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A hot brass plate is having its upper surface cooled by an impinging jet of air at a temperature of \(15^{\circ} \mathrm{C}\) and convection heat transfer coefficient of \(220 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\). The 10 -cm-thick brass plate $\left(\rho=8530 \mathrm{~kg} / \mathrm{m}^{3}, c_{p}=380 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}, k=110 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\right.\(, and \)\alpha=33.9 \times 10^{-6} \mathrm{~m}^{2} / \mathrm{s}$ ) had a uniform initial temperature of \(650^{\circ} \mathrm{C}\), and the lower surface of the plate is insulated. Using a uniform nodal spacing of \(\Delta x=2.5 \mathrm{~cm}\) and time step of \(\Delta t=10 \mathrm{~s}\), determine \((a)\) the implicit finite difference equations and \((b)\) the nodal temperatures of the brass plate after 10 seconds of cooling.

Short Answer

Expert verified
Question: Determine the nodal temperatures of the brass plate after 10 seconds of cooling using implicit finite difference equations for the given scenario. Answer: To find the nodal temperatures after 10 seconds, we need to follow these steps: 1. List down the given information, including material properties, geometry, and time step. 2. Discretize the heat conduction equation implicitly using the finite difference method. 3. Apply initial and boundary conditions to the discretized equation. 4. Create a system of equations for nodal temperatures. 5. Solve the system of equations for nodal temperatures after 10 seconds. By solving the system of equations, we will obtain the nodal temperatures of the brass plate after 10 seconds of cooling, i.e., temperatures at Node 1, Node 2, Node 3, and Node 4.

Step by step solution

01

List down given information

We are given the following information: - Air temperature: \(T_\infty = 15^\circ C\) - Convection heat transfer coefficient: \(h = 220\, W/(m^2 K)\) - Brass material properties: \(\rho = 8530\, kg/m^3\), \(c_p = 380\, J/(kg\cdot K)\), \(k = 110\, W/(m\cdot K)\) - Brass plate thickness and geometry: \(d = 10 \, cm\), \(\Delta x = 2.5\, cm\) - Time step: \(\Delta t = 10\, s\) - Initial temperature: \(T_0 = 650\,^{\circ}C\)
02

Discretize the heat conduction equation implicitly

The heat conduction equation is: \(\frac{\partial T}{\partial t} = \alpha \frac{\partial^2 T}{\partial x^2}\) Using implicit finite difference method, we approximate the equation as: \(\frac{T^{n+1}_i - T^n_i}{\Delta t} = \alpha \left(\frac{T^{n+1}_{i+1} - 2T^{n+1}_i + T^{n+1}_{i-1}}{(\Delta x)^2}\right) \) Rearranging the equation: \(T^{n+1}_{i} = T^{n}_{i} + \frac{\alpha\Delta t}{(\Delta x)^2}(T^{n+1}_{i+1} - 2T^{n+1}_i + T^{n+1}_{i-1}) \)
03

Apply initial and boundary conditions

Initial condition: The initial temperature of the brass plate is uniform and constant, \(T_i^n = T_0 = 650^{\circ} C\). Boundary conditions: 1. Upper surface (cooling by air impinging): Convection heat transfer, \(q(x=0, t) = h(T_0 - T_\infty)\) where \(T_0 = T^{n+1}_1\) 2. Lower surface (insulated): No heat loss, \(q(x=10cm, t) = 0\) which is equivalent to \(T^{n+1}_{i+1} = T^{n+1}_{i-1}\)
04

Create the system of equations for nodal temperatures

We consider 4 nodes with uniform spacing of \(\Delta_x = 2.5 cm\). Equation for node 1: \(T^{n+1}_{1} = T^{n}_{1} + \frac{\alpha\Delta t}{(\Delta x)^2}(T^{n+1}_{2}- 2T^{n+1}_1 + T^{n+1}_{0}) \) Using the boundary condition \(q(x=0, t) = h(T^{n+1}_1 - T_\infty)\) at node 1, we obtain \(T^{n+1}_{0} = 2\frac{T_\infty - T^{n+1}_1}{(2h\Delta x / k)} + T^{n+1}_1\) Equation for node 2: \(T^{n+1}_{2} = T^{n}_{2} + \frac{\alpha\Delta t}{(\Delta x)^2}(T^{n+1}_{3} - 2T^{n+1}_2 + T^{n+1}_{1})\) Equation for node 3: \(T^{n+1}_{3} = T^{n}_{3} + \frac{\alpha\Delta t}{(\Delta x)^2}(T^{n+1}_{4} - 2T^{n+1}_3 + T^{n+1}_{2})\) Using the boundary condition \(q(x=10\, cm, t) = 0\) at node 4, we obtain \(T^{n+1}_{4} = T^{n+1}_{2}\).
05

Solve the system for nodal temperatures after 10 seconds

We can now use the initial temperature and the equations from the previous step to solve for the nodal temperatures after 10 seconds, i.e. when \(n+1 = 1\). Temperature at all nodes initially \(T^n_i = 650 ^\circ C\). Substitute the initial temperatures and material properties into each equation and solve using any numerical method, like Gauss-Seidel Iterations or Tridiagonal matrix method to find: - \(T^{1}_1\) (Temperature at Node 1) - \(T^{1}_2\) (Temperature at Node 2) - \(T^{1}_3\) (Temperature at Node 3) - \(T^{1}_4\) (Temperature at Node 4) After solving the system of equations, we will obtain the nodal temperatures of the brass plate after 10 seconds of cooling.

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Most popular questions from this chapter

Consider transient 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 \(h\) and by radiation to the surrounding surfaces at an average temperature of \(T_{\text {surr }}\) 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 explicit finite difference formulation of this problem for the case of a specified temperature at the fin base and negligible heat transfer at the fin tip.

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.

A hot surface at \(120^{\circ} \mathrm{C}\) is to be cooled by attaching 8-cm- long, \(0.8-\mathrm{cm}\) - diameter aluminum pin fins ( $k=237 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\( and \)\left.\alpha=97.1 \times 10^{-6} \mathrm{~m}^{2} / \mathrm{s}\right)$ to it with a center-to-center distance of \(1.6 \mathrm{~cm}\). The temperature of the surrounding medium is $15^{\circ} \mathrm{C}\(, and the heat transfer coefficient on the surfaces is \)35 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}$. Initially, the fins are at a uniform temperature of \(30^{\circ} \mathrm{C}\), and at time \(t=0\), the temperature of the hot surface is raised to \(120^{\circ} \mathrm{C}\). Assuming one-dimensional heat conduction along the fin and taking the nodal spacing to be \(\Delta x=2 \mathrm{~cm}\) and a time step to be \(\Delta t=0.5 \mathrm{~s}\), determine the nodal temperatures after \(10 \mathrm{~min}\) by using the explicit finite difference method. Also, determine how long it will take for steady conditions to be reached.

A circular fin of uniform cross section, with diameter of \(10 \mathrm{~mm}\) and length of \(50 \mathrm{~mm}\), is attached to a wall with a surface temperature of \(350^{\circ} \mathrm{C}\). The fin is made of material with thermal conductivity of \(240 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\), it is exposed to an ambient air condition of \(25^{\circ} \mathrm{C}\), and the convection heat transfer coefficient is \(250 \mathrm{~W} / \mathrm{m}^{2}\). \(\mathrm{K}\). 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. (b) Determine the nodal temperatures along the fin by solving those equations, and compare the results with the analytical solution. (c) Calculate the heat transfer rate, and compare the result with the analytical solution.

In many engineering applications variation in thermal properties is significant, especially when there are large temperature gradients or the material is not homogeneous. To account for these variations in thermal properties, develop a finite difference formulation for an internal node in the case of a three-dimensional, steady-state heat conduction equation with variable thermal conductivity.

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