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An airfoil with a characteristic length of \(0.2 \mathrm{ft}\) is placed in airflow at 1 atm and \(60^{\circ} \mathrm{F}\) with free stream velocity of $150 \mathrm{ft} / \mathrm{s}\( and convection heat transfer coefficient of \)21 \mathrm{Btu} / \mathrm{h} \cdot \mathrm{ft}^{2} \cdot{ }^{\circ} \mathrm{F}$. If a second airfoil with a characteristic length of \(0.4 \mathrm{ft}\) is placed in the airflow at \(1 \mathrm{~atm}\) and \(60^{\circ} \mathrm{F}\) with free stream velocity of \(75 \mathrm{ft} / \mathrm{s}\), determine the heat flux from the second airfoil. Both airfoils are maintained at a constant surface temperature of \(180^{\circ} \mathrm{F}\).

Short Answer

Expert verified
Answer: The heat flux from the second airfoil is 1260 Btu/h·ft².

Step by step solution

01

Given Data for Airfoil 1

Characteristic length: \(L_1 = 0.2 \ \mathrm{ft}\). Free stream velocity: \(V_1 = 150 \ \mathrm{ft/s}\). Convection heat transfer coefficient: \(h_1 = 21 \ \mathrm{Btu/h \cdot ft^2 \cdot ^\circ F}\).
02

Given Data for Airfoil 2

Characteristic length: \(L_2 = 0.4 \ \mathrm{ft}\). Free stream velocity: \(V_2 = 75 \ \mathrm{ft/s}\).
03

Common Data for Both Airfoils

Air pressure: \(1 \ \mathrm{atm}\). Air temperature: \(T_\infty = 60 \ ^\circ\mathrm{F}\). Surface temperature: \(T_s = 180 \ ^\circ\mathrm{F}\).
04

Heat Transfer Rate Equation

The convection heat transfer equation we'll use is: \(q = h * A * (T_s - T_\infty)\).
05

Heat Flux from Airfoil 1

First, we need to find the heat transfer rate from airfoil 1: \(q_1 = h_1 * A_1 * (T_s - T_\infty)\). Since we don't have the surface area \(A_1\), we can rewrite the equation in terms of heat flux, \(\phi_1 = q_1/A_1\): \(\phi_1 = h_1 * (T_s - T_\infty)\). Now, substitute the known values: \(\phi_1 = 21 \ \mathrm{Btu/h \cdot ft^2 \cdot ^\circ F} * (180 \ ^\circ\mathrm{F} - 60 \ ^\circ\mathrm{F}) = 2520 \ \mathrm{Btu/h \cdot ft^2}\).
06

Finding the Convection Heat Transfer Coefficient for Airfoil 2

Since the airfoils have the same geometry and properties, the Reynolds number and Prandtl number will remain constant. Since we know the convection heat transfer coefficient \(h_1\), we can use the following relation to find \(h_2\): \(\frac{h_2}{h_1} = \frac{L_2}{L_1} * \frac{V_2}{V_1}\). Substitute the given values: \(\frac{h_2}{21 \ \mathrm{Btu/h \cdot ft^2 \cdot ^\circ F}} = \frac{0.4 \ \mathrm{ft}}{0.2 \ \mathrm{ft}} * \frac{75 \ \mathrm{ft/s}}{150 \ \mathrm{ft/s}}\). Solving for \(h_2\): \(h_2 = 10.5 \ \mathrm{Btu/h \cdot ft^2 \cdot ^\circ F}\).
07

Heat Flux from Airfoil 2

Now, we can find the heat flux from airfoil 2 using the convection heat transfer equation in terms of heat flux, \(\phi_2 = q_2/A_2\): \(\phi_2 = h_2 * (T_s - T_\infty)\). Since we have the values of \(h_2\), \(T_s\), and \(T_\infty\), we can substitute them into the equation: \(\phi_2 = 10.5 \ \mathrm{Btu/h \cdot ft^2 \cdot ^\circ F} * (180 \ ^\circ\mathrm{F} - 60 \ ^\circ\mathrm{F}) = 1260 \ \mathrm{Btu/h \cdot ft^2}\). So, the heat flux from the second airfoil is \(1260 \ \mathrm{Btu/h \cdot ft^2}\).

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Most popular questions from this chapter

In any forced or natural convection situation, the velocity of the flowing fluid is zero where the fluid wets any stationary surface. The magnitude of heat flux where the fluid wets a stationary surface is given by (a) \(k\left(T_{\text {fluid }}-T_{\text {wall }}\right)\) (b) \(\left.k \frac{d T}{d y}\right|_{\text {wall }}\) (c) \(\left.k \frac{d^{2} T}{d y^{2}}\right|_{\text {wall }}\) (d) \(\left.h \frac{d T}{d y}\right|_{\text {wall }}\) (e) None of them

The coefficient of friction \(C_{f}\) for a fluid flowing across a surface in terms of the surface shear stress, \(\tau_{w}\), is given by (a) \(2 \rho V^{2} / \tau_{w}\) (b) \(2 \tau_{w} / \rho V^{2}\) (c) \(2 \tau_{w} / \rho V^{2} \Delta T\) (d) \(4 \tau_{u} / \rho V^{2}\) (e) None of them

Consider a 5-cm-diameter shaft rotating at \(5600 \mathrm{rpm}\) in a \(25-\mathrm{cm}\)-long bearing with a clearance of \(0.5 \mathrm{~mm}\). Determine the power required to rotate the shaft if the fluid in the gap is (a) air, (b) water, and (c) oil at \(40^{\circ} \mathrm{C}\) and $1 \mathrm{~atm}$.

A \(4-\mathrm{cm}\)-diameter shaft rotates at \(5200 \mathrm{rpm}\) 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. Treat this problem as parallel flow between two large plates with one plate moving at constant velocity and the other stationary.

Air at \(5^{\circ} \mathrm{C}\), with a convection heat transfer coefficient of \(30 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\), is used for cooling metal plates coming out of a heat treatment oven at an initial temperature of \(300^{\circ} \mathrm{C}\). The plates $\left(k=180 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}, \rho=2800 \mathrm{~kg} / \mathrm{m}^{3}\right.$, and \(\left.c_{p}=880 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\right)\) have a thickness of \(10 \mathrm{~mm}\). Using appropriate software, determine the effect of cooling time on the temperature gradient in the metal plates at the surface. By varying the cooling time from 0 to \(3000 \mathrm{~s}\), plot the temperature gradient in the plates at the surface as a function of cooling time. Hint: Use the lumped system analysis to calculate the plate surface temperature. Make sure to verify the application of this method to this problem.

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