Supercritical Carbon Dioxide Cycle Analysis

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Supercritical Carbon Dioxide Cycle Analysis ( supercritical-carbon-dioxide-cycle-analysis )

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3.3.5 Loss Calculations Within the impeller losses will occur. They are represented by both pressure losses and additional work terms. The loss calculations depend on some parameters that describe the shape of the impeller. The impeller shape is determined by the hub and tip diameters at inlet, the outlet diameters, blade height, and blade angles. The shape will affect the losses as the fluid flows through the passages. The subroutine IMP_SHAPE calculates the blade length based on the impeller diameters and the blade angles. The blade passage is assumed to follow an elliptical shape in the meridional plane. The impeller losses are then calculated using subroutines that are based on empirical or semi-empirical formulas. There is no hard and fast convention for how losses are calculated. When more experimental data for S-CO2 compressors is available in the literature, the loss calculations may be improved by adding appropriate correction factors to the present loss correlations. Losses in the impeller are subdivided into incidence, blade loading, skin friction, hub-to- shroud loading, mixing, diffusion, expansion, and tip clearance loss. These are expressed as fractional pressure losses and are defined as described by Aungier [2000]. Disk friction, leakage, and recirculation losses are expressed as additional work terms, per unit mass. The total fractional pressure loss, πœ”π‘‘π‘œπ‘‘ , will be converted into an absolute pressure loss by βˆ†π‘ƒπ‘–π‘šπ‘ =𝜌1𝑉12πœ”π‘‘π‘œπ‘‘ Eqn.3-11 2 so that πœ”π‘‘π‘œπ‘‘ represents a portion of the dynamic pressure at the impeller inlet. Clearance loss is the loss associated with Coriolis forces on the fluid between the impeller blades and the stationary casing. It is defined as a fractional pressure loss and is given by πœ”πΆπΏ =2π‘šπΆπΏβˆ†π‘ƒπΆπΏ Eqn.3-12 π‘š 𝜌 1 π‘Š1 where βˆ†π‘ƒπΆπΏ is the pressure gradient along the clearance gap and is determined by the geometry of the impeller blades, the blade speeds, and the mass flow rate through the impeller, as βˆ†π‘ƒπΆπΏ = π‘š 𝐷2π‘‰π‘ˆ2 βˆ’ 𝐷1π‘‰π‘ˆ1 Eqn. 3-13 2 π‘π‘’π‘“π‘“π‘Ÿπ‘πΏπ‘ 60

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