In turbomachinery, the slip factor is a measure of the fluid slip in the impeller of a compressor or a turbine, mostly a centrifugal machine. Fluid slip is the deviation in the angle at which the fluid leaves the impeller from the impeller's blade/vane angle. Being quite small in axial impellers (inlet and outlet flow in the same direction), slip is a very important phenomenon in radial impellers and is useful in determining the accurate estimation of work input or the energy transfer between the impeller and the fluid, rise in pressure and the velocity triangles at the impeller exit. A simple explanation for the fluid slip can be given as: Consider an impeller with z number of blades rotating at angular velocity ω. A difference in pressure and velocity during the course of clockwise flow through the impeller passage can be observed between the trailing and leading faces of the impeller blades. High pressure and low velocity are observed at the leading face of the impeller's blade as compared to lower pressure with high velocity at the trailing face of the blade. This results in circulation in the direction of ω around the impeller blade which prevents the air from acquiring the whirl velocity equivalent to impeller speed with non-uniform velocity distribution at any radius. This phenomenon reduces the output whirl velocity, which is a measure of the net power output from a turbine or a compressor. Hence, the slip factor accommodates for a slip loss which affects the net power developed which increases with increasing flow-rate.
Factors accounting for slip factor Relative eddy. Back eddy. Impeller design or geometry Mean blade loading. Thickness of blade. Finite number of blades. Fluid entry conditions. Working fluid's viscosity. Effect of boundary layer growth. Flow separation. Friction forces on the walls of flow packages. Boundary layer blockage.
Mathematical Formulae for Slip factor
Mathematically, the Slip factor denoted by 'σ' is defined as the ratio of the actual & ideal values of the whirl velocity components at the exit of the impeller. The ideal values can be calculated using an analytical approach while the actual values should be observed experimentally.
σ = V w 2 ′ V w 2 {\displaystyle \sigma ={\frac {V'_{w2}}{V_{w2}}}}
where,
V'w2 : Actual Whirl Velocity Component , Vw2 : Ideal Whirl Velocity Component Usually,σ varies from 0-1 with an average ranging from 0.8-0.9. The Slip Velocity is given as: VS = Vw2 - V'w2 = Vw2(1-σ) The Whirl Velocity is given as: V'w2 = σ Vw2
Slip Factor correlations Stodola's Equation: According to Stodola, it is the relative eddy that fills the entire exit session of the impeller passage. For a given flow geometry, the slip factor increases with the increase in the number of impeller blades, thus, accounts for one of the important parameter for losses.
σ = 1 − π z sin β 2 ( 1 − ϕ 2 cot β 2 ) {\displaystyle \sigma =1-{\frac {\pi }{z}}{\frac {\sin \beta _{2}}{(1-\phi _{2}\cot \beta _{2})}}}
where, z = number of blades and ϕ 2 = V r 2 U 2 {\displaystyle \phi _{2}={\frac {V_{r2}}{U_{2}}}} For Radial tip, β2 = 900 ∴ σ = 1 − π z {\displaystyle \sigma =1-{\frac {\pi }{z}}}
Theoretically, In order to get the perfect ideal flow guidance, one can infinitesimally increase the number of thin vanes so that the flow should leave the impeller at an exact vane angle. However, later experiments proved that beyond a particular value, a further increase in number of blades results in reduction of slip factor due to increase in blockage area. Stanitz's Equation: Stanitz found the slip velocity does not depend upon the blade exit angle and hence, gave the following equation.
σ = 1 − 1.98 z ( 1 − ϕ 2 cot β 2 ) {\displaystyle \sigma =1-{\frac {1.98}{z(1-\phi _{2}\cot \beta _{2})}}}
where, z = number of blades, β2 varies from 450 to 900. For radial tip: β2 = 900 ∴ σ = 1 − 1.98 z = 1 − 0.63 ∗ p i z {\displaystyle \sigma =1-{\frac {1.98}{z}}=1-{\frac {0.63*pi}{z}}}
Balje's formula: An approximate formula given by Balje for radial-tipped (β2=900) blade impellers:
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