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Explain how the finite difference form of a heat conduction problem is obtained by the energy balance method.

Short Answer

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Answer: The finite difference form of the heat conduction problem derived using the energy balance method is: \begin{equation} \frac{\partial T_i}{\partial t} = \alpha \left( \frac{T_{i+1} - 2T_i + T_{i-1}}{\Delta x^2} \right) \end{equation} where \(T_i\) is the temperature at position \(x_i\) and time \(t\), \(\alpha\) is the thermal diffusivity, and \(\Delta x\) is the length of a small control volume.

Step by step solution

01

Understand the Heat Conduction Equation

The heat conduction equation, also known as the heat equation or diffusion equation, describes the heat transfer through a material. In one dimension, it is given by: \begin{equation} \frac{\partial T(x,t)}{\partial t} = \alpha \frac{\partial^2 T(x,t)}{\partial x^2} \end{equation} where \(T(x,t)\) is the temperature at position \(x\) and time \(t\), and \(\alpha\) is the thermal diffusivity of the material, which is a constant.
02

Apply the Energy Balance Method

The energy balance method states that the rate of change of thermal energy in a control volume is equal to the rate at which heat enters the control volume minus the rate at which heat leaves the control volume. In the context of the heat conduction problem, we consider a small control volume with a length \(\Delta x\) in our one-dimensional problem. Let the heat entering and leaving the control volume be \(Q_{in}\) and \(Q_{out}\), respectively. Then, the energy balance equation can be written as: \begin{equation} \frac{\partial T}{\partial t} \Delta x = - (Q_{out} - Q_{in}) \end{equation}
03

Calculate Heat Fluxes

Next, we need to determine the heat flux entering and leaving the control volume. For this, we use Fourier's law of heat conduction, which states: \begin{equation} q = -k \frac{\partial T}{\partial x} \end{equation} where \(q\) is the heat flux, and \(k\) is the thermal conductivity of the material. For the control volume, the heat fluxes can be written as: \begin{align} Q_{in} = -k \frac{\partial T}{\partial x} \Big|_{x = x_i - \frac{\Delta x}{2}} \\ Q_{out} = -k \frac{\partial T}{\partial x} \Big|_{x = x_i + \frac{\Delta x}{2}} \end{align} Here, \(x_i\) denotes the position of the center of the control volume.
04

Discretize the Equation using Finite Difference Approximation

To obtain the finite difference form of the heat conduction problem, we need to discretize the spatial derivatives using finite difference approximations. For the heat fluxes, we use the central difference approximation, which gives: \begin{align} \frac{\partial T}{\partial x} \Big|_{x = x_i - \frac{\Delta x}{2}} \approx \frac{T_{i-1} - T_i}{\Delta x} \\ \frac{\partial T}{\partial x} \Big|_{x = x_i + \frac{\Delta x}{2}} \approx \frac{T_i - T_{i+1}}{\Delta x} \end{align} Substituting these approximations into the expressions for \(Q_{in}\) and \(Q_{out}\), we get: \begin{align} Q_{in} = k \frac{T_{i-1} - T_i}{\Delta x} \\ Q_{out} = k \frac{T_i - T_{i+1}}{\Delta x} \end{align} Now, substituting the heat fluxes back into the energy balance equation, we have: \begin{equation} \frac{\partial T_i}{\partial t} \Delta x = - k (T_i - T_{i+1} - T_{i-1} + T_i) \end{equation} Finally, divide both sides of the equation by \(\Delta x\), and substitute the thermal diffusivity \(\alpha = k/\rho c_p\), where \(\rho\) is the material density and \(c_p\) is the specific heat capacity, to obtain the finite difference form: \begin{equation} \frac{\partial T_i}{\partial t} = \alpha \left( \frac{T_{i+1} - 2T_i + T_{i-1}}{\Delta x^2} \right) \end{equation} This is the finite difference form of the heat conduction problem derived using the energy balance method.

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Most popular questions from this chapter

How can a node on an insulated boundary be treated as an interior node in the finite difference formulation of a plane wall? Explain.

The explicit finite difference formulation of a general interior node for transient heat conduction in a plane wall is given by $$ T_{m=1}^{i}-2 T_{m}^{i}+T_{m+1}^{i}+\frac{e_{m}^{i} \Delta x^{2}}{k}=\frac{T_{m}^{i+1}-T_{m}^{i}}{\tau} $$ Obtain the finite difference formulation for the steady case by simplifying the preceding relation.

Design a defrosting plate to speed up defrosting of flat food items such as frozen steaks and packaged vegetables, and evaluate its performance using the finite difference method. Compare your design to the defrosting plates currently available on the market. The plate must perform well, and it must be suitable for purchase and use as a household utensil, durable, easy to clean, easy to manufacture, and affordable. The frozen food is expected to be at an initial temperature of \(-18^{\circ} \mathrm{C}\) at the beginning of the thawing process and \(0^{\circ} \mathrm{C}\) at the end with all the ice melted. Specify the material, shape, size, and thickness of the proposed plate. Justify your recommendations by calculations. Take the ambient and surrounding surface temperatures to be \(20^{\circ} \mathrm{C}\) and the convection heat transfer coefficient to be \(15 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) in your analysis. For a typical case, determine the defrosting time with and without the plate.

Consider steady one-dimensional heat conduction in a plane wall with variable heat generation and constant thermal conductivity. The nodal network of the medium consists of nodes \(0,1,2,3,4\), and 5 with a uniform nodal spacing of \(\Delta x\). The temperature at the right boundary (node 5) is specified. Using the energy balance approach, obtain the finite difference formulation of the boundary node 0 on the left boundary for the case of combined convection, radiation, and heat flux at the left boundary with an emissivity of \(\varepsilon\), convection coefficient of \(h\), ambient temperature of \(T_{\infty}\), surrounding temperature of \(T_{\text {surr }}\) and uniform heat flux of \(\dot{q}_{0}\). Also, obtain the finite difference formulation for the rate of heat transfer at the right boundary.

Consider a large plane wall of thickness \(L=0.3 \mathrm{~m}\), thermal conductivity \(k=1.8 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\), and surface area \(A=24 \mathrm{~m}^{2}\). The left side of the wall is subjected to a heat flux of \(\dot{q}_{0}=350 \mathrm{~W} / \mathrm{m}^{2}\), while the temperature at that surface is measured to be \(T_{0}=60^{\circ} \mathrm{C}\). Assuming steady one-dimensional heat transfer and taking the nodal spacing to be $6 \mathrm{~cm},(a)$ obtain the finite difference formulation for the six nodes and \((b)\) determine the temperature of the other surface of the wall by solving those equations.

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