/*! This file is auto-generated */ .wp-block-button__link{color:#fff;background-color:#32373c;border-radius:9999px;box-shadow:none;text-decoration:none;padding:calc(.667em + 2px) calc(1.333em + 2px);font-size:1.125em}.wp-block-file__button{background:#32373c;color:#fff;text-decoration:none} Problem 77 A very thick slab with thermal d... [FREE SOLUTION] | 91Ó°ÊÓ

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A very thick slab with thermal diffusivity \(5.6 \mathrm{x}\) \(10^{-6} \mathrm{~m}^{2} / \mathrm{s}\) and thermal conductivity \(20 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\) is ini tially at a uniform temperature of \(325^{\circ} \mathrm{C}\). Sudklenly, tte surface is exposed to a ccolant at \(15^{\circ} \mathrm{C}\) for which the convection heat transfer coefficient is \(100 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\). (a) Determine temperatures at the surface and at a depth of \(45 \mathrm{~mm}\) after 3 min have elapsed. (b) Compute and plot temperature histories \((0 \leq t \leq\) \(3(x)\) s) at \(x=0)\) and \(x=45 \mathrm{~mm}\) for the following parametric variations: (i) \(\alpha=5.6 \times 10^{-7} .5 .6 \times\) \(10^{-6}\), and \(5.6 \times 10^{-3} \mathrm{~m}^{2} / \mathrm{s}\); and (ii) \(k=2,20\), and \(200 \mathrm{~W} / \mathrm{m}-\mathrm{K}\).

Short Answer

Expert verified
Surface temperature is 15°C; temperature at 45mm is computed using the error function and varies with parameters.

Step by step solution

01

Determine the Block Parameters

We have thermal diffusivity \(\alpha = 5.6 \times 10^{-6} \text{ m}^2/\text{s}\), thermal conductivity \(k = 20 \text{ W/m} \cdot \text{K}\), initial slab temperature \(T_i = 325^\circ \text{C}\), surface coolant temperature \(T_\infty = 15^\circ \text{C}\), and convection heat transfer coefficient \(h = 100 \text{ W/m}^2 \cdot \text{K}\). The slab thickness \(L\) is very large, and we need to find temperatures after \(t = 3 \times 60 = 180\) seconds.
02

Calculate Biot Number

The Biot number \(Bi\) determines the appropriateness of different heat transfer solutions. Use \(Bi = \frac{h L}{k}\). Since \(L\) is large, the assumption of a semi-infinite wall is applicable, especially since \(Bi \gg 0.1\), enabling use of the error function solution for semi-infinite solids.
03

Use the Error Function Solution

For a semi-infinite solid, the temperature \(T(x, t)\) at depth \(x\) and time \(t\) is given by:\[ T(x,t) = T_\infty + (T_i - T_\infty) \text{erf}\left( \frac{x}{2\sqrt{\alpha t}} \right) \]where the error function is based on depth \(x\) and time \(t\): \(\text{erf}(z) = \text{error function}(z)\).
04

Calculate Surface Temperature

Set \(x=0\) for the surface temperature calculation:\[ T(0, 180) = 15 + (325 - 15) \times \text{erf}(0) \]Since \(\text{erf}(0) = 0\), it simplifies to:\[ T(0, 180) = 15^\circ \text{C} \].
05

Calculate Temperature at 45mm Depth

For \(x = 0.045 \text{ m}\), use:\[ T(0.045, 180) = 15 + (325 - 15) \times \text{erf}\left( \frac{0.045}{2\sqrt{5.6 \times 10^{-6} \times 180}} \right) \]Calculate the argument for the error function and determine \(\text{erf}\left(\frac{0.045}{2 \times 0.01}\right)\) from standard tables.
06

Vary Parameters and Plot

For different values of \(\alpha\) and \(k\), repeat steps 3 to 5. Consider new scenarios with parameters: (i) \(\alpha = 5.6 \times 10^{-7}, 5.6 \times 10^{-6}, 5.6 \times 10^{-3} \text{ m}^2/\text{s}\)(ii) \(k = 2, 20, 200 \text{ W/m} \cdot \text{K}\)Use these values to recompute and plot \(T(0, t)\) and \(T(0.045, t)\) from \(t = 0\) to \(t = 180\) seconds using the same formula structure for error function temperatures.

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Key Concepts

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

Thermal Diffusivity
Thermal diffusivity is a property of materials that measures how quickly heat spreads through an object. In simpler terms, it determines the speed at which a material heats up or cools down. It is particularly crucial when analyzing the heat conduction of a material. The units of thermal diffusivity are square meters per second (m²/s). Thermal diffusivity is calculated using the formula \( \alpha = \frac{k}{\rho c_p} \), where:
  • \( k \) is the thermal conductivity
  • \( \rho \) is the density of the material
  • \( c_p \) is the specific heat capacity
In practical applications, a high thermal diffusivity means a material will rapidly adjust its temperature. Meanwhile, a low thermal diffusivity indicates a slow temperature change. Understanding thermal diffusivity helps us determine how a material reacts to temperature changes, which is essential in designing heating and cooling systems.
Biot Number
The Biot number (Bi) is a dimensionless number that compares internal conduction resistance within a body to the convection resistance at the surface of the body. It helps us decide the type of heat conduction problem we're dealing with. The Biot number is given by the formula: \( Bi = \frac{hL}{k} \), where:
  • \( h \) is the convection heat transfer coefficient
  • \( L \) is the characteristic length of the object
  • \( k \) is the thermal conductivity
A small Biot number (\( Bi < 0.1 \)) suggests that temperature within the object is uniform and can be treated as a lumped system, which means simpler mathematical models can be used. For large objects or when \( Bi > 0.1 \), the temperature gradient within the body is significant enough to consider more detailed models like semi-infinite solid approximations.
Error Function Solution
The error function solution is a crucial part of solving heat conduction problems, especially when dealing with semi-infinite solids, like very thick slabs. This function helps us determine the temperature at a specific depth and time after a sudden change at the surface.The error function, denoted as \( \text{erf}(z) \), is a special mathematical function often used in diffusion problems. For heat conduction, the temperature \( T(x,t) \) at depth \( x \) and time \( t \) can be calculated by:\[ T(x, t) = T_{\infty} + (T_i - T_{\infty}) \times \text{erf}\left( \frac{x}{2\sqrt{\alpha t}} \right) \]Where:
  • \( T_{\infty} \) is the coolant temperature
  • \( T_i \) is the initial temperature of the body
  • \( \alpha \) is the thermal diffusivity
The error function value varies between -1 and 1, reflecting how far the temperature has reached through the material at any given time.
Convection Heat Transfer Coefficient
The convection heat transfer coefficient (h) is a measure of how effective a fluid is at transferring heat through convection. It describes the thermal boundary layer between a solid surface and a moving fluid.The value of \( h \) depends on several factors:
  • Type of fluid (air, water, etc.)
  • Flow characteristics (laminar or turbulent)
  • Surface roughness
  • Fluid velocity
In many practical applications, determining the correct \( h \) value is crucial for designing energy-efficient systems. It is also used to calculate the Biot number, which, as mentioned earlier, helps in analyzing heat transfer problems. The unit is typically \( \text{W/m}^2 \cdot \text{K} \), describing energy transfer per unit area per degree of temperature difference.

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Most popular questions from this chapter

Spheres \(\mathrm{A}\) and \(\mathrm{B}\) are initially at \(800 \mathrm{~K}\), and they are simultancously quenched in large constant temperature baths. each having a temperature of \(320 \mathrm{~K}\). The follow. ing parameters are associated with each of the spheres and their cooling processes. $$ \begin{array}{lcc} & \text { Sphere A } & \text { Sphere B } \\ \hline \text { Diameter }(\mathrm{mm}) & 300 & 30 \\ \text { Density }\left(\mathrm{kg} / \mathrm{m}^{2}\right) & 1600 & 400 \\ \text { Specific heat }(\mathrm{N} / \mathrm{kg} \cdot \mathrm{K}) & 0.400 & 1.60 \\ \text { Thermal conductivity }(\mathrm{W} / \mathrm{m} \cdot \mathrm{K}) & 170 & 1.70 \\ \text { Convection coefficient }\left(\mathrm{W} / \mathrm{m}^{2}-\mathrm{K}\right) & 5 & 50 \\ \hline \end{array} $$ (a) Show in a qualitative manner, on \(T\) versus \(t\) coordinates, the temperatures at the center and at the surface for each sphere as a function of time. Briefly explain the reasening by which you determine the relative positions of the curves, (b) Calculate the time required for the surface of each sphere to reach \(415 \mathrm{~K}\). (c) Determine the energy that has been gained by each of the baths during the process of the spheres cooling to \(415 \mathrm{~K}\).

Consider a thin electrical heater artached to a plate and hacked by insulation. Initially, the heater and plate are at the temperafure of the ambient air, \(T\) - Suddenly, the power to the heater is activated, yielding a constant heat fux \(q_{e}^{*}\left(\mathrm{~W} / \mathrm{m}^{2}\right)\) at the inner surface of the plate. (a) Sketch and label, on \(T-x\) cocrdinates, the temperature distributions: initial, steady-state, and at two intermediate times. (b) Sketch the heat flux at the outer surface \(q_{z}^{\prime \prime}(L, t)\) as a function of time.

A cold air chamber is proposed for quenching steel ball bearings of dinmeter \(D=0.2 \mathrm{~m}\) and initial temperature \(T_{i}=400^{\circ} \mathrm{C}\). Air in the chamber is maintained at \(-15^{\circ} \mathrm{C}\) by a refrigeration system, and the steel balls pass through the chamber on a conveyor belt. Optimum bearing production requires that \(70 \%\) of the initial thermal energy content of the ball above \(-15^{\circ} \mathrm{C}\) be removed. Radiation effects muy be neglected, and the convection heut transfer coefficient within the chamber is \(1000 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\). Estimute the residence time of the balls within the chamber, und recommend a drive velocity of the conveyor. The following properties may be used for the steel: \(k=50 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}, \alpha=2 \times 10^{-3} \mathrm{~m}^{2} / \mathrm{s}\), and \(c=450 \mathrm{~J} / \mathrm{kg}-\mathrm{K}\).

A long wire of diameter \(D=1 \mathrm{~mm}\) is submerged it an oil bath of temperature \(T_{s}=25^{\circ} \mathrm{C}\). The wire has at electrical resistance per unit length of \(R_{e}^{2}=0.01 \mathrm{f} \mathrm{Nm}\) If a current of \(I=100 \mathrm{~A}\) flows throegh the wirt and the convection coefficient is \(h=500 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\). what is the steady-state temperature of the wire? From the time the current is applied, how long does it take for the wire to reach a temperature that is within \(1^{\circ} \mathrm{C}\) of the steady-state value? The properties of the wire are \(\rho\) a \(8000 \mathrm{~kg} / \mathrm{m}^{3}, c=500 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\), and \(\mathrm{k}=20 \mathrm{~W} / \mathrm{m}-\mathrm{K}\).

The inner surface of a plane wall is insulated while the cuter surface is exposed to an airstream at \(T_{\text {a }}\). The wall is af a uniform temperature corresponding to that of the ainstream, Sudilenly, a radiation heat source is switched cn applying a uniform fiux \(q_{e}^{*}\) to the outer surface. (a) Shetch and label, on \(T-x\) coordinates, the temperature distributions: initial, steady-state, and at two intermediate times. (b) Sketch the heat flux at the outer surface \(q_{,}^{\prime \prime}\left(L_{n} t\right)\) as a function of time.

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