Analysis of reciprocating booster compressor performance by mathematical modelling methods

Kotlov, A. A.; Kuznetsov, L. G.; Burakov, A. V.

doi:10.1063/1.5122062

Cited by 2 publications

(1 citation statement)

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“… 18 It can effectively decrease the compressor size, contributing to a higher competition of fuel cell vehicles to conventional ones. Kotlov et al 19 analyzed the performance of a reciprocating compressor using a numerical simulation method, indicating that optimizations of valve designs effectively improved the compressor efficiency. In-cylinder flows of a reciprocating compressor were conducted using dynamic numerical simulations by Mi et al 20 P – V diagrams of the compressor were used to analyze the pressure loss over various rotation speeds.…”

Section: Introductionmentioning

confidence: 99%

Preliminary Investigations of an Opposed Rotary Piston Compressor for the Air Feeding of a Polymer Electrolyte Membrane Fuel Cell System

et al. 2020

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Automotive polymer electrolyte membrane fuel cell systems are attracting much attention, driven by the requirements of low automotive exhaust emissions and energy consumption. A polymer electrolyte membrane fuel cell system provides opportunities for the developments in different types of air compressors. This paper proposed an opposed rotary piston compressor, which had the merits of more compact structures, less movement components, and a high pressure ratio, meeting the requirements of polymer electrolyte membrane fuel cell systems. Preliminary performance evaluations of the opposed rotary piston compressor were conducted under various scenarios. This will make a foundation for optimizations of outlet pipe layouts of the compressor. A three-dimensional numerical simulation approach was used; further, in-cylinder pressure evolutions, fluid mass flow rates, and P – V diagrams were analyzed. It indicated that the cyclic period of the opposed rotary piston compressor was half of reciprocating piston compressors. The specific mass flow rate of the compressor is in the range of 0.094–0.113 kg·(s·L) −1 for the given scenarios. Outlet ports 1 and 2 dominated the mass flow in the discharge process under scenarios 1, 3, and 4. In-cylinder pressure profiles show multipeaks for all of these scenarios. In-cylinder pressure increased rapidly in the compression process and part of the discharge process, which led to high energy consumption and low adiabatic efficiency. The maximum adiabatic efficiency is approximately 43.96% among the given scenarios.

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Section: Introductionmentioning

confidence: 99%