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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 \(\Delta x\). Using the energy balance approach, obtain the finite difference formulation of the boundary nodes for the case of insulation at the left boundary (node 0 ) and radiation at the right boundary (node 5) with an emissivity of \(\varepsilon\) and surrounding temperature of \(T_{\text {surr }}\)

Short Answer

Expert verified
Answer: The finite difference formulations for the boundary nodes are: For node 0 (insulation): \(T_1 = T_0 + \frac{Δx^2}{k}q_0\) For node 5 (radiation): \(T_5=\frac{εσΔx^2T^4_5+(kΔx^2+εσΔx^2T^4_{\text{surr}})T_4-q_5Δx^2}{kΔx^2+εσΔx^2T^4_5}\)

Step by step solution

01

Energy balance for insulation at node 0

Considering the left boundary node 0, which has insulation, no heat is allowed to transfer in or out of the boundary. The energy balance equation for the insulated boundary node 0 can be written as follows: \([\frac{k}{Δx^2}(T_1 - T_0)] - q_0 = 0\) Where: - \(k\) is the constant thermal conductivity - \(Δx\) is the nodal spacing - \(T_0\) and \(T_1\) are temperatures at nodes 0 and 1, respectively - \(q_0\) is the heat generation at node 0
02

Energy balance for radiation at node 5

Considering the right boundary node 5, which has radiation, the energy balance equation can be written as follows: \([\frac{k}{Δx^2}(T_4 - T_5)] - q_5 = εσ(T^4_5 - T^4_{\text{surr}})\) Where: - \(T_4\) and \(T_5\) are temperatures at nodes 4 and 5, respectively - \(q_5\) is the heat generation at node 5 - \(ε\) is the emissivity - \(σ\) is the Stefan-Boltzmann constant - \(T_{\text{surr}}\) is the surrounding temperature
03

Finite difference formulation for boundary nodes

Now, we can write the finite difference formulations for the boundary nodes by rearranging the energy balance equations from Steps 1 and 2: For node 0 (insulation): \(T_1 = T_0 + \frac{Δx^2}{k}q_0\) For node 5 (radiation): \(T_5=\frac{εσΔx^2T^4_5+(kΔx^2+εσΔx^2T^4_{\text{surr}})T_4-q_5Δx^2}{kΔx^2+εσΔx^2T^4_5}\) The finite difference formulation for the boundary nodes in the given heat conduction problem with insulation at node 0 and radiation at node 5 are derived as shown in the steps above. These formulations can be used to solve for the temperature at the boundary nodes given the material properties, heat generation, and surrounding temperature.

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Key Concepts

These are the key concepts you need to understand to accurately answer the question.

Heat Conduction
Heat conduction is the process of thermal energy transfer through a material without any movement of the material itself. Imagine heat flowing along a metal rod that you heat on one end. The heat moves from the hot end to the cold one. This flow happens due to temperature differences. Thermal energy transitions from high to low temperatures until balance is achieved.

For our exercise, we deal with heat conduction across a plane wall with constant thermal conductivity, described by a nodal network. Several nodes exist at defined intervals, known as nodal spacing \( \Delta x \). This spacing helps set up a framework for analyzing temperature variation throughout the wall. Keeping the thermal conductivity constant simulates real-world materials like metals, ensuring accurate calculations in our model.
Energy Balance
The energy balance approach is crucial for solving heat conduction problems. It involves accounting for energy entering and leaving a particular node, maintaining consistency throughout the system of nodes. For each node, the energy in must equal the energy out, unless there's energy generation or absorption.

In our specific problem statement, we formulate energy balance equations by inspecting each boundary. Heat forms generated aren’t transferred between nodes, oversees the heat produced or absorbed at each node, and helps design the balanced condition. Hence, formulating these equations for different boundaries becomes essential in determining the temperature distribution. This approach lets us use finite difference methods to map out how heat propagates through the wall.
Insulated Boundary
An insulated boundary is where no heat can pass through. In our problem, node 0 represents such a boundary.

Insulation implies that neither heat leaves nor enters the node. As a result, the energy balance for this node does not include any terms for heat transfer through the boundary. The derived equation \( \frac{k}{\Delta x^2}(T_1 - T_0) - q_0 = 0 \) simplifies to solving for the heat already within the node. This setup is common in real-world applications where engineers want to prevent energy loss through materials, such as in building insulation or thermal garments, helping maintain internal temperatures effectively.
Radiative Boundary
Radiative boundaries incorporate heat exchange through radiation, one of the modes of heat transfer distinct from conduction or convection. Unlike an insulated boundary, this allows heat transfer utilizing the surrounding environment.

The problem's node 5 is a radiative boundary, modeled by the equation \( \frac{k}{\Delta x^2}(T_4 - T_5) - q_5 = \varepsilon \sigma (T^4_5 - T^4_{\text{surr}}) \). Here, emissivity \( \varepsilon \) and the Stefan-Boltzmann constant \( \sigma \) determine the radiative heat loss to surroundings. The term \( T^4_{\text{surr}} \) represents the fourth power of the surrounding temperature, indicating radiation's dependency on temperature differences and physical properties. This concept is pivotal in designing systems like radiators or solar panels, where thermal radiation directly affects efficiency.

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Most popular questions from this chapter

A circular fin \((k=240 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\) of uniform cross section, with diameter of \(10 \mathrm{~mm}\) and length of \(50 \mathrm{~mm}\), is attached to a wall with surface temperature of \(350^{\circ} \mathrm{C}\). The fin tip has a temperature of \(200^{\circ} \mathrm{C}\), and it is exposed to ambient air condition of \(25^{\circ} \mathrm{C}\) and the convection heat transfer coefficient is \(250 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\). Assume steady one-dimensional heat transfer along the fin and the nodal spacing to be uniformly \(10 \mathrm{~mm}\), (a) using the energy balance approach, obtain the finite difference equations to determine the nodal temperatures, and (b) determine the nodal temperatures along the fin by solving those equations and compare the results with the analytical solution.

Consider steady two-dimensional heat transfer in a long solid bar \((k=25 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\) of 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. Heat is generated in the bar uniformly at a rate of \(\dot{e}=5 \times 10^{6} \mathrm{~W} / \mathrm{m}^{3}\). Using a uniform mesh size \(\Delta x=\Delta y=1 \mathrm{~cm}\) determine \((a)\) the finite difference equations and \((b)\) the nodal temperatures with the Gauss-Seidel iterative method.

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 transient heat conduction in a plane wall whose left surface (node 0 ) is maintained at \(50^{\circ} \mathrm{C}\) while the right surface (node 6) is subjected to a solar heat flux of \(600 \mathrm{~W} / \mathrm{m}^{2}\). The wall is initially at a uniform temperature of \(50^{\circ} \mathrm{C}\). Express the explicit finite difference formulation of the boundary nodes 0 and 6 for the case of no heat generation. Also, obtain the finite difference formulation for the total amount of heat transfer at the left boundary during the first three time steps.

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

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