Chapter 6: Problem 91
How is the modified Reynolds analogy expressed? What is the value of it? What are its limitations?
Chapter 6: Problem 91
How is the modified Reynolds analogy expressed? What is the value of it? What are its limitations?
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Get started for freeThe upper surface of an ASME SB-96 coppersilicon plate is subjected to
convection with hot air flowing at \(7.5 \mathrm{~m} / \mathrm{s}\) parallel
over the plate surface. The length of the plate is \(1 \mathrm{~m}\), and the
temperature of the hot air is \(200^{\circ} \mathrm{C}\). 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
\(93^{\circ} \mathrm{C}\). In the interest of designing a cooling mechanism to
keep the plate surface temperature from exceeding \(93^{\circ} \mathrm{C}\),
determine the variation of the local heat flux on the plate surface for $0
A 6-cm-diameter shaft rotates at 3000 rpm in a 20 -cm-long bearing with a uniform clearance of \(0.2 \mathrm{~mm}\). At steady operating conditions, both the bearing and the shaft in the vicinity of the oil gap are at $50^{\circ} \mathrm{C}$, and the viscosity and thermal conductivity of lubricating oil are \(0.05 \mathrm{~N} \cdot \mathrm{s} / \mathrm{m}^{2}\) and $0.17 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}$. By simplifying and solving the continuity, momentum, and energy equations, determine \((a)\) the maximum temperature of oil, \((b)\) the rates of heat transfer to the bearing and the shaft, and \((c)\) the mechanical power wasted by the viscous dissipation in the oil. Treat this problem as parallel flow between two large plates with one plate moving at constant velocity and the other stationary. Answers: (a) $53.3^{\circ} \mathrm{C}\(, (b) \)419 \mathrm{~W}\(, (c) \)838 \mathrm{~W}$
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 \(h_{x}=C[V /(x T)]^{w}\), where \(C\) and \(m\) are constants.
Define incompressible flow and incompressible fluid. Must the flow of a compressible fluid necessarily be treated as compressible?
A metallic airfoil of elliptical cross section has a mass of $50 \mathrm{~kg}\(, surface area of \)12 \mathrm{~m}^{2}$, and a specific heat of \(0.50 \mathrm{~kJ} / \mathrm{kg} \cdot \mathrm{K}\). The airfoil is subjected to airflow at \(1 \mathrm{~atm}\), \(25^{\circ} \mathrm{C}\), and $5 \mathrm{~m} / \mathrm{s}$ along its 3 -m-long side. The average temperature of the airfoil is observed to drop from \(160^{\circ} \mathrm{C}\) to \(150^{\circ} \mathrm{C}\) within 2 min of cooling. Assuming the surface temperature of the airfoil to be equal to its average temperature and using the momentum-heat transfer analogy, determine the average friction coefficient of the airfoil surface. Evaluate the air properties at \(25^{\circ} \mathrm{C}\) and 1 atm. Answer: \(0.000363\)
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