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A 0.1-W small cylindrical resistor mounted on a lower part of a vertical circuit board is \(0.3\) in long and has a diameter of \(0.2 \mathrm{in}\). The view of the resistor is largely blocked by another circuit board facing it, and the heat transfer through the connecting wires is negligible. The air is free to flow through the large parallel flow passages between the boards as a result of natural convection currents. If the air temperature near the resistor is \(120^{\circ} \mathrm{F}\), determine the approximate surface temperature of the resistor. Evaluate air properties at a film temperature of \(170^{\circ} \mathrm{F}\) and \(1 \mathrm{~atm}\) pressure. Is this a good assumption? Answer: \(211^{\circ} \mathrm{F}\)

Short Answer

Expert verified
Answer: The approximate surface temperature of the cylindrical resistor is \(211^{\circ} \mathrm{F}\).

Step by step solution

01

Find the Nusselt number

Calculate the Nusselt number (Nu) for the given scenario using the expression for natural convection for a vertical cylinder: \[Nu = C \times (Gr \times Pr)^n\] where C and n are constants for natural convection, Gr is the Grashof number, and Pr is the Prandtl number. Using the air properties at the film temperature of \(170^{\circ} \mathrm{F}\) and \(1 \mathrm{~atm}\) pressure, we obtain: \[\textrm{Density} (\rho) = 0.075 \,\mathrm{lbm/ft^3}\] \[\textrm{Thermal conductivity} (k) = 0.0147 \, \mathrm{Btu/hr \cdot ft \cdot ^{\circ} F}\] \[\textrm{Dynamic viscosity} (\mu) = 3.28 \times 10^{-7} \, \mathrm{lbm/ft \cdot s}\] \[\textrm{Specific heat} (c_p) = 0.240 \, \mathrm{Btu/lbm \cdot ^{\circ} F}\] Now, we can calculate Pr and Gr: \[Pr = \frac{c_p \times \mu}{k} \approx 0.710\] \[Gr = \frac{g \times \beta \times L^3 \times (\Delta{T})}{\nu^2}\] where g is the gravitational acceleration, \(\beta\) is the thermal expansion coefficient, L is the length of the resistor, \(\Delta{T}\) is the temperature difference between the surface and ambient air, and \(\nu\) is the kinematic viscosity: \[g = 32.2 \, \mathrm{ft/s^2}\] \[\beta = \frac{1}{T_{film}} = \frac{1}{(170 + 459.67) \, \mathrm{R}} \approx 0.00310~\mathrm{R^{-1}}\] \[L = 0.3 \, \mathrm{in} = 0.025 \, \mathrm{ft}\] \[\nu = \frac{\mu}{\rho} \approx 4.37 \times 10^{-5} \, \mathrm{ft^2/s}\] Ignoring \(\Delta{T}\) for an initial estimation: \[Gr \approx \frac{32.2 \times 0.00310 \times (0.025)^3}{(4.37 \times 10^{-5})^2} \approx 1.09 \times 10^6\] Assuming laminar flow, we have C = 0.59 and n = 1/4. Therefore, the Nusselt number is: \[Nu = 0.59 \times (1.09 \times 10^6 \times 0.710)^{1/4} \approx 4.04\]
02

Calculate the convection heat transfer coefficient

With the Nusselt number, we can now calculate the convection heat transfer coefficient (h) using the equation: \[h = \frac{Nu \times k}{L} \approx \frac{4.04 \times 0.0147}{0.025} \approx 2.34 \, \mathrm{Btu/hr \cdot ft^2 \cdot ^{\circ} F}\]
03

Calculate the surface temperature of the resistor

The energy balance equation between the heat generated by the resistor and the heat loss due to convection at the surface is: \[\textrm{Heat generated} = \textrm{Heat loss due to convection}\] \[0.1 \, \mathrm{W} \times 3.41 \, \mathrm{Btu/hr \cdot W} = h \times A \times (\Delta{T})\] where A is the surface area of the resistor and \(\Delta{T} = T_s - T_a\), with \(T_s\) being the surface temperature and \(T_a\) being the ambient air temperature. We can calculate the surface area: \[A = \pi D L = \pi(0.2)(0.3) \, \mathrm{in^2} \approx 0.00265 \, \mathrm{ft^2}\] Now we can find the surface temperature: \[T_s = T_a + \frac{0.1 \times 3.41}{h\times A} \approx 120 + \frac{0.1 \times 3.41}{2.34 \times 0.00265} \approx 211^{\circ} \mathrm{F}\] The surface temperature of the resistor is approximately \(211^{\circ} \mathrm{F}\).
04

Check the assumption

We initially ignored the temperature difference between the surface and ambient air to estimate the Grashof number. The calculated surface temperature is within reasonable limits, confirming that our assumption is valid. In conclusion, the surface temperature of the resistor is approximately \(211^{\circ} \mathrm{F}\), and our assumption was reasonable.

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Most popular questions from this chapter

The upper and lower compartments of a wellinsulated container are separated by two parallel sheets of glass with an airspace between them. One of the compartments is to be filled with a hot fluid and the other with a cold fluid. If it is desired that heat transfer between the two compartments be minimal, would you recommend putting the hot fluid into the upper or the lower compartment of the container? Why?

Why are finned surfaces frequently used in practice? Why are the finned surfaces referred to as heat sinks in the electronics industry?

A spherical tank \((k=15 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\) with an inner diameter of \(3 \mathrm{~m}\) and a wall thickness of \(10 \mathrm{~mm}\) is used for storing hot liquid. The hot liquid inside the tank causes the inner surface temperature to be as high as \(100^{\circ} \mathrm{C}\). To prevent thermal burns to the people working near the tank, the tank is covered with a \(7-\mathrm{cm}\)-thick layer of insulation $(k=0.15 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})$, and the outer surface is painted to give an emissivity of \(0.35\). The tank is located in surroundings with air at $16^{\circ} \mathrm{C}$. Determine whether or not the insulation layer is sufficient to keep the outer surface temperature below \(45^{\circ} \mathrm{C}\) to prevent thermal burn hazards. Discuss ways to further decrease the outer surface temperature. Evaluate the air properties at \(30^{\circ} \mathrm{C}\) and $1 \mathrm{~atm}$ pressure. Is this a good assumption?

A \(0.5-\mathrm{m} \times 0.5-\mathrm{m}\) vertical ASTM B152 copper plate has one surface subjected to convection with hot, quiescent air. The maximum use temperature for the ASTM B152 copper plate is \(260^{\circ} \mathrm{C}\) (ASME Code for Process Piping, ASME B31.3-2014, Table A-1M). If the rate of heat removal from the plate is \(90 \mathrm{~W}\), determine the maximum temperature that the air can reach without causing the surface temperature of the copper plate to increase above \(260^{\circ} \mathrm{C}\). Evaluate the properties of air at \(300^{\circ} \mathrm{C}\). Is this an appropriate temperature to evaluate the air properties?

A spherical tank with an inner diameter of \(3 \mathrm{~m}\) is filled with a solution undergoing an exothermic reaction that generates $233 \mathrm{~W} / \mathrm{m}^{3}\( of heat and causes the surface temperature to be \)120^{\circ} \mathrm{C}$. To prevent thermal burn hazards, the tank is enclosed by a concentric outer cover that provides an air gap of \(5 \mathrm{~cm}\) in the enclosure. Determine whether the air gap is sufficient to keep the outer cover temperature below \(45^{\circ} \mathrm{C}\) to prevent thermal burns on human skin. Evaluate the properties of air in the enclosure at $80^{\circ} \mathrm{C}$ and 1 atm pressure. Is this a good assumption?

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