Performance Analysis and Multi-Objective Optimization of a Cooling-Power-Desalination Combined Cycle for Shipboard Diesel Exhaust Heat Recovery

Abstract

This study presents a novel cooling-power-desalination combined cycle for recovering shipboard diesel exhaust heat, integrating a freezing desalination sub-cycle to regulate the ship’s cooling-load fluctuations. The combined cycle employs ammonia–water as the working fluid and efficiently utilizes excess cooling capacity to pretreat reverse osmosis desalination. By adjusting the mass flow rate of the working fluid in both the air conditioning refrigeration cycle and the freezing desalination sub-cycle, the combined cycle can dynamically meet the cooling-load demand under different working conditions and navigation areas. To analyze the cycle’s performance, a mathematical model is established for energy and exergy analysis, and key parameters including net output work, comprehensive efficiency, and heat exchanger area are optimized using the MOPSO algorithm. The results indicate that the system achieves optimal performance when the generator temperature reaches 249.95 °C, the sea water temperature is 22.29 °C, and 42% ammonia–water is used as the working fluid. Additionally, an economic analysis of frozen seawater desalination as RO seawater desalination pretreatment reveals a substantial cost reduction of 22.69%, showcasing the advantageous features of this proposed cycle. The research in this paper is helpful for waste energy recovery and sustainable development.

Energy, Exergy, Exergoeconomic Analysis, and Optimization in a Natural Gas Decompression Station with a Vortex Tube and Geothermal Preheating

“…Once the heat exchanger's ending temperature differences are obtained (θ A and θ B in • C), the LMTD is defined from Equation (7) [51]:…”

“…The overall heat transfer coefficient is defined by the inside and outside pipe diameter relation (m), the convective heat transfer coefficient ( kW/m 2 •K , and the thermal conduc-tivity of the pipe ( W/m•K) [52]. A term that considers the U form from the exchanger tube and the well filling ( W/m•K) is implemented, Equation ( 8): Once the heat exchanger s ending temperature differences are obtained (𝜃 and 𝜃 in °C), the LMTD is defined from Equation ( 7) [51]:…”