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Bounds for internally heated convection with fixed boundary heat flux

Published online by Cambridge University Press:  05 July 2021

Ali Arslan*
Affiliation:
Department of Aeronautics, Imperial College London, London SW7 2AZ, UK
Giovanni Fantuzzi
Affiliation:
Department of Aeronautics, Imperial College London, London SW7 2AZ, UK
John Craske
Affiliation:
Department of Civil and Environmental Engineering, Imperial College London, London SW7 2AZ, UK
Andrew Wynn
Affiliation:
Department of Aeronautics, Imperial College London, London SW7 2AZ, UK
*
†Email address for correspondence: a.arslan18@imperial.ac.uk

Abstract

We prove a new rigorous bound for the mean convective heat transport $\langle w T \rangle$, where $w$ and $T$ are the non-dimensional vertical velocity and temperature, in internally heated convection between an insulating lower boundary and an upper boundary with a fixed heat flux. The quantity $\langle wT \rangle$ is equal to half the ratio of convective to conductive vertical heat transport, and also to $\frac 12$ plus the mean temperature difference between the top and bottom boundaries. An analytical application of the background method based on the construction of a quadratic auxiliary function yields $\langle w T \rangle \leq \frac {1}{2}(\frac {1}{2}+ \frac {1}{\sqrt {3}} ) - 1.6552\, {\textit {R}}^{-(1/3)}$ uniformly in the Prandtl number, where R is the non-dimensional control parameter measuring the strength of the internal heating. Numerical optimisation of the auxiliary function suggests that the asymptotic value of this bound and the $-1/3$ exponent are optimal within our bounding framework. This new result halves the best existing (uniform in $ {\textit {R}}$) bound (Goluskin, Internally Heated Convection and Rayleigh–Bénard Convection, Springer, 2016, table 1.2), and its dependence on $ {\textit {R}}$ is consistent with previous conjectures and heuristic scaling arguments. Contrary to physical intuition, however, it does not rule out a mean heat transport larger than $\frac 12$ at high $ {\textit {R}}$, which corresponds to the top boundary being hotter than the bottom one on average.

Information

Type
JFM Rapids
Copyright
© The Author(s), 2021. Published by Cambridge University Press
Figure 0

Figure 1. The IH convection (a) with isothermal boundaries, studied by Arslan et al. (2021), and (b) with fixed-flux boundary conditions, studied in this paper. In both panels, IH represents the uniform unit internal heat generation. Red dashed lines denote the conductive temperature profiles, and red solid lines denote indicative mean temperature profiles in the turbulent regime.

Figure 1

Figure 2. Sketch of the piecewise linear $\phi '(z)$ in (4.5a,b).

Figure 2

Figure 3. (a) Numerically optimal bounds $U_{n}$ computed with quinopt (black solid line), compared to the analytical bound $U_{a}$ (4.15) (blue solid line) and the improved uniform upper bound $\frac 12(\frac 12 + \frac {1}{\sqrt {3}})$ (dotted line). The inset (b) shows the ratio of the two R-dependent bounds. (c) Analytical (blue) and numerical (black) corrections to the uniform bound $\frac 12(\frac 12 + \frac {1}{\sqrt {3}})$, compensated by $ {\textit {R}}^{1/3}$. (d) Numerically optimal profiles $\phi '$ for $10^{3} \leq {\textit {R}} \leq 10^{9}$ (grey). Highlighted profiles for $ {\textit {R}} = 10^{5}$ (yellow), $ {\textit {R}} = 10^{7}$ (red) and $ {\textit {R}} = 10^{9}$ (brown) correspond to the circles in panels (a) and (c). (e) Balance parameters $a$ (blue solid line, optimal; blue dashed line, analytical) and $b$ (orange solid line, optimal; orange dashed line, analytical).