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where v1 is the specific volume of the suction gas, and h1 and h2 are the specific enthalpy of the suction and discharge gas, respectively. The latter was calculated as: h2 =h1+⎛⎜his −h1⎞⎟⋅(1−βHL) (6.3) ⎝ ηis ⎠ The subscript is refers to isentropic compression of the gas. The discharge temperature from the compressor was computed on the basis of the discharge pressure and the specific enthalpy of the discharge gas. For most of the simulations, the volumetric and isentropic efficiencies as well as the relative heat loss from the compressor were based on measure- ments from the prototype CO2 compressor (ref. Section 5.1.3.6, Com- pressor Performance). 6.1.3 The Tripartite Gas Cooler Model 6.1.3.1 Introduction The tripartite CO2 gas cooler was modelled as three single-pass counter- flow tube-in-tube heat exchanger units, where the CO2 was flowing in the inner tube and water in the annulus. Figure 6.2 sketches the principle of the cross-section of one of the gas cooler units. Wire CO2 Water Figure 6.2 Principle of the cross section of a gas cooler unit. The input parameters for the tripartite gas cooler were as follows: ♦ Detailed tube geometries ♦ The CO2 inlet pressure, pGC ♦ The CO2 inlet temperature, TGC ♦ The CO2 mass flow rate, m& ♦ The inlet water temperatures ♦ The water flow rates 6 – Modelling 173PDF Image | Residential CO2 Heat Pump System for Combined
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CO2 Organic Rankine Cycle Experimenter Platform The supercritical CO2 phase change system is both a heat pump and organic rankine cycle which can be used for those purposes and as a supercritical extractor for advanced subcritical and supercritical extraction technology. Uses include producing nanoparticles, precious metal CO2 extraction, lithium battery recycling, and other applications... More Info
Heat Pumps CO2 ORC Heat Pump System Platform More Info
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