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A stainless steel plate $(k=13 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}, 1 \mathrm{~cm}\( thick) is attached to an ASME SB-96 coppersilicon plate ( \)k=36 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}, 3 \mathrm{~cm}$ thick) to form a plane wall. The bottom surface of the ASME SB-96 plate (surface 1) is subjected to a uniform heat flux of \(750 \mathrm{~W} / \mathrm{m}^{2}\). The top surface of the stainless steel plate (surface 2 ) is exposed to convection heat transfer with air at \(T_{\infty}=20^{\circ} \mathrm{C}\), and thermal radiation with the surroundings at \(T_{\text {surr }}=20^{\circ} \mathrm{C}\). The combined heat transfer coefficient for convection and radiation is \(h_{\mathrm{comb}}=7.76 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\). The ASME Boiler and Pressure Vessel Code (ASME BPVC.IV-2015, HF-300) limits equipment constructed with ASME SB-96 plate to be operated at a temperature not exceeding \(93^{\circ} \mathrm{C}\). Using the finite difference method with a uniform nodal spacing of \(\Delta x=5 \mathrm{~mm}\) along the plate thicknesses, determine the temperature at each node. Would the use of the ASME SB-96 plate under these conditions be in compliance with the ASME Boiler and Pressure Vessel Code? What is the highest heat flux that the bottom surface can be subjected to such that the ASME SB-96 plate is still operating below \(93^{\circ} \mathrm{C}\) ?

Short Answer

Expert verified
Question: Determine the temperature at each node using the finite difference method and check if the temperature does not exceed the limit specified by the ASME code for the first plate. Also, find the highest heat flux that keeps the temperature below the limit.

Step by step solution

01

Set up the equation for the finite difference method

First, we need to apply the finite difference method to the one-dimensional heat conduction equation: $$ q = -k \frac{dT}{dx}, $$ where \(q\) is the heat flux, \(k\) is the thermal conductivity, \(T\) is the temperature, and \(x\) is the distance along the plate thickness. For the nth node, we can approximate the temperature change by using a central difference scheme: $$ \frac{T_{n + 1} - 2T_n + T_{n - 1}}{\Delta x^2}, $$ where \(T_n\) is the temperature at the nth node.
02

Apply boundary conditions

We have two boundary conditions: one at the bottom surface of the first plate, where \(q_1 = 750 W/m^2\) and another one at the top surface of the second plate, where the heat flux is due to both convection and radiation. For the convection and radiation heat transfer, the heat flux at the top surface can be written as: $$ q_2 = h_{comb}(T_2 - T_{\infty}), $$ where \(h_{comb} = 7.76 W/m^2 K\) and \(T_{\infty} = T_{surr} = 20^{\circ} C\).
03

Create equations for each node

Now that we have our difference equation and boundary conditions, we can create equations for each node in the system by applying the difference equation to each plate separately. For each plate, we use the respective thermal conductivity, \(k\), in the equation. Write the equations in matrix form. Denote the nodal temperature in the stainless steel plate with \(T_n^s\) and the nodal temperature in the ASME SB-96 plate with \(T_n^c\), with \(n = 1, 2, 3\), as \(\Delta x = 5 mm\) for both plates.
04

Solve the system of equations

Once the equations are set up in a matrix form, use either a numerical method or a software tool to solve for the unknown nodal temperatures, \(T_n^s\) and \(T_n^c\). This will give the temperature profile across both plates.
05

Check compliance with the ASME code

Now that we have the temperature profile across the plates, assess if the temperature at the first plate (ASME SB-96 plate) does not exceed the temperature limit of \(93^{\circ} C\) specified by the ASME code. If all the nodal temperatures of the first plate are below this limit, then the plate is in compliance with the code.
06

Determine the highest heat flux

To find the highest heat flux that the bottom surface can be subjected to while having a temperature of \(93^{\circ} C\) at the ASME SB-96 plate, we can either use trial and error or a numerical method. Repeat steps 1-5 with different heat flux values until we find the highest heat flux that keeps the ASME SB-96 plate at a temperature below \(93^{\circ} C\).

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Most popular questions from this chapter

A nonmetal plate \((k=0.05 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\) is attached on the upper surface of an ASME SB-96 copper-silicon plate $(k=36 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})$. The nonmetal plate and the ASME SB-96 plate have thicknesses of \(20 \mathrm{~mm}\) and \(30 \mathrm{~mm}\), respectively. The bottom surface of the ASME SB-96 plate (surface 1) is subjected to a uniform heat flux of \(150 \mathrm{~W} / \mathrm{m}^{2}\). The top nonmetal plate surface (surface 2) is exposed to convection at an air temperature of \(15^{\circ} \mathrm{C}\) and a convection heat transfer coefficient of \(5 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\). Copper- silicon alloys are not always suitable for applications where they are exposed to certain median and high temperatures. Therefore, the ASME Boiler and Pressure Vessel Code (ASME BPVC.IV-2015, HF-300) limits equipment constructed with ASME SB-96 plate to be operated at a temperature not exceeding \(93^{\circ} \mathrm{C}\). Using the finite difference method with a uniform nodal spacing of \(\Delta x=5 \mathrm{~mm}\) along the the temperature distribution as a function of \(x\). Would the use of the ASME SB- 96 plate under these conditions be in compliance with the ASME Boiler and Pressure Vessel Code? What is the lowest value of the convection heat transfer coefficient for the air so that the ASME SB-96 plate is below $93^{\circ} \mathrm{C}$ ?

A series of long stainless steel bolts (ASTM A437 B4B) are fastened into a metal plate with a thickness of \(4 \mathrm{~cm}\). The bolts have a thermal conductivity of \(23.9 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\), a specific heat of \(460 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\), and a density of \(7.8 \mathrm{~g} / \mathrm{cm}^{3}\). For the metal plate, the specific heat, thermal conductivity, and density are $500 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}, 16.3 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\(, and \)8 \mathrm{~g} / \mathrm{cm}^{3}$, respectively. The upper surface of the plate is occasionally exposed to cryogenic fluid at \(-70^{\circ} \mathrm{C}\) with a convection heat transfer coefficient of $300 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}$. The lower surface of the plate is exposed to convection with air at \(10^{\circ} \mathrm{C}\) and a convection heat transfer coefficient of \(10 \mathrm{~W} / \mathrm{m}^{2}\). K. The bolts are fastened into the metal plate from the bottom surface, and the distance measured from the plate's upper surface to the bolt tips is \(1 \mathrm{~cm}\). The ASME Code for Process Piping limits the minimum suitable temperature for ASTM A437 B4B stainless steel bolt to \(-30^{\circ} \mathrm{C}\) (ASME B31.3-2014, Table A-2M). If the initial temperature of the plate is \(10^{\circ} \mathrm{C}\) and the plate's upper surface is exposed to the cryogenic fluid for \(9 \mathrm{~min}\), would the bolts fastened in the plate still comply with the ASME code? Using the explicit finite difference formulations with a uniform nodal spacing of \(\Delta x=1 \mathrm{~cm}\), determine the temperature at each node for the duration of the upper surface being exposed to the cryogenic fluid. Plot the nodal temperatures as a function of time.

Consider transient heat conduction in a plane wall whose left surface (node 0 ) is maintained at \(80^{\circ} \mathrm{C}\) 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.

The finite difference formulation of steady two-dimensional heat conduction in a medium with heat generation and constant thermal conductivity is given by $$ \begin{gathered} \frac{T_{m-1, n}-2 T_{m, n}+T_{m+1, n}}{\Delta x^{2}}+\frac{T_{m, n-1}-2 T_{m, n}+T_{m, n+1}}{\Delta y^{2}} \\ +\frac{\dot{e}_{m, n}}{k}=0 \end{gathered} $$ in rectangular coordinates. Modify this relation for the threedimensional case.

How is an insulated boundary handled in the finite difference formulation of a problem? How does a symmetry line differ from an insulated boundary in the finite difference formulation?

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