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The finite difference formulation of steady two-dimensional heat conduction in a medium with heat generation and constant thermal conductivity is given by $$ \begin{gathered} \frac{T_{m-1, n}-2 T_{m, n}+T_{m+1, n}}{\Delta x^{2}}+\frac{T_{m, n-1}-2 T_{m, n}+T_{m, n+1}}{\Delta y^{2}} \\ +\frac{\dot{e}_{m, n}}{k}=0 \end{gathered} $$ in rectangular coordinates. Modify this relation for the threedimensional case.

Short Answer

Expert verified
Answer: The three-dimensional finite difference equation for steady heat conduction with heat generation and constant thermal conductivity is given by: $$\frac{T_{m-1, n, p}-2 T_{m, n, p}+T_{m+1, n, p}}{\Delta x^{2}}+\frac{T_{m, n-1, p}-2 T_{m, n, p}+T_{m, n+1, p}}{\Delta y^{2}} + \frac{T_{m, n, p-1}-2 T_{m, n, p}+T_{m, n, p+1}}{\Delta z^{2}} + \frac{\dot{e}_{m, n, p}}{k} = 0$$

Step by step solution

01

Understand the given two-dimensional equation

The finite difference equation provided represents a two-dimensional heat conduction problem with heat generation and constant thermal conductivity. In this equation, the term \(\frac{T_{m-1, n}-2 T_{m, n}+T_{m+1, n}}{\Delta x^{2}}\) represents the heat conduction in the x-direction while \(\frac{T_{m, n-1}-2 T_{m, n}+T_{m, n+1}}{\Delta y^{2}}\) represents heat conduction in the y-direction. \(\frac{\dot{e}_{m, n}}{k}\) is the heat generation term divided by thermal conductivity.
02

Introduce the third dimension (z-direction)

As we want to modify this equation for the three-dimensional case, we need to introduce an additional variable, z, to account for heat conduction in the z-direction. To do this, we will add a term similar to the x and y directions, representing heat conduction in the z-direction: $$\frac{T_{m, n, p-1}-2 T_{m, n, p}+T_{m, n, p+1}}{\Delta z^{2}}$$
03

Formulate the three-dimensional finite difference equation

Now, we will combine the given two-dimensional equation with the new z-direction term to form the three-dimensional finite difference equation. $$\frac{T_{m-1, n, p}-2 T_{m, n, p}+T_{m+1, n, p}}{\Delta x^{2}}+\frac{T_{m, n-1, p}-2 T_{m, n, p}+T_{m, n+1, p}}{\Delta y^{2}} + \frac{T_{m, n, p-1}-2 T_{m, n, p}+T_{m, n, p+1}}{\Delta z^{2}} + \frac{\dot{e}_{m, n, p}}{k} = 0$$ Here, we have the three-dimensional finite difference formulation for steady heat conduction with heat generation and constant thermal conductivity.

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Most popular questions from this chapter

Consider transient one-dimensional heat conduction in a plane wall that is to be solved by the explicit method. If both sides of the wall are at specified temperatures, express the stability criterion for this problem in its simplest form.

Consider a large plane wall of thickness \(L=0.4 \mathrm{~m}\), thermal conductivity \(k=2.3 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\), and surface area \(A=20 \mathrm{~m}^{2}\). The left side of the wall is maintained at a constant temperature of \(95^{\circ} \mathrm{C}\), while the right side loses heat by convection to the surrounding air at $T_{\infty}=15^{\circ} \mathrm{C}\( with a heat transfer coefficient of \)h=18 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}$. Assuming steady one-dimensional heat transfer and taking the nodal spacing to be \(10 \mathrm{~cm}\), (a) obtain the finite difference formulation for all nodes, (b) determine the nodal temperatures by solving those equations, and (c) evaluate the rate of heat transfer through the wall.

Consider a house whose windows are made of \(0.375\)-in-thick glass $\left(k=0.48 \mathrm{Btu} / \mathrm{h} \cdot \mathrm{ft} \cdot{ }^{\circ} \mathrm{F}\right.\( and \)\alpha=4.2 \times\( \)10^{-6} \mathrm{ft}^{2} / \mathrm{s}$ ). Initially, the entire house, including the walls and the windows, is at the outdoor temperature of \(T_{o}=35^{\circ} \mathrm{F}\). It is observed that the windows are fogged because the indoor temperature is below the dew-point temperature of \(54^{\circ} \mathrm{F}\). Now the heater is turned on, and the air temperature in the house is raised to $T_{i}=72^{\circ} \mathrm{F}\( at a rate of \)2^{\circ} \mathrm{F}$ rise per minute. The heat transfer coefficients at the inner and outer surfaces of the wall can be taken to be \(h_{i}=1.2\) and $h_{o}=2.6 \mathrm{Btu} / \mathrm{h} \cdot \mathrm{ft}^{2}{ }^{\circ} \mathrm{F}$, respectively, and the outdoor temperature can be assumed to remain constant.

Consider an aluminum alloy fin $(k=180 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\( of triangular cross section whose length is \)L=5 \mathrm{~cm}$, base thickness is \(b=1 \mathrm{~cm}\), and width \(w\) in the direction normal to the plane of paper is very large. The base of the fin is maintained at a temperature of \(T_{0}=180^{\circ} \mathrm{C}\). The fin is losing heat by convection to the ambient air at \(T_{\infty}=25^{\circ} \mathrm{C}\) with a heat transfer coefficient of $h=25 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}$ and by radiation to the surrounding surfaces at an average temperature of \(T_{\text {sarr }}=290 \mathrm{~K}\). Using the finite difference method with six equally spaced nodes along the fin in the \(x\)-direction, determine \((a)\) the temperatures at the nodes and (b) the rate of heat transfer from the fin for \(w=1 \mathrm{~m}\). Take the emissivity of the fin surface to be \(0.9\) and assume steady onedimensional heat transfer in the fin. Answers: (a) \(177.0^{\circ} \mathrm{C}\), $174.1^{\circ} \mathrm{C}, 171.2^{\circ} \mathrm{C}, 168.4^{\circ} \mathrm{C}, 165.5^{\circ} \mathrm{C} ;\( (b) \)537 \mathrm{~W}$

Consider steady two-dimensional heat transfer in a square cross section $(3 \mathrm{~cm} \times 3 \mathrm{~cm})$ with the prescribed temperatures at the top, right, bottom, and left surfaces to be $100^{\circ} \mathrm{C}, 200^{\circ} \mathrm{C}, 300^{\circ} \mathrm{C}\(, and \)500^{\circ} \mathrm{C}$, respectively. Using a uniform mesh size \(\Delta x=\Delta y\), determine \((a)\) the finite difference equations and \((b)\) the nodal temperatures with the GaussSeidel iterative method.

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