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A vertical array of circuit boards is immersed in quiescent ambient air at \(T_{\infty}=17^{\circ} \mathrm{C}\). Although the components protrude from their substrates, it is reasonable, as a first approximation, to assume \(A t\) plates with uniform surface heat flux \(q_{s}^{\prime \prime}\). Consider boards of length and width \(L=W=0.4 \mathrm{~m}\) and spacing \(S=25 \mathrm{~mm}\). If the maximum allowable board temperature is \(77^{\circ} \mathrm{C}\), what is the maximum allowable power dissipation per board?

Short Answer

Expert verified
The maximum allowable power dissipation per board can be calculated using the given data, and a step-by-step approach involving the calculation of characteristic length, temperature difference, Grashof and Rayleigh numbers, heat transfer coefficient, maximum heat transfer rate, and finally, the maximum allowable power dissipation. Following these steps and using the appropriate equations and constants for air and the geometry of the problem, we can find the maximum allowable power dissipation per board.

Step by step solution

01

Find the characteristic length

The characteristic length is the length scale that governs the heat transfer process. In this case, the characteristic length will be the spacing between the boards, S. \(L_c = S = 25 \ mm = 0.025 \ m \)
02

Find the temperature difference

The temperature difference between the ambient air and the circuit boards will be: \(\Delta T = T_{max} - T_\infty = 77^{\circ} C - 17^{\circ} C = 60^{\circ} C \)
03

Calculate the Grashof number

The Grashof number is a dimensionless quantity that characterizes the ratio of buoyancy to viscous forces in a fluid. It is given by: \(Gr = \frac{g \beta \Delta T {L_c}^{3}}{\nu^2}\) where: \(g\) is the gravitational acceleration, approximately \(9.8 \ m/s^2\), \(\beta\) is the coefficient of thermal expansion for air, approximately \(3.4 \times 10^{-3} \ K^{-1}\), \(\Delta T\) is the temperature difference, \(L_c\) is the characteristic length, and \(\nu\) is the kinematic viscosity of air, approximately \(1.6 \times 10^{-5} \ m^2/s\).
04

Calculate the Rayleigh number

The Rayleigh number is a dimensionless quantity that signifies the occurrence of natural convection or free convection. It is given by: \(Ra = Pr \times Gr\) where: \(Pr\) is the Prandtl number of the fluid (for air, \(Pr \approx 0.7\)), \(Gr\) is the Grashof number.
05

Find the heat transfer coefficient

Next, we need to calculate the heat transfer coefficient, which accounts for the heat transfer rate and surface area. We can obtain the heat transfer coefficient (h) using the Nusselt number (Nu) relation for natural convection: \(Nu = C \times Ra^n\) where \(C\) and \(n\) are constants dependent on the geometry of the problem. For a vertical plate in natural convection, we use: \(Nu = 0.59 \times Ra^{1/4}\) Now, the heat transfer coefficient can be calculated as: \(h = \frac{Nu \times k}{L_c}\) where: \(k\) is the thermal conductivity of the fluid (for air, \(k \approx 0.026 \ W/(m \cdot K)\)).
06

Calculate the maximum heat transfer rate

The maximum heat transfer rate per board can now be calculated using the heat transfer coefficient and the surface area of the circuit board: \(\dot{Q}_{max} = h \times A \times \Delta T\) where: \(A\) is the surface area of the circuit board, \(\Delta T\) is the temperature difference, \(h\) is the heat transfer coefficient.
07

Calculate the maximum allowable power dissipation

The maximum allowable power dissipation per board can be determined using the maximum heat transfer rate: \(P_{max} = \dot{Q}_{max}\) Compute all the values and arrive at the maximum allowable power dissipation per board.

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Key Concepts

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

Natural Convection
Natural convection is a mechanism of heat transfer that occurs in fluids without any external force, such as a fan or pump. Instead, this transfer is driven by differences in fluid density, which arise due to temperature variations within the fluid. As fluid around a warm object, like a circuit board, heats up, it becomes less dense and rises, while cooler, denser fluid moves in to replace it. This cycle creates a natural circulation of fluid, facilitating the transfer of heat away from the object.

Understanding natural convection is crucial when designing electronics like circuit boards. If the heat produced by the electrical components isn't dissipated adequately, it can result in overheating and potentially cause the components to fail. Designers use knowledge of natural convection to ensure efficient cooling, typically by optimizing the layout and orientation of circuit boards to maximize the area exposed to cooling air and using materials that enhance heat dissipation.
Grashof Number
The Grashof number is crucial in characterizing natural convection flows. It's a dimensionless quantity indicating the relative significance of buoyancy forces, caused by fluid density changes, to viscous forces within the fluid. In the realm of circuit board cooling, the Grashof number helps engineers determine whether natural convection will be strong enough to cool the electronics effectively.

Calculated with the formula \(Gr = \frac{g \beta \Delta T {L_c}^{3}}{u^2}\), the Grashof number includes the acceleration due to gravity (\(g\)), the thermal expansion coefficient (\(\beta\)), the temperature difference between the board's surface and the ambient air (\(\Delta T\)), the characteristic length of the problem (\(L_c\)), and the kinematic viscosity of air (\(u\)). A larger Grashof number means that buoyancy forces dominate over viscous forces, indicating a propensity for natural convection to occur.
Nusselt Number
The Nusselt number is another dimensionless quantity of paramount importance in the study of heat transfer, especially in situations where convection plays a role. It represents the enhancement of heat transfer through a fluid layer as a result of convection compared to pure thermal conduction.

For natural convection calculations along vertical surfaces, engineers apply the Nusselt number using an empirical correlation, such as \(Nu = 0.59 \times Ra^{1/4}\), where \(Ra\) is the Rayleigh number—a product of the Grashof and Prandtl numbers. The Nusselt number directly relates to the heat transfer coefficient (\(h\)), which is essential for determining how much heat can be removed from a surface, like that of a circuit board.
Heat Transfer Coefficient
The heat transfer coefficient (\(h\)) is a measure that represents the heat transfer rate per unit area per unit temperature difference. It's a significant factor in calculating the cooling performance of systems where heat transfer is critical, like circuit boards. The higher the coefficient, the more efficient the heat transfer from the circuit board to the surrounding air.

A calculated heat transfer coefficient helps engineers predict how much heat can be dissipated from a circuit board. It is used in conjunction with the maximum temperature difference (\(\Delta T\)) and surface area (\(A\)) to determine the maximum amount of power (\(P_{max}\)) that can be safely dissipated by natural convection cooling.
Maximum Power Dissipation
Maximum power dissipation refers to the highest amount of heat energy that can be released by a circuit board without exceeding the maximum allowable temperature. It's a crucial figure in electronic design, as it determines the threshold beyond which the component may fail due to overheating.

To calculate maximum power dissipation, engineers employ the maximum heat transfer rate, which uses the heat transfer coefficient, the surface area of the circuit board, and the maximum temperature difference the board can endure. By keeping the power dissipation below this maximum limit, reliability and longevity of the electronic components are ensured. In the given exercise, the power dissipation per board is determined, ensuring the boards operate within safe thermal conditions. This process involves understanding and controlling the aforementioned heat transfer principles.

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Most popular questions from this chapter

A refrigerator door has a height and width of \(H=1 \mathrm{~m}\) and \(W=0.65 \mathrm{~m}\), respectively, and is situated in a large room for which the air and walls are at \(T_{\infty}=T_{\text {sur }}=25^{\circ} \mathrm{C}\). The door consists of a layer of polystyrene insulation \((k=0.03 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\) sandwiched between thin sheets of steel \((\varepsilon=0.6)\) and polypropylene. Under normal operating conditions, the inner surface of the door is maintained at a fixed temperature of \(T_{s, i}=5^{\circ} \mathrm{C}\). (a) Estimate the heat gain through the door for the worst case condition corresponding to no insulation \((L=0)\). (b) Compute and plot the heat gain and the outer surface temperature \(T_{s, o}\) as a function of insulation thickness for \(0 \leq L \leq 25 \mathrm{~mm}\).

The heat transfer rate due to free convection from a vertical surface, \(1 \mathrm{~m}\) high and \(0.6 \mathrm{~m}\) wide, to quiescent air that is \(20 \mathrm{~K}\) colder than the surface is known. What is the ratio of the heat transfer rate for that situation to the rate corresponding to a vertical surface, \(0.6 \mathrm{~m}\) high and \(1 \mathrm{~m}\) wide, when the quiescent air is \(20 \mathrm{~K}\) warmer than the surface? Neglect heat transfer by radiation and any influence of temperature on the relevant thermophysical properties of air.

Many laptop computers are equipped with thermal management systems that involve liquid cooling of the central processing unit (CPU), transfer of the heated liquid to the back of the laptop screen assembly, and dissipation of heat from the back of the screen assembly by way of a flat, isothermal heat spreader. The cooled liquid is recirculated to the CPU and the process continues. Consider an aluminum heat spreader that is of width \(w=275 \mathrm{~mm}\) and height \(L=175 \mathrm{~mm}\). The screen assembly is oriented at an angle \(\theta=30^{\circ}\) from the vertical direction, and the heat spreader is attached to the \(t=3\)-mm-thick plastic housing with a thermally conducting adhesive. The plastic housing has a thermal conductivity of \(k=0.21 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\) and emissivity of \(\varepsilon=0.85\). The contact resistance associated with the heat spreaderhousing interface is \(R_{t, c}^{\prime \prime}=2.0 \times 10^{-4} \mathrm{~m}^{2} \cdot \mathrm{K} / \mathrm{W}\). If the CPU generates, on average, \(15 \mathrm{~W}\) of thermal energy, what is the temperature of the heat spreader when \(T_{\infty}=T_{\text {sur }}=23^{\circ} \mathrm{C}\) ? Which thermal resistance (contact, conduction, radiation, or free convection) is the largest?

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}

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?

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