equation 1. The compressor power requirement is substantial because the specific volume of the refrigerant vapor, v, is large. Additional power is needed to operate the fans or pumps to move the external fluids. (1) The figure of merit for a vapor compression refrigeration system is its coefficient of performance (COP) defined as the ratio of the cooling capacity to the total electrical power required. The COP for a system providing refrigeration at 1 C (14 F) while rejecting heat to a temperature at 3 C (86 F) is approximately 3. The system COP diminishes from that level when the electrical power required for moving the external fluids is accounted for in the coefficient of performance. Two of the solar refrigeration systems considered here rely on the vapor compression refrigeration cycle in some form. The third solar refrigeration system uses thermal energy as the primary input to the cycle. Open cycle systems that use water as the refrigerant, such as the solar desiccant cycle, could be used to provide cooling at temperatures above freezing, but these alternatives are not considered here. Photovoltaic Operated Refrigeration Cycle Photovoltaics (PV) involve the direct conversion of solar radiation to direct current (dc) electricity using semiconducting materials. In concept, the operation of a PV-powered solar refrigeration cycle is simple. Solar photovoltaic panels produce dc electrical power that can be used to operate a dc motor, which is coupled to the compressor of a vapor compression refrigeration system. The major considerations in designing a PV-refrigeration cycle involve appropriately matching the electrical characteristics of the motor driving the compressor with the available current and voltage being produced by the PV array. The rate of electrical power capable of being generated by a PV system is typically provided by manufacturers of PV modules for standard rating conditions, i.e., incident solar radiation of 1, W/m 2 (1 8 W/ft 2 ) and a module temperature of 25 C (77 F). Unfortunately, PV modules will operate over a wide range of conditions that are rarely as favorable as the rating condition. In addition, the power produced by a PV array is as variable as the solar resource from which it is derived. The performance of a PV module, expressed in terms of its currentvoltage and power-voltage characteristics, principally depends on the solar radiation and module temperature. Figure 2 shows current (solid lines) and power (dotted lines) vs. voltage for a 1.32 m 2 (14 ft 2 ) single crystalline PV module at the reference condition and four operating conditions. At any level of solar radiation and module temperature, a single operating voltage will result in maximum electrical power production from the module. The module represented in Figure 2 shows the voltage that yields maximum power ranges between 3 and 35 volts for this PV array. S e p t e m b e r 2 5 B u i l d i n g f o r t h e F u t u r e A S u p p l e m e n t t o A S H R A E J o u r n a l S 2 7
A B Figure 1a: Schematic of a vapor compression refrigeration sysgtem. Figure 1b: Pressure-enthalpy diagram for the cycle. 5 14 5 4 12 4 Current (Amp) 3 2 1 8 6 Power (W) Current (Amp) 3 2 1 4 2 1 1 2 3 4 5 Voltage (V) The efficiency of the solar panels, defined as the ratio of the electrical power produced to the incident radiation is between 8% to 1% at maximum power conditions for the PV array represented in Figure 2. If the PV refrigeration system is to operate at high efficiency, it is essential that the voltage imposed on the PV array be close to the voltage that provides maximum power. This requirement can be met in several ways. First, a maximum power tracker can be used which, in effect, continuously transforms the voltage required by the load to the maximum power voltage. If the system includes a battery, the battery voltage will control the operating voltage of the PV module. PV panels can then be chosen so that their maximum power voltage is close to the voltage for the battery system. The battery also provides electrical storage so that the system can operate at times when solar radiation is unavailable. However, the addition of a battery increases the weight of the system 1 2 3 4 5 Voltage (V) Figure 2 (left): Current (solid lines) and power (dotted lines) vs. voltage for a single crystalline PV module at different operating conditions. Figure 3 (right): Current-voltage characteristics for a PV module and two dc motor types. and reduces its steady-state efficiency. Electrical storage may not be needed in a solar refrigeration system as thermal storage, e.g., ice or other low temperature phase storage medium, may be more efficient and less expensive. A final option for systems that do not use a maximum power tracker or a battery is to select an electric motor having current-voltage characteristics closely matched to the maximum power output of the module. Figure 3 superimposes the current-voltage characteristics of a series dc motor and separately excited motor on the photovoltaic module. In this case, the separately excited motor would provide more efficient operation because it more closely matches the maximum power curve for the photovoltaic module. However, neither motor type represented in Figure 3 is well-matched to the characteristics of the PV module over the entire range of incident solar radiation. Studies of solar-powered motors have shown that permanent magnet or separately excited dc motors S 2 8 B u i l d i n g f o r t h e F u t u r e A S u p p l e m e n t t o A S H R A E J o u r n a l S e p t e m b e r 2 5
are always a better choice than series excited dc motors in direct-coupled systems that are not equipped with a maximum power tracker. Solar Mechanical Refrigeration Solar mechanical refrigeration uses a conventional vapor compression system driven by mechanical power that is produced with a solar-driven heat power cycle. The heat power cycle usually considered for this application is a Rankine cycle in which a fluid is vaporized at an elevated pressure by heat exchange with a fluid heated by solar collectors. A storage tank can be included to provide some high temperature thermal storage. The vapor flows through a turbine or piston expander to produce mechanical power, as shown in Figure 4. The fluid exiting the expander is condensed and pumped back to the boiler pressure where it is again vaporized. The efficiency of the Rankine cycle increases with increasing temperature of the vaporized fluid entering the expander, as shown in Figure 5 (bold line). The Rankine cycle efficiency in Figure 5 was estimated for a high-temperature organic fluid assuming that saturated vapor is provided to a 7% efficient expander and condensation occurs at 35 C (95 F). The efficiency of a solar collector, however, decreases with increasing Figure 4: Solar driven mechanical power cycle. temperature of the delivered energy. High temperatures can be obtained from concentrating solar collectors that track the sun s position in one or two dimensions. Tracking systems add cost, weight and complexity to the system. If tracking is to be avoided, evacuated tubular, compound parabolic or advanced multi-cover flat plate collectors can be used to produce fluid temperatures ranging between 1 C 2 C (212 F 392 F). The efficiency of solar collectors depends on both solar radiation and the difference in temperature between the entering fluid and ambient. Figure 5 also shows approximate solar collector efficiencies as a function of fluid delivery temperature for a range of solar radiation values. The overall efficiency of solar mechanical refrigeration, defined as the ratio of mechanical energy produced to the incident solar radiation, is the product of the efficiencies of the solar collector and the power cycle. Because of the competing effects with temperature, there is an optimum efficiency at any solar radiation. However, the opti- Efficiency.5.4.3.2.1. 1 12 14 16 18 2 1 12 14 16 18 2 Temperature ( C) Figure 5: Approximate efficiencies for a Rankine cycle (bold line) and evacuated solar collectors (fine lines) at 3 C (86 F) ambient and differing solar radiation values. mum efficiency would be a maximum of 4.5% for the conditions assumed in Figure 5. This efficiency is significantly lower than that which can be achieved with non-concentrating PV modules. Solar mechanical systems are competitive only at higher temperatures for which tracking solar collectors are required. Because of its economy-of-scale, this option would only be applicable for large refrigeration systems (e.g., 1, tons or 3,517 kw T ). Absorption Refrigeration Absorption refrigeration is the least intuitive of the solar refrigeration alternatives. Unlike the PV and solar mechanical refrigeration options, the absorption refrigeration system is considered a heatdriven system that requires minimal mechanical power for the compression process. It replaces the energy-intensive compression in a vapor compression system with a heatactivated thermal compression system. A schematic of a single-stage absorption system using ammonia as the refrigerant and ammonia-water as the absorbent is shown in Figure 6. Absorption cooling systems that use lithium bromide-water absorption-refrigerant working fluids can not be used at temperatures below C (32 F). The condenser, throttle and evaporator operate in the exactly the same manner as for the vapor compression system. In place of the compressor, however, the absorption system uses a series of three heat exchangers (absorber, regenerating intermediate heat exchanger and a generator) and a small solution pump. Ammonia vapor exiting the evaporator (State 6) is absorbed in a liquid solution of water-ammonia in the absorber. The absorption of ammonia vapor into the water-ammonia solution is analogous to a condensation process. The process is exothermic and so cooling water is required to carry away the heat of absorption. The principle governing this phase of the operation is that a vapor is more readily absorbed into a liquid solution as the temperature of the liquid solution is reduced. The ammonia-rich liquid solution leaving the absorber (State 7) is pumped to a higher pressure, passed through a heat exchanger and delivered to the generator (State 1). The minimum mechanical power needed to operate the pump is given by Equation 1, the same equation that applies to the minimum power needed by a compressor. However, the power requirement for the pump is S e p t e m b e r 2 5 B u i l d i n g f o r t h e F u t u r e A S u p p l e m e n t t o A S H R A E J o u r n a l S 2 9
much smaller than that for the compressor since v, the specific volume of the liquid solution, is much smaller than the specific volume of a refrigerant vapor. It is, in fact, possible to design an absorption system that does not require any mechanical power input relying instead on gravity. However, grid-connected systems usually rely on the use of a small pump. In the generator, the liquid solution is heated, which promotes desorption of the refrigerant (ammonia) from the solution. Unfortunately, some water also is desorbed with the ammonia, and it must be separated from the ammonia using the rectifier. Without the use of a rectifier, water exits at State 2 with the ammonia and travels to the evaporator, where it increases the temperature at which refrigeration can be provided. This solution temperature needed to drive the desorption process with ammonia-water is in the range between 12 C to 13 C (248 F to 266 F). Temperatures in this range can be obtained using low cost non-tracking solar collectors. At these temperatures, evacuated tubular collectors may be more suitable than flat-plate collectors as their efficiency is less sensitive to operating temperature. The overall efficiency of a solar refrigeration system is the product of the solar collection efficiency and the coefficient of performance of the absorption system. The efficiency of an evacuated tubular collector for different levels of solar radiation and energy delivery temperatures is given in Figure 5. The COP for a single-stage ammonia-water system depends on the evaporator and condenser temperatures. The COP for providing refrigeration at 1 C (14 F) with a 35 C (95 F) condensing temperature is approximately.5. Advanced absorption cycle configurations have been developed that could achieve higher COP values. The absorption cycle will operate with lower temperatures of thermal energy supplied from the solar collectors with little penalty to the COP, although the capacity will be significantly reduced. Figure 6: Ammonia-water absorption refrigeration system. A number of barriers have prevented more widespread use of solar refrigeration systems. First, solar refrigeration systems necessarily are more complicated, costly, and bulky than conventional vapor compression systems because of the necessity to locally generate the power needed to operate the refrigeration cycle. Second, the ability of a solar refrigeration system to function is driven by the availability of solar radiation. Because this energy resource is variable, some form of redundancy or energy storage (electrical or thermal) is required for most applications, which further adds to the system size and cost. The advantage of solar refrigeration systems is that they displace some or all of the conventional fuel use. The operating costs of a solar refrigeration system should be lower than that of conventional systems, but at current and projected fuel costs, this operating cost savings would not likely compensate for their additional capital costs, even in a longterm life-cycle analysis. The major advantage of solar refrigeration is that it can be designed to operate independent of a utility grid. Applications exist in which this capability is essential, such as storing medicines in remote areas. Of the three solar refrigeration concepts presented here, the photovoltaic system is most appropriate for small capacity portable systems located in areas not near conventional energy sources (electricity or gas). Absorption and solar mechanical systems are necessarily larger and bulkier and require extensive plumbing as well as electrical connections. In situations where the cost of thermal energy is high, absorption systems may be viable for larger stationary refrigeration systems. The solar mechanical refrigeration systems would require tracking solar collectors to produce high temperatures at which the heat power cycle efficiency becomes competitive. If the capital cost and efficiency of tracking solar collectors can be significantly reduced, this refrigeration system option could be effective in larger scale refrigeration applications. Conclusions An overall system coefficient of performance (COP sys ) can be defined as the ratio of refrigeration capacity to input solar energy. The COP sys is low for all three types of solar refrigeration systems. However, this definition of efficiency may not be the most relevant metric for a solar refrigeration system because the fuel that drives the system during operation, solar energy, is free. Other system metrics that are more important are the specific size, weight, and, of course, the cost. Additional Reading 21 ASHRAE Handbook Fundamentals, Chapter 1. Duffie, J.A. and W.A. Beckman. 1991. Solar Engineering of Thermal Processes, 2 nd ed. Wiley Interscience. Herold, K.E., R. Radermacher and S.A. Klein. 1996. Absorption Chillers and Heat Pumps, CRC Press. Al-Ibrahim, A.M. 1997. Optimum Selection of Direct-Coupled Photovoltaic Pumping System in Solar Domestic Hot Water Systems. Ph.D. Thesis, University of Wisconsin-Madison. S 3 B u i l d i n g f o r t h e F u t u r e A S u p p l e m e n t t o A S H R A E J o u r n a l S e p t e m b e r 2 5