Chapter 5: Problem 99
Is there any limitation on the size of the time step \(\Delta t\) in the solution of transient heat conduction problems using \((a)\) the explicit method and \((b)\) the implicit method?
Chapter 5: Problem 99
Is there any limitation on the size of the time step \(\Delta t\) in the solution of transient heat conduction problems using \((a)\) the explicit method and \((b)\) the implicit method?
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Get started for freeA fuel element \((k=67 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\) that can be modeled as a plane wall has a thickness of \(4 \mathrm{~cm}\). The fuel element generates \(5 \times 10^{7} \mathrm{~W} / \mathrm{m}^{3}\) of heat uniformly. Both side surfaces of the fuel element are cooled by liquid with temperature of \(90^{\circ} \mathrm{C}\) and convection heat transfer coefficient of $5000 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}$. Use a uniform nodal spacing of \(4 \mathrm{~mm}\) and make use of the symmetry line at the center of the plane wall to determine \((a)\) the finite difference equations and \((b)\) the nodal temperatures by solving those equations.
Using appropriate software, solve these systems of algebraic equations. (a) $$ \begin{aligned} 3 x_{1}+2 x_{2}-x_{3}+x_{4} &=6 \\ x_{1}+2 x_{2}-x_{4} &=-3 \\ -2 x_{1}+x_{2}+3 x_{3}+x_{4} &=2 \\ 3 x_{2}+x_{3}-4 x_{4} &=-6 \end{aligned} $$ (b) $$ \begin{aligned} 3 x_{1}+x_{2}^{2}+2 x_{3} &=8 \\ -x_{1}^{2}+3 x_{2}+2 x_{3} &=-6.293 \\ 2 x_{1}-x_{2}^{4}+4 x_{3} &=-12 \end{aligned} $$
Consider steady one-dimensional heat conduction in a pin fin of constant diameter \(D\) with constant thermal conductivity. The fin is losing heat by convection to the ambient air at \(T_{\infty}\) with a heat transfer coefficient of \(h\). The nodal network of the fin consists of nodes 0 (at the base), 1 (in the middle), and 2 (at the fin tip) with a uniform nodal spacing of $\Delta x$. Using the energy balance approach, obtain the finite difference formulation of this problem to determine \(T_{1}\) and \(T_{2}\) for the case of specified temperature at the fin base and negligible heat transfer at the fin tip. All temperatures are in \({ }^{\circ} \mathrm{C}\).
Consider transient heat conduction in a plane wall with variable heat generation and constant thermal conductivity. The nodal network of the medium consists of nodes 0,1 , 2,3 , and 4 with a uniform nodal spacing of $\Delta x$. The wall is initially at a specified temperature. Using the energy balance approach, obtain the explicit finite difference formulation of the boundary nodes for the case of uniform heat flux \(\dot{q}_{0}\) at the left boundary (node 0 ) and convection at the right boundary (node 4) with a convection coefficient of \(h\) and an ambient temperature of \(T_{\infty}\). Do not simplify.
Consider steady two-dimensional heat transfer in a long solid bar of square cross section in which heat is generated uniformly at a rate of $\dot{e}=0.19 \times 10^{5} \mathrm{Btu} / \mathrm{h} \cdot \mathrm{ft}^{3}$. The cross section of the bar is \(0.5 \mathrm{ft} \times 0.5 \mathrm{ft}\) in size, and its thermal conductivity is $k=16 \mathrm{Btu} / \mathrm{h} \cdot \mathrm{ft} \cdot{ }^{\circ} \mathrm{F}$. All four sides of the bar are subjected to convection with the ambient air at \(T_{\infty}=70^{\circ} \mathrm{F}\) with a heat transfer coefficient of $h=7.9 \mathrm{Btu} / \mathrm{h} \cdot \mathrm{ft}^{2}{ }^{\circ} \mathrm{F}$. Using the finite difference method with a mesh size of \(\Delta x=\Delta y=0.25 \mathrm{ft}\), determine \((a)\) the temperatures at the nine nodes and \((b)\) the rate of heat loss from the bar through a 1-ft-long section.
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