Chapter 3: Problem 4
Can we define the convection resistance for a unit surface area as the inverse of the convection heat transfer coefficient?
Chapter 3: Problem 4
Can we define the convection resistance for a unit surface area as the inverse of the convection heat transfer coefficient?
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Get started for freeConsider a \(1.5-\mathrm{m}\)-high and 2 -m-wide triple pane window. The thickness of each glass layer $(k=0.80 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\( is \)0.5 \mathrm{~cm}$, and the thickness of each airspace \((k=0.025 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\) is \(1.2 \mathrm{~cm}\). If the inner and outer surface temperatures of the window are $10^{\circ} \mathrm{C}\( and \)0^{\circ} \mathrm{C}$, respectively, the rate of heat loss through the window is (a) \(3.4 \mathrm{~W}\) (b) \(10.2 \mathrm{~W}\) (c) \(30.7 \mathrm{~W}\) (d) \(61.7 \mathrm{~W}\) (e) \(86.8 \mathrm{~W}\)
A cylindrical pin fin of diameter \(0.6 \mathrm{~cm}\) and length of $3 \mathrm{~cm}$ with negligible heat loss from the tip has an efficiency of 0.7. The effectiveness of this fin is (a) \(0.3\) (b) \(0.7\) (c) 2 (d) 8 (e) 14
The heat transfer surface area of a fin is equal to the sum of all surfaces of the fin exposed to the surrounding medium, including the surface area of the fin tip. Under what conditions can we neglect heat transfer from the fin tip?
A 2.2-mm-diameter and 14-m-long electric wire is tightly wrapped with a \(1-\mathrm{mm}\)-thick plastic cover whose thermal conductivity is $k=0.15 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}$. Electrical measurements indicate that a current of \(13 \mathrm{~A}\) passes through the wire, and there is a voltage drop of \(8 \mathrm{~V}\) along the wire. If the insulated wire is exposed to a medium at \(T_{\infty}=30^{\circ} \mathrm{C}\) with a heat transfer coefficient of \(h=24 \mathrm{~W} / \mathrm{m}^{2}\), \(\mathrm{K}\), determine the temperature at the interface of the wire and the plastic cover in steady operation. Also determine if doubling the thickness of the plastic cover will increase or decrease this interface temperature.
An 8-m-internal-diameter spherical tank made of \(1.5\)-cm-thick stainless steel \((k=15 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\) is used to store iced water at \(0^{\circ} \mathrm{C}\). The tank is located in a room whose temperature is \(25^{\circ} \mathrm{C}\). The walls of the room are also at $25^{\circ} \mathrm{C}$. The outer surface of the tank is black (emissivity \(\varepsilon=1\) ), and heat transfer between the outer surface of the tank and the surroundings is by natural convection and radiation. The convection heat transfer coefficients at the inner and the outer surfaces of the tank are $80 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\( and \)10 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\(, respectively. Determine \)(a)$ the rate of heat transfer to the iced water in the tank and \((b)\) the amount of ice at \(0^{\circ} \mathrm{C}\) that melts during a 24 -h period. The heat of fusion of water at atmospheric pressure is \(h_{i f}=333.7 \mathrm{~kJ} / \mathrm{kg}\).
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