Determine the heat flux at the wall of a microchannel of width \(1 \mu \mathrm{m}\) if the wall temperature is \(50^{\circ} \mathrm{C}\) and the average gas temperature near the wall is \(100^{\circ} \mathrm{C}\) for the cases of (a) \(\sigma_{T}=1.0, \gamma=1.667, k=0.15 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}, \lambda / \operatorname{Pr}=0.5\) (b) \(\sigma_{T}=0.8, \gamma=2, k=0.1 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}, \lambda / \operatorname{Pr}=5\)

Short Answer

Expert verified
Answer: The heat flux at the wall of the microchannel is -75,000 W/m² for case (a) and -50,000 W/m² for case (b).

Step by step solution

01

Calculate the temperature difference

First, calculate the temperature difference between the wall and the gas temperature, which is given by: $$ \Delta T = T_w - T_g $$ For both cases, this will be: $$ \Delta T = 50^{\circ} \mathrm{C} - 100^{\circ} \mathrm{C} = -50^{\circ} \mathrm{C} $$ Note that \(\Delta T\) is negative since we expect the heat to flow from the gas to the wall.
02

Calculate the heat flux for case (a)

In case (a), we have values for \(k_a = 0.15 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\) and the microchannel width \(\Delta x_a = 1 \mu\mathrm{m}\). Let's calculate the heat flux in case (a): $$ q_a = k_a * \frac{\Delta T}{\Delta x_a} = 0.15 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K} * \frac{-50^{\circ} \mathrm{C}}{1 \mu\mathrm{m}} $$ Converting the width from \(\mu\mathrm{m}\) to meters, we get \(1 \mu\mathrm{m} = 1 * 10^{-6} \mathrm{m}\). Thus, the heat flux for case (a) becomes: $$ q_a = 0.15 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K} * \frac{-50^{\circ} \mathrm{C}}{1 * 10^{-6} \mathrm{m}} = -75,\!000 \,\mathrm{W}/\mathrm{m}^2 $$
03

Calculate the heat flux for case (b)

In case (b), we have values for \(k_b = 0.1 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\) and the microchannel width \(\Delta x_b = 1 \mu\mathrm{m}\). Let's calculate the heat flux in case (b): $$ q_b = k_b * \frac{\Delta T}{\Delta x_b} = 0.1 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K} * \frac{-50^{\circ} \mathrm{C}}{1 \mu\mathrm{m}} $$ Using the same width conversion as before, the heat flux for case (b) becomes: $$ q_b = 0.1 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K} * \frac{-50^{\circ} \mathrm{C}}{1 * 10^{-6} \mathrm{m}} = -50,\!000 \,\mathrm{W}/\mathrm{m}^2 $$ In conclusion, the heat flux at the wall of the microchannel is \(-75,\!000 \,\mathrm{W}/\mathrm{m}^2\) for case (a), and \(-50,\!000 \,\mathrm{W}/\mathrm{m}^2\) for case (b).

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Most popular questions from this chapter

Consider a laminar ideal gas flow over a flat plate, where the local Nusselt number can be expressed as \(\mathrm{Nu}_{x}=0.332 \mathrm{Re}_{x}^{1 / 2} \operatorname{Pr}^{1 / 3}\). Using the expression for the local Nusselt number, show that it can be rewritten in terms of local convection heat transfer coefficient as \(h_{x}=C[V /(x T)]^{m}\), where \(C\) and \(m\) are constants.

Object 1 with a characteristic length of \(0.5 \mathrm{~m}\) is placed in airflow at 1 atm and \(20^{\circ} \mathrm{C}\) with free stream velocity of \(50 \mathrm{~m} / \mathrm{s}\). The heat flux transfer from object 1 when placed in the airflow is measured to be \(12,000 \mathrm{~W} / \mathrm{m}^{2}\). If object 2 has the same shape and geometry as object 1 (but with a characteristic length of \(5 \mathrm{~m}\) ) is placed in the airflow at 1 atm and \(20^{\circ} \mathrm{C}\) with free stream velocity of \(5 \mathrm{~m} / \mathrm{s}\), determine the average convection heat transfer coefficient for object 2 . Both objects are maintained at a constant surface temperature of \(120^{\circ} \mathrm{C}\).

A 5-cm-diameter shaft rotates at \(4500 \mathrm{rpm}\) in a \(15-\mathrm{cm}-\) long, 8 -cm-outer-diameter cast iron bearing \((k=70 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\) with a uniform clearance of \(0.6 \mathrm{~mm}\) filled with lubricating oil \(\left(\mu=0.03 \mathrm{~N} \cdot \mathrm{s} / \mathrm{m}^{2}\right.\) and \(\left.k=0.14 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\right)\). The bearing is cooled externally by a liquid, and its outer surface is maintained at \(40^{\circ} \mathrm{C}\). Disregarding heat conduction through the shaft and assuming one-dimensional heat transfer, determine \((a)\) the rate of heat transfer to the coolant, \((b)\) the surface temperature of the shaft, and ( \(c\) ) the mechanical power wasted by the viscous dissipation in oil.

An electrical water \((k=0.61 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\) heater uses natural convection to transfer heat from a 1 -cm-diameter by \(0.65\)-m-long, \(110 \mathrm{~V}\) electrical resistance heater to the water. During operation, the surface temperature of this heater is \(120^{\circ} \mathrm{C}\) while the temperature of the water is \(35^{\circ} \mathrm{C}\), and the Nusselt number (based on the diameter) is 5 . Considering only the side surface of the heater (and thus \(A=\pi D L\) ), the current passing through the electrical heating element is (a) \(2.2 \mathrm{~A}\) (b) \(2.7 \mathrm{~A}\) (c) \(3.6 \mathrm{~A}\) (d) \(4.8 \mathrm{~A}\) (e) \(5.6 \mathrm{~A}\)

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