/*! This file is auto-generated */ .wp-block-button__link{color:#fff;background-color:#32373c;border-radius:9999px;box-shadow:none;text-decoration:none;padding:calc(.667em + 2px) calc(1.333em + 2px);font-size:1.125em}.wp-block-file__button{background:#32373c;color:#fff;text-decoration:none} Problem 67 To augment heat transfer between... [FREE SOLUTION] | 91Ó°ÊÓ

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To augment heat transfer between two flowing fluids, it is proposed to insert a 100 -mm-long, 5 -mm-diameter 2024 aluminum pin fin through the wall separating the two fluids. The pin is inserted to a depth of \(d\) into fluid 1 . Fluid 1 is air with a mean temperature of \(10^{\circ} \mathrm{C}\) and velocity of \(10 \mathrm{~m} / \mathrm{s}\). Fluid 2 is air with a mean temperature of \(40^{\circ} \mathrm{C}\) and velocity of \(3 \mathrm{~m} / \mathrm{s}\). (a) Determine the rate of heat transfer from the warm air to the cool air through the pin fin for \(d=50 \mathrm{~mm}\). (b) Plot the variation of the heat transfer rate with the insertion distance, \(d\). Does an optimal insertion distance exist?

Short Answer

Expert verified
The heat transfer rate, \(q\), through a \(100\,\text{mm}\)-long, \(5\,\text{mm}\)-diameter 2024 aluminum pin fin between two fluids can be calculated for a given insertion distance, \(d\), by determining the heat transfer coefficients for both fluids, calculating the thermal resistance of the pin fin, and using the temperature difference between the two fluids. For \(d = 50 \,\text{mm}\), the heat transfer rate can be calculated using this process. By plotting the variation of the heat transfer rate with insertion distance, we can analyze if an optimal insertion distance exists that maximizes the heat transfer rate from the warm air to the cool air through the pin fin.

Step by step solution

01

Determine the heat transfer coefficients for both fluids

To calculate the heat transfer rate, we first need to find the heat transfer coefficients for both fluids, \(h_1\) and \(h_2\), using the Nusselt number (\(Nu\)), which depends on Reynolds number (\(Re\)) and Prandtl number (\(Pr\)). You can refer to an appropriate correlation for forced convection over cylinders, such as the Zukauskas correlation: \(Nu = C \cdot Re^m \cdot Pr^n\) Where \(C\), \(m\), and \(n\) are constants that depend on the flow regime and geometry. Once we have the Nusselt number, we can obtain the heat transfer coefficients: \(h = \frac{Nu \cdot k}{L}\) Here, \(k\) is the thermal conductivity of the fluid, and \(L\) is the characteristic length, which in our case is the diameter of the pin fin. Calculate \(h_1\) and \(h_2\) for fluid 1 and fluid 2, respectively, using their temperatures, velocities, and relevant properties.
02

Compute the thermal resistance of the pin fin

To determine the heat transfer rate through the pin fin, we have to calculate the thermal resistance of the pin fin. The thermal resistance, \(R_{th}\), can be computed using the equation: \(R_{th} = \frac{1}{h_1 \cdot A_1} + \frac{\ln(r_2 / r_1)}{2 \pi \cdot k_{al} \cdot L} + \frac{1}{h_2 \cdot A_2}\) Where: - \(h_1\) and \(h_2\) are the heat transfer coefficients for fluid 1 and fluid 2, respectively, - \(A_1\) and \(A_2\) are the surface areas of the pin fin exposed to fluid 1 and fluid 2, respectively, - \(r_1\) and \(r_2\) are the inner and outer radii of the pin fin, respectively, - \(k_{al}\) is the thermal conductivity of the aluminum pin, - \(L\) is the length of the pin fin.
03

Calculate the heat transfer rate

Now that we have the thermal resistance, we can calculate the heat transfer rate, \(q\), using the temperature difference between the two fluids and the thermal resistance: \(q = \frac{T_1 - T_2}{R_{th}}\) Where \(T_1\) and \(T_2\) are the temperatures of fluid 1 and fluid 2, respectively. Calculate \(q\) for \(d = 50 \,\text{mm}\).
04

Plot the variation of the heat transfer rate with insertion distance

To analyze the effect of the insertion distance on the heat transfer rate, we will vary the insertion distance \(d\) and recalculate the heat transfer rate for each value. Choose a relevant range of insertion distances and calculate the heat transfer rate as described in Steps 1-3 for each insertion distance. Plot the heat transfer rate as a function of insertion distance.
05

Analyze the optimal insertion distance

Analyze the plot obtained in the previous step to determine if there is an optimal insertion distance that maximizes the heat transfer rate from the warm air to the cool air through the pin fin. If there is an optimal insertion distance, identify its approximate value. Otherwise, discuss the trends observed in the graph and explain the implications for the heat transfer process.

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Key Concepts

These are the key concepts you need to understand to accurately answer the question.

Nusselt Number
To better understand heat transfer, we often use the Nusselt number, which helps determine the efficiency of heat exchange between a fluid and a solid surface. In essence, the Nusselt number (Nu) is a dimensionless number that describes how well the fluid conducts heat compared to natural convection.
When calculating the Nusselt number, we encounter important variables such as the Reynolds number (Re) and the Prandtl number (Pr). These figures help describe the behavior of the fluid flow and its thermal properties:
  • Reynolds number (Re): This characterizes the type of fluid flow, whether it's laminar or turbulent, based on the fluid's density, velocity, and viscosity.
  • Prandtl number (Pr): This describes how quickly thermal energy diffuses through the fluid and is derived from the fluid's viscosity and thermal conductivity.
The formula for the Nusselt number can be written as: \[ Nu = C \cdot Re^m \cdot Pr^n \]Here, C, m, and n are constants found through empirical correlations, like the Zukauskas correlation, tailored for specific conditions and geometries.
By using the Nusselt number, we determine the convective heat transfer coefficient (h) for a fluid. This involves multiplying the Nusselt number by the fluid's thermal conductivity, then dividing by a characteristic length (usually the fin's diameter in pin fins). Thus, it is clear how essential the Nusselt number is for sizing up the heat transfer capabilities effectively.
Thermal Resistance
Thermal resistance is a crucial concept when it comes to evaluating how effectively heat is transferred through layers of materials. Imagine thermal resistance as a barrier that heat must "cross" when moving through the pin fin from one fluid to another.
Much like electrical resistance in circuits, thermal resistance quantifies how difficult it is for heat to pass through a particular material. Lower thermal resistance implies better heat transfer. The formula to calculate thermal resistance in the context of pin fins is:\[ R_{th} = \frac{1}{h_1 \cdot A_1} + \frac{\ln(r_2 / r_1)}{2 \pi \cdot k_{al} \cdot L} + \frac{1}{h_2 \cdot A_2} \]Where each term accounts for:
  • The convective resistance from fluid 1 to the fin's surface using heat transfer coefficient \( h_1 \) and area \( A_1 \).
  • The conductive resistance within the pin itself, characterized by the fin's radii \( r_1 \) and \( r_2 \), and the aluminum's thermal conductivity \( k_{al} \).
  • The resistance from the fin's other end to fluid 2, using heat transfer coefficient \( h_2 \) and area \( A_2 \).
Understanding thermal resistance is vital for engineers seeking to improve heat transfer in systems; reducing resistance can augment heat flow, ensuring more effective thermal management across various applications.
Pin Fin
Pin fins are marvelous components engineered to boost heat transfer between surfaces and fluids. They are typically small, cylindrical rods extending from a surface. Their purpose? To increase the surface area exposed to the fluid, enhancing heat dissipation.
The use of pin fins in thermal systems is driven by the principle that more surface area allows more contact between the solid surface and the fluid, which equates to better heat exchange. These tiny fins draw heat from the warmer fluid and deliver it to the cooler fluid via conduction and convection processes.
When discussing pin fins, several factors should be considered:
  • Material Type: Materials with high thermal conductivity, like aluminum or copper, are often chosen for making pin fins due to their ability to quickly conduct heat.
  • Size and Geometry: The length, diameter, and arrangement of pin fins influence how efficiently heat can be transferred.
  • Insertion Depth: Pin fins can be inserted to different depths, affecting how they interact with fluids and thus the rate of heat transfer.
Experimental and theoretical studies look at optimal configurations for pin fins, such as the right insertion depth, which can significantly impact the heat transfer rate and efficiency. By adjusting these variables, engineers can design pin fin systems that meet specific thermal requirements, improving device performance across many fields.

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Most popular questions from this chapter

Evaporation of liquid fuel droplets is often studied in the laboratory by using a porous sphere technique in which the fuel is supplied at a rate just sufficient to maintain a completely wetted surface on the sphere. Consider the use of kerosene at \(300 \mathrm{~K}\) with a porous sphere of 1 -mm diameter. At this temperature the kerosene has a saturated vapor density of \(0.015 \mathrm{~kg} / \mathrm{m}^{3}\) and a latent heat of vaporization of \(300 \mathrm{~kJ} / \mathrm{kg}\). The mass diffusivity for the vapor-air mixture is \(10^{-5} \mathrm{~m}^{2} / \mathrm{s}\). If dry, atmospheric air at \(V=15 \mathrm{~m} / \mathrm{s}\) and \(T_{\infty}=300 \mathrm{~K}\) flows over the sphere, what is the minimum mass rate at which kerosene must be supplied to maintain a wetted surface? For this condition, by how much must \(T_{\infty}\) actually exceed \(T_{s}\) to maintain the wetted surface at \(300 \mathrm{~K}\) ?

Air at a pressure of 1 atm and a temperature of \(50^{\circ} \mathrm{C}\) is in parallel flow over the top surface of a flat plate that is heated to a uniform temperature of \(100^{\circ} \mathrm{C}\). The plate has a length of \(0.20 \mathrm{~m}\) (in the flow direction) and a width of \(0.10 \mathrm{~m}\). The Reynolds number based on the plate length is 40,000 . What is the rate of heat transfer from the plate to the air? If the free stream velocity of the air is doubled and the pressure is increased to \(10 \mathrm{~atm}\), what is the rate of heat transfer?

A stream of atmospheric air is used to dry a series of biological samples on plates that are each of length \(L_{i}=0.25 \mathrm{~m}\) in the direction of the airflow. The air is dry and at a temperature equal to that of the plates \(\left(T_{\infty}=T_{s}=50^{\circ} \mathrm{C}\right)\). The air speed is \(u_{\infty}=9.1 \mathrm{~m} / \mathrm{s}\). (a) Sketch the variation of the local convection mass transfer coefficient \(h_{m x}\) with distance \(x\) from the leading edge. Indicate the specific nature of the \(x\) dependence. (b) Which of the plates will dry the fastest? Calculate the drying rate per meter of width for this plate \((\mathrm{kg} / \mathrm{s}+\mathrm{m})\). (c) At what rate would heat have to be supplied to the fastest drying plate to maintain it at \(T_{s}=50^{\circ} \mathrm{C}\) during the drying process?

Consider a flat plate subject to parallel flow (top and bottom) characterized by \(u_{\infty}=5 \mathrm{~m} / \mathrm{s}, T_{\infty}=20^{\circ} \mathrm{C}\). (a) Determine the average convection heat transfer coefficient, convective heat transfer rate, and drag force associated with an \(L=2\)-m-long, \(w=2-\mathrm{m}\) wide flat plate for airflow and surface temperatures of \(T_{s}=50^{\circ} \mathrm{C}\) and \(80^{\circ} \mathrm{C}\). (b) Determine the average convection heat transfer coefficient, convective heat transfer rate, and drag force associated with an \(L=0.1\)-m-long, \(w=0.1\)-m-wide flat plate for water flow and surface temperatures of \(T_{s}=50^{\circ} \mathrm{C}\) and \(80^{\circ} \mathrm{C}\).

An air-cooled steam condenser is operated with air in cross flow over a square, in-line array of 400 tubes \(\left(N_{L}=N_{T}=20\right.\) ), with an outside tube diameter of \(20 \mathrm{~mm}\) and longitudinal and transverse pitches of \(S_{L}=60 \mathrm{~mm}\) and \(S_{T}=30 \mathrm{~mm}\), respectively. Saturated steam at a pressure of \(2.455\) bars enters the tubes, and a uniform tube outer surface temperature of \(T_{s}=390 \mathrm{~K}\) may be assumed to be maintained as condensation occurs within the tubes. (a) If the temperature and velocity of the air upstream of the array are \(T_{i}=300 \mathrm{~K}\) and \(V=4 \mathrm{~m} / \mathrm{s}\), what is the temperature \(T_{o}\) of the air that leaves the array? As a first approximation, evaluate the properties of air at \(300 \mathrm{~K}\). (b) If the tubes are \(2 \mathrm{~m}\) long, what is the total heat transfer rate for the array? What is the rate at which steam is condensed in \(\mathrm{kg} / \mathrm{s}\) ? (c) Assess the effect of increasing \(N_{L}\) by a factor of 2 , while reducing \(S_{L}\) to \(30 \mathrm{~mm}\). For this configuration, explore the effect of changes in the air velocity.

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