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Research Papers

Investigation on Operating Processes for a New Solar Cooling Cogeneration Plant

[+] Author and Article Information
R. Shankar

CO2 Research and Green Technologies Centre,
Energy Division School of Mechanical
and Building Sciences,
VIT University,
Vellore 632 014, Tamil Nadu, India

T. Srinivas

CO2 Research and Green Technologies Centre,
Energy Division School of Mechanical
and Building Sciences,
VIT University,
Vellore 632 014, Tamil Nadu, India
e-mail: srinivastpalli@yahoo.co.in

1Corresponding author.

Contributed by the Solar Energy Division of ASME for publication in the JOURNAL OF SOLAR ENERGY ENGINEERING. Manuscript received January 31, 2013; final manuscript received March 30, 2014; published online May 2, 2014. Assoc. Editor: Werner Platzer.

J. Sol. Energy Eng 136(3), 031016 (May 02, 2014) (10 pages) Paper No: SOL-13-1034; doi: 10.1115/1.4027423 History: Received January 31, 2013; Revised March 30, 2014

Some commercial units and industries need more amount of cooling than the power such as cold storage, shopping complex, etc. In this work, a new cooling cogeneration cycle (Srinivas cycle) has been proposed and solved to generate more cooling with adequate power generation from single source of heat at hot climatic conditions with ammonia–water mixture as a working fluid. The operational processes conditions for the proposed cooling cogeneration plant are different compared to the power-only (Kalina cycle system) system and cooling-only (vapor absorption refrigeration) system. This work focused to generate the optimum working conditions by parametric analysis from thermodynamic point of view. An increase in cycle maximum temperature is only supporting the power generation but not the cooling output. Cooling output is also 15 times more than power generation. So, it has been recommended to operate the integrated plant with low temperature heat recovery. The resulted cycle thermal efficiency, plant thermal efficiency, specific power, specific cooling, cycle power efficiency, cycle coefficient of performance (COP), and solar collector's specific area are 27%, 10%, 15 kW, 220 kW, 1.8%, 0.25, and 10 m2/kW, respectively.

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Figures

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Fig. 1

Schematic arrangement of cooling cogeneration plant; THR, throttle valve; MIX, mixer

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Fig. 2

(a) Enthalpy–concentration and (b) temperature–entropy diagram for the cooling cogeneration cycle shown in Fig. 1

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Fig. 3

Plant pressure variations with separator vapor fraction and generator temperature at the turbine concentration of 0.9

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Fig. 4

Plant performance variations with vapor fraction and its temperature on (a) cycle thermal efficiency–specific power; (b) plant thermal efficiency–cooling effect; (c) cycle power efficiency–cycle COP; and (d) total output–solar collector's area at the turbine concentration of 0.9

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Fig. 5

Plant pressure variations with separator vapor fraction and turbine ammonia concentration at the separator temperature of 150 °C

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Fig. 6

Plant performance variations with vapor fraction and turbine concentration on (a) cycle thermal efficiency–specific power; (b) plant thermal efficiency–cooling effect; (c) cycle power efficiency–cycle COP; and (d) total output–solar collector's area at the separator temperature of 150 °C

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Fig. 7

Plant performance variations with vapor fraction and circulating cooling water inlet temperature on (a) cycle thermal efficiency–specific power; (b) plant thermal efficiency–cooling effect; (c) cycle power efficiency–cycle COP; and (d) total output–solar collector's area

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Fig. 8

Comparison of exergetic losses in compound cycle components/processes; ABS, absorber; CDP, condensate pump; CND, condenser; DM, dephlegmator; EVP, evaporator; HEX, heat exchanger; HRVG, heat recovery vapor generator; MIX, mixer; SEP, separator; THR, throttling

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