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Electric Power Generation From Low-Enthalpy Heat Recovery in FPSOs Using Kalina Cycle

[+] Author Affiliations
Carlos Eymel Campos Rodríguez, Cesar Adolfo Rodríguez Sotomonte

3E Gestão Energética LTDA, Itajubá, Brazil

Thiago Gotelip Correa Veloso, Antônio Alves de Moura Junior, Christian Jeremi Coronado Rodríguez, Marco Antônio Rosa do Nascimento

Universidade Federal de Itajubá, Itajubá, Brazil

Paper No. GT2016-56238, pp. V003T25A003; 10 pages
  • ASME Turbo Expo 2016: Turbomachinery Technical Conference and Exposition
  • Volume 3: Coal, Biomass and Alternative Fuels; Cycle Innovations; Electric Power; Industrial and Cogeneration; Organic Rankine Cycle Power Systems
  • Seoul, South Korea, June 13–17, 2016
  • Conference Sponsors: International Gas Turbine Institute
  • ISBN: 978-0-7918-4974-3
  • Copyright © 2016 by ASME


The present work aims to study, by mean of the First and Second Law the Thermodynamic, the performance of a Kalina Cycle (KCS-34) using low-temperature waste heat recovery in the fourth stage of compression in the CO2 Compression Unit on a Floating Production, Storage and Offloading System (FPSO). Different parameters are evaluated associated with the evaporator to improve the heat absorption of the cycle and taking into account the area of the system too. Three different concentrations of ammonia water mixture are studied, between 65% and 85% of ammonia mass fraction, the CO2 acting as a hot fluid, entry to the evaporator of the Kalina Cycle at 135.2 °C. Some other parameters taking into account in this work are: evaporation pressure, pinch point temperature and terminal temperature differential (TTD) to reach the maximum power production and first and second law efficiency. The Aspen-Hysys software V. 8.6 is used as a tool to simulate the thermal system and Peng-Robinson Stryek-Vera (PRSV) equations of state (EoS). A power output gain in the cycle is obtained with a higher ammonia mass fraction, reaching a maximum net power output of 598 kW using 85% of ammonia mass fraction, a pinch point of 2 °C, a terminal temperature differential of 10 °C and 3500 kPa of the working pressure. Ending, a total heat exchange area calculation is determined in order to have an idea of how big the system is for the different design projects.

Copyright © 2016 by ASME



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