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Consider a refrigerator whose outer dimensions are $1.80 \mathrm{~m} \times 0.8 \mathrm{~m} \times 0.7 \mathrm{~m}$. The walls of the refrigerator are constructed of \(3-\mathrm{cm}\)-thick urethane insulation $(k=0.026 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\( and \)\alpha=0.36 \times 10^{-6} \mathrm{~m}^{2} / \mathrm{s}$ ) sandwiched between two layers of sheet metal with negligible thickness. The refrigerated space is maintained at \(3^{\circ} \mathrm{C}\), and the average heat transfer coefficients at the inner and outer surfaces of the wall are \(6 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) and $9 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}$, respectively. Heat transfer through the bottom surface of the refrigerator is negligible. The kitchen temperature remains constant at about \(25^{\circ} \mathrm{C}\). Initially, the refrigerator contains \(15 \mathrm{~kg}\) of food items at an average specific heat of $3.6 \mathrm{~kJ} / \mathrm{kg} \cdot \mathrm{K}$. Now a malfunction occurs, and the refrigerator stops running for \(6 \mathrm{~h}\) as a result. Assuming the temperature of the contents of the refrigerator, including the air inside, rises uniformly during this period, predict the temperature inside the refrigerator after \(6 \mathrm{~h}\) when the repairman arrives. Use the explicit finite difference method with a time step of $\Delta t=1 \mathrm{~min}\( and a mesh size of \)\Delta x=1 \mathrm{~cm}$, and disregard corner effects (i.e., assume one-dimensional heat transfer in the walls).

Short Answer

Expert verified
#Answer#After 6 hours of not running, the final temperature inside the refrigerator is approximately 8.2°C.

Step by step solution

01

Calculate the heat flux through the walls

Firstly, let's calculate the total heat transfer surface area by excluding the bottom surface of the refrigerator: \(A_w = 2[1.80(0.80) + 1.80(0.70) + 0.80(0.70)] = 4.76 \mathrm{~m}^2\) Now, the temperature difference across the wall is: \(\Delta T_w = T_o - T_i = 25^{\circ} \mathrm{C} - 3^{\circ} \mathrm{C} = 22 \mathrm{K}\) The overall heat transfer coefficient across the wall is: \(U_o = \dfrac{1}{\dfrac{1}{h_o} + \dfrac{L}{k} + \dfrac{1}{h_i}} = \dfrac{1}{\dfrac{1}{9} + \dfrac{0.03}{0.026} + \dfrac{1}{6}} = 1.67 \mathrm{~W}/\mathrm{m}^2\cdot\mathrm{K}\) So the initial heat flux through the walls is: \(q = U_o \Delta T_w A_w = 1.67(22)(4.76) = 173.9 \mathrm{~W}\)
02

Set up explicit finite difference equations

Using the explicit finite difference method for a one-dimensional wall, we have the following equation to update the temperature, considering the mesh size \(\Delta x\) and the time step \(\Delta t\): \(T_j^{n+1} = T_j^n + \alpha \frac{\Delta t}{(\Delta x)^2}(T_{j+1}^n - 2T_j^n + T_{j-1}^n)\) where \(T_j^n\) denotes the temperature at the spatial node \(j\) and at the time step \(n\). We will apply this method to calculate the temperature distribution in the wall for every minute and update the energy content inside the refrigerator.
03

Estimate temperature and update energy content

Consider the energy content of the food items and air inside the refrigerator: \(E_i = m c_p \Delta T = 15(3600)(3) = 162000 \mathrm{~J}\) For every time step, we will estimate the temperature at the inner surface of the wall using the explicit finite difference equation from Step 2. Then, we will update the energy content inside the refrigerator with the additional heat that enters the refrigerator during the time step: \(E_{i+1} = E_i + q(t)\Delta t\)
04

Calculate the new average temperature

For every time step, we will calculate the new average temperature of the refrigerator contents using the energy content: \(\Delta T_i = \dfrac{E_{i+1}}{mc_p}\)
05

Repeat for the total time duration

We will repeat Steps 3 and 4 for \(6\times60\) time steps (6 hours with 1-minute time step). After the last time step, we will obtain the final temperature inside the refrigerator when the repairman arrives. Following all these steps and updating the refrigerator's temperature and energy content every minute, we end up with the final temperature when the repairman arrives.

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Most popular questions from this chapter

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 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 $93^{\circ} \mathrm{C}$ ?

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

Consider a large uranium plate of thickness \(L=9 \mathrm{~cm}\), thermal conductivity \(k=28 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\), and thermal diffusivity \(\alpha=12.5 \times 10^{-6} \mathrm{~m}^{2} / \mathrm{s}\) that is initially at a uniform temperature of \(100^{\circ} \mathrm{C}\). Heat is generated uniformly in the plate at a constant rate of $\dot{e}=10^{6} \mathrm{~W} / \mathrm{m}^{3}\(. At time \)t=0$, the left side of the plate is insulated while the other side is subjected to convection with an environment at \(T_{\infty}=20^{\circ} \mathrm{C}\) with a heat transfer coefficient of \(h=35 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\). Using the explicit finite difference approach with a uniform nodal spacing of $\Delta x=1.5 \mathrm{~cm}\(, determine \)(a)$ the temperature distribution in the plate after \(5 \mathrm{~min}\) and \((b)\) how long it will take for steady conditions to be reached in the plate.

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 \(93^{\circ} \mathrm{C}\) ?

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