How does the finite difference formulation of a transient heat conduction problem differ from that of a steady heat conduction problem? What does the term \(\rho A \Delta x c_{p}\left(T_{m}^{i+1}-T_{m}^{i}\right) / \Delta t\) represent in the transient finite difference formulation?

Short Answer

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In summary, steady heat conduction problems involve a constant temperature distribution, while transient heat conduction problems involve a time-varying temperature distribution. The finite difference formulation for these problems is based on the governing equation of heat conduction, and it differs between steady and transient problems due to the presence of a time derivative in the transient case. The term \(\rho A \Delta x c_{p}\left(T_{m}^{i+1}-T_{m}^{i}\right) / \Delta t\) in the transient finite difference formulation represents the change in internal energy (heat stored) of a control volume over a time step.

Step by step solution

01

Steady vs. Transient Heat Conduction

In steady heat conduction problems, the temperature distribution does not change with time, and the heat flow reaches a steady-state condition. On the other hand, in transient heat conduction problems, the temperature distribution changes with time, and the heat flow depends on the time-varying temperature distribution.
02

Finite Difference Formulation in Steady and Transient Heat Conduction

The governing equation for heat conduction can be written as \( \rho c_{p}\frac{\partial{T}}{\partial{t}} = k \nabla^2 T + S\) Where \(\rho\) is the material's density, \(c_{p}\) is its specific heat capacity, \(k\) is its thermal conductivity, \(T\) is temperature, \(t\) is time, and \(S\) is the heat source. Finite difference formulations for both steady and transient heat conduction problems are derived from this governing equation. In the steady heat conduction problem, as the temperature distribution is time-independent, the left side of the governing equation becomes zero: \(0 = k \nabla^2 T + S\) The finite difference formulation will involve discretizing the Laplace operator (\(\nabla^2 T\)) in space using finite difference approximations. In the transient heat conduction problem, the left side of the equation is non-zero due to the time-varying temperature distribution. Thus, the governing equation is: \( \rho c_{p}\frac{\partial{T}}{\partial{t}} = k \nabla^2 T + S\) The finite difference formulation will involve discretizing both the Laplace operator in space and the time derivative of temperature using finite difference approximations.
03

Meaning of the Term \(\rho A \Delta x c_{p}\left(T_{m}^{i+1}-T_{m}^{i}\right) / \Delta t\)

In the context of transient finite difference formulation, the term \(\rho A \Delta x c_{p}\left(T_{m}^{i+1}-T_{m}^{i}\right) / \Delta t\) represents the change in internal energy (heat stored) of a control volume over a time step. Here, \(\rho\) is the density, \(A\) is the cross-sectional area, \(\Delta x\) is the control volume's length, and \(c_{p}\) is the specific heat capacity of the material, \((T_{m}^{i+1}-T_{m}^{i})\) is the change in temperature of the control volume from time step \(i\) to \(i+1\), and \(\Delta t\) is the time step.

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Key Concepts

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

Finite Difference Formulation
Understanding how engineers and scientists predict temperature variations in objects over time is crucial, particularly when dealing with heat transfer problems. This is where the finite difference formulation comes into play. The method approximates differential equations of continuum models using a discrete set of points, thereby translating the problem into a set of algebraic equations that can be solved numerically.

Specifically, in the context of heat conduction, the partial differential equation that governs the heat transfer is discretized using finite difference approximations. This involves taking the continuous domain and breaking it into a finite number of points where the temperature is to be calculated. For steady heat conduction, the temperature at a point in space is influenced by neighboring points and is independent of time, while for transient conditions, temperature values change with time and the formulation must account for this temporal variation.

In essence, the finite difference formulation transforms the complicated mathematical model into a more tractable form that can be solved using computers, and it's a powerful tool in thermal analysis for a wide range of applications.
Steady Heat Conduction
Now, let's talk about steady heat conduction. This phenomenon occurs when the temperature in a material doesn't change with time, meaning that after a certain period, the thermal equilibrium has been achieved, and the heat entering any region of the material equals the heat leaving it.

For instance, think of a metal rod with one end held in a flame. Initially, the rod heats up, but after a while, the temperature along the rod stabilizes and doesn’t fluctuate—this is steady state. Mathematically, there is no time derivative in the governing heat conduction equation for steady state, simplifying the analysis significantly since the temperature distribution is only a function of position.

An advantage of achieving steady state in heat conduction analysis is that it allows for the design of systems where a constant temperature is desired or predictable behavior is important, such as in building design or electronic systems.
Internal Energy Change
When we delve into transient heat conduction, the concept of internal energy change becomes essential. This represents the amount of energy stored or released within a material as it undergoes temperature changes over time.

The term \(\rho A \Delta x c_{p}\left(T_{m}^{i+1}-T_{m}^{i}\right) / \Delta t\) encapsules this idea. Each variable corresponds to physical properties that contribute to how heat energy is absorbed or dissipated. Heat storage within a volume is derived from its density (\(\rho\)), specific heat capacity (\(c_p\)), size (via cross-sectional area (\(A\)) and length (\(\Delta x\))), and the rate of temperature change with respect to time (\(\Delta t\)).

Understanding internal energy change is vital for transient analyses as it influences how a material’s temperature will evolve, affecting everything from structural integrity to thermal comfort in engineered designs.
Temperature Distribution
Lastly, let’s examine temperature distribution. This refers to how temperature varies within a material or system and is affected by the material's properties and the external conditions imposed on it, such as boundary temperatures, heat sources, and environment.

Temperature distribution is a critical concept in both steady and transient heat conduction because it directly relates to how heat transfers within a material and dictates whether the material's structural and functional integrity is maintained. Engineers have to calculate the temperature distribution carefully to ensure that components can withstand operational stresses over time.

For steady-state problems, the temperature distribution is stationary, and for transient problems, it changes dynamically with time. Therefore, accurately predicting temperature distribution is not only key to ensuring the effective operation of thermal systems but also to maintaining safety and reliability.

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Most popular questions from this chapter

Consider steady two-dimensional heat transfer in a rectangular cross section \((60 \mathrm{~cm} \times 30 \mathrm{~cm})\) with the prescribed temperatures at the left, right, and bottom surfaces to be \(0^{\circ} \mathrm{C}\), and the top surface is given as \(100 \sin (\pi x / 60)\). Using a uniform mesh size \(\Delta x=\Delta y\), determine (a) the finite difference equations and \((b)\) the nodal temperatures.

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 Gauss-Seidel iterative method.

Starting with an energy balance on the volume element, obtain the three- dimensional transient explicit finite difference equation for a general interior node in rectangular coordinates for \(T(x, y, z, t)\) for the case of constant thermal conductivity and no heat generation.

Consider steady heat conduction in a plane wall with variable heat generation and constant thermal conductivity. The nodal network of the medium consists of nodes \(0,1,2,3\), and 4 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 uniform heat flux \(\dot{q}_{0}\) at the left boundary (node 0 ) and convection at the right boundary (node 4) with a convection coefficient of \(h\) and an ambient temperature of \(T_{\infty}\).

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 surface temperature of \(350^{\circ} \mathrm{C}\). The fin is made of material with thermal conductivity of \(240 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\), and it is exposed to an ambient air condition of \(25^{\circ} \mathrm{C}\) and the convection heat transfer coefficient is \(250 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\). 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, \((b)\) determine the nodal temperatures along the fin by solving those equations and compare the results with the analytical solution, and (c) calculate the heat transfer rate and compare the result with the analytical solution.

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