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Research Papers: Energy Systems Analysis

Performance Assessments of Organic Rankine Cycle With Internal Heat Exchanger Based on Exergetic Approach

[+] Author and Article Information
Nurettin Yamankaradeniz

Department of Mechanical Engineering,
Engineering Faculty,
Uludag University,
Bursa 16059, Turkey
e-mail: nyk@uludag.edu.tr

Ali Husnu Bademlioglu

Department of Energy Systems Engineering,
Faculty of Natural Sciences,
Architecture and Engineering,
Bursa Technical University,
Bursa 16330, Turkey
e-mail: husnu.bademlioglu@btu.edu.tr

Omer Kaynakli

Professor
Department of Mechanical Engineering,
Engineering Faculty,
Uludag University,
Bursa 16059, Turkey
e-mail: kaynakli@uludag.edu.tr

Contributed by the Advanced Energy Systems Division of ASME for publication in the JOURNAL OF ENERGY RESOURCES TECHNOLOGY. Manuscript received October 25, 2017; final manuscript received April 30, 2018; published online May 15, 2018. Assoc. Editor: Abel Hernandez-Guerrero.

J. Energy Resour. Technol 140(10), 102001 (May 15, 2018) (8 pages) Paper No: JERT-17-1588; doi: 10.1115/1.4040108 History: Received October 25, 2017; Revised April 30, 2018

This study makes energy and exergy analysis of a sample organic Rankine cycle (ORC) with a heat exchanger which produces energy via a geothermal source with a temperature of 140 °C. R600a is preferred as refrigerant to be used in the cycle. The changes in exergy destructions (of irreversibility) and exergy efficiencies in each cycle element are calculated in the analyses made based on the effectiveness of heat exchanger used in cycle and evaporator temperature changing between 60 and 120 °C for fixed pinch point temperature differences in evaporator and condenser. Parameters showing system performance are assessed via second law approach. Effectiveness of heat exchanger and temperature of evaporator are taken into consideration within the scope of this study, and energy and exergy efficiencies of cycle are enhanced maximum 6.87% and 6.21% respectively. Similarly, exergy efficiencies of evaporator, heat exchanger, and condenser are increased 4%, 82%, and 1.57%, respectively, depending on the effectiveness of heat exchanger and temperature of evaporator.

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Figures

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Fig. 1

Schematic (a) and T–s (b) diagrams of ORC with heat exchanger

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Fig. 2

The change of turbine work, exergy destruction, and exergy efficiency in the turbine depending on the evaporator temperature

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Fig. 3

The change of exergy destruction (a) and exergy efficiency in the condenser (b) for different evaporator temperatures depending on the effectiveness of heat exchanger

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Fig. 4

The changes of exergy destruction (a) and exergy efficiency in the heat exchanger (b) for different evaporator temperatures depending on the effectiveness of heat exchanger

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Fig. 5

The change of required pump work, exergy destruction, and exergy efficiency in the pump depending on the evaporator temperature

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Fig. 6

The change of exergy destruction (a) and efficiency in the evaporator (b) for varying evaporator temperatures depending on the effectiveness of heat exchanger

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Fig. 7

The change of thermal (a) and exergy (b) efficiencies of cycle for varying evaporator temperatures depending on the effectiveness of heat exchanger

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Fig. 8

Exergy destruction in cycle elements and their proportional changes in total exergy destructions (a) ε = 0.2, Tevap = 120 °C, (b) ε = 0.8, Tevap = 120 °C, (c) ε = 0.2, Tevap = 60 °C, and (d) ε = 0.8, Tevap = 60 °C

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