Turbulent Prandtl number

Turbulent Prandtl number

The turbulent Prandtl number (Pr_t) is a non-dimensional term defined as the ratio between the momentum eddy diffusivity and the heat transfer eddy diffusivity. It is useful for solving the heat transfer problem of turbulent boundary layer flows. The simplest model for Pr_t is the Reynolds analogy, which yields a turbulent Prandtl number of 1. From experimental data, Pr_t has an average value of 0.85, but ranges from 0.7 to 0.9 depending on the Prandtl number of the fluid in question.

Definition

The introduction of eddy diffusivity and subsequently the turbulent Prandtl number works as a way to define a simple relationship between the extra shear stress and heat flux that is present in turbulent flow. If the momentum and thermal eddy diffusivities are zero (no apparent turbulent shear stress and heat flux), then the turbulent flow equations reduce to the laminar equations. We can define the eddy diffusivities for momentum transfer epsilon_M and heat transfer epsilon_H as
-overline{u'v'} = epsilon_M frac{partial ar{u{partial y} and -overline{v'T'} = epsilon_H frac{partial ar{T{partial y}
where -overline{u'v'} is the apparent turbulent shear stress and -overline{v'T'} is the apparent turbulent heat flux.
The turbulent Prandtl number is then defined as
Pr_t = frac{epsilon_M}{epsilon_H}

Application

Turbulent momentum boundary layer equation:
ar {u} frac{partial ar{u{partial x} + ar {v} frac{partial ar{u{partial y} = -frac{1}{ ho} frac{dar{P{dx} + frac{partial}{partial y} left [( u frac{partial ar{u{partial y} - overline{u'v'}) ight]
Turbulent thermal boundary layer equation,
ar {u} frac{partial ar{T{partial x} + ar {v} frac{partial ar{T{partial y} = frac{partial}{partial y} left (alpha frac{partial ar{T{partial y} - overline{v'T'} ight)

Substituting the eddy diffusivities into the momentum and thermal equations yields
ar {u} frac{partial ar{u{partial x} + ar {v} frac{partial ar{u{partial y} = -frac{1}{ ho} frac{dar{P{dx} + frac{partial}{partial y} left [( u + epsilon_M) frac{partial ar{u{partial y} ight]
and
ar {u} frac{partial ar{T{partial x} + ar {v} frac{partial ar{T{partial y} = frac{partial}{partial y} left [(alpha + epsilon_H) frac{partial ar{T{partial y} ight]
Substitute into the thermal equation using the definition of the turbulent Prandtl number to get
ar {u} frac{partial ar{T{partial x} + ar {v} frac{partial ar{T{partial y} = frac{partial}{partial y} left [(alpha + frac{epsilon_M}{Pr_t}) frac{partial ar{T{partial y} ight]

Consequences

In the special case where the Prandtl number and turbulent Prandtl number are both equal to one (as in the Reynolds analogy), the velocity profile and temperature profiles are identical. This greatly simplifies the solution of the heat transfer problem. If the Prandtl number and turbulent Prandtl number are not one, the solution is still simplified because by knowing the fluid's properties but only the momentum eddy diffusivity, one can still solve both the momentum and thermal equations.

In a general case of three-dimensional turbulence, the concept of eddy viscosity and eddy diffusivity are not valid. Consequently, the turbulent Prandtl number has no meaning(W. M. Kays, 1994 Turbulent Prandtl Number--where are we? "Transaction of the ASME", 116, 284-295)

References


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