/*! 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 97 Most architects know that the ce... [FREE SOLUTION] | 91Ó°ÊÓ

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Most architects know that the ceiling of an ice-skating rink must have a high reflectivity. Otherwise, condensation may occur on the ceiling, and water may drip onto the ice, causing bumps on the skating surface. Condensation will occur on the ceiling when its surface temperature drops below the dew point of the rink air. Your assignment is to perform an analysis to determine the effect of the ceiling emissivity on the ceiling temperature, and hence the propensity for condensation. The rink has a diameter of \(D=50 \mathrm{~m}\) and a height of \(L=10 \mathrm{~m}\), and the temperatures of the ice and walls are \(-5^{\circ} \mathrm{C}\) and \(15^{\circ} \mathrm{C}\), respectively. The rink air temperature is \(15^{\circ} \mathrm{C}\), and a convection coefficient of \(5 \mathrm{~W} / \mathrm{m}^{2}+\mathrm{K}\) characterizes conditions on the ceiling surface. The thickness and thermal conductivity of the ceiling insulation are \(0.3 \mathrm{~m}\) and \(0.035 \mathrm{~W} / \mathrm{m}-\mathrm{K}\), respectively, and the temperature of the outdoor air is \(-5^{\circ} \mathrm{C}\). Assume that the ceiling is a diffuse-gray surface and that the Walls and ice may be approximated as blackbodies. (a) Consider a flat ceiling having an emissivity of \(0.05\) (highly reflective panels) or \(0.94\) (painted panels). Perform an energy balance on the ceiling to calculate the corresponding values of the ceiling temperature. If the relative humidity of the rink air is \(70 \%\), will condensation occur for either or both of the emissivities? (b) For each of the emissivities, calculate and plot the ceiling temperature as a function of the insulation thickness for \(0.1 \leq r \leq 1 \mathrm{~m}\). Identify conditions for which condensation will occur on the ceiling.

Short Answer

Expert verified
In this analysis, we determined the effect of ceiling emissivity on its temperature and propensity for condensation in an ice-skating rink. By performing an energy balance on the ceiling and calculating the dew point, it's possible to determine whether condensation would occur for the given emissivities of 0.05 (highly reflective panels) and 0.94 (painted panels). We also calculated and plotted the ceiling temperature as a function of insulation thickness, identifying the conditions under which condensation would occur on the ceiling.

Step by step solution

01

Analyze the problem and identify known values and formulas

To solve this problem, first identify the given values and the required formulas for calculating the ceiling temperature for different emissivities and the propensity for condensation. The given values and formulas are as follows: - Diameter (D) = 50 m - Height (L) = 10 m - Ice temperature (T_ice) = -5 °C - Walls temperature (T_wall) = 15 °C - Rink air temperature (T_air) = 15 °C - Convection coefficient (h) = 5 W/m²K - Insulation thickness (r) = 0.3 m (initially) - Thermal conductivity (k) = 0.035 W/m∙K We will need to use these values in the energy balance equation, which includes both radiation and convection heat transfer components. The heat balance equation can be written as:
02

Perform energy balance for each emissivity

We need to perform an energy balance on the ceiling to calculate the corresponding values of the ceiling temperature for the given emissivities of 0.05 (highly reflective panels) and 0.94 (painted panels). Using the heat balance equation stated above, and calculating the radiative heat transfer coefficient (hr) for each case, we can solve for the ceiling temperature (T_c). Recall that: \(Q_{conv} = h_c \times A \times (T_c - T_{air}) \) \(Q_{rad} = h_r \times A \times (T_c^4 - T_{wall}^4) \) In steady state condition, \(Q_{conv} = Q_{rad}\).
03

Calculate dew point and determine condensation

To determine whether condensation will occur for the calculated ceiling temperatures, we need to calculate the dew point of the rink air at the given relative humidity of 70%. We will use the approximation formula: \(T_{dew} \approx T_{air} - \frac{100 - RH}{5} \) where \(T_{dew}\) is the dew point temperature, and RH is the relative humidity in percentage. Once we have the dew point, we can compare it to the calculated ceiling temperatures. If the ceiling temperatures fall below the dew point, condensation will occur, leading to the formation of bumps on the skating surface.
04

Calculate and plot the ceiling temperature as a function of insulation thickness

Now, we need to calculate the ceiling temperature as a function of insulation thickness for both emissivities. To do this, we can use the same energy balance equation from step 2. However, this time, we will vary the insulation thickness value (r) between 0.1 m to 1 m. Using a spreadsheet or other mathematical software, you can create a plot of the ceiling temperature vs. insulation thickness for both emissivities, and identify the conditions under which condensation will occur on the ceiling. By completing these steps, the analysis and calculations can be made to determine the effect of ceiling emissivity on the ceiling temperature and propensity for condensation.

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Key Concepts

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

Energy Balance
In the context of heat transfer within an ice-skating rink, a crucial aspect to understand is the energy balance of the ceiling. The ceiling, acting as a barrier between the indoor rink environment and the outside conditions, interacts with both radiative and convective heat transfers.

At the core, the energy balance refers to the equilibrium condition where the rate of energy entering a system equals the rate of energy leaving it. For the rink's ceiling, this involves two primary heat transfer mechanisms:In practice, the energy balance is maintained when the convective and radiative heat transfers are equal, denoting a steady-state: \(Q_{conv} = Q_{rad}\). Understanding this balance is key to analyzing how changes in surface conditions affect the ceiling temperature.

By adjusting factors like insulation thickness or surface emissivity, we can manipulate the energy balance to control the ceiling temperature, crucial for predicting condensation occurrence.
Condensation on Ceilings
Condensation is a phenomenon that occurs when the temperature of a surface drops below the dew point of the surrounding air. In ice rinks, condensation on ceilings can lead to water droplets forming and dripping onto the ice surface, causing imperfections and safety hazards.

To predict whether condensation will occur on the rink's ceiling, understanding the dew point is essential. The dew point is the temperature at which air becomes saturated and water vapor begins to condense into liquid droplets. It depends on the air temperature and its relative humidity. For the exercise, the dew point is estimated through the formula:
\(T_{dew} \approx T_{air} - \frac{100 - RH}{5}\)
where \(RH\) stands for the relative humidity percentage.

In the case of the skating rink, if the ceiling's temperature, calculated through the energy balance analysis, is below this dew point, condensation will likely occur. The design choice of materials, such as using reflective paints to change emissivity, significantly impacts this outcome. Rinks aim to maintain ceiling temperatures above the dew point, often employing solutions like enhanced insulation or reflective surfaces to mitigate condensation risks.

These strategies are crucial for successful rink operation, ensuring that environmental controls prevent condensation, thereby preserving both the ice quality and safety.
Radiative and Convective Heat Transfer
The concepts of radiative and convective heat transfer are fundamental in analyzing heat exchange in systems like the ice rink. Each type of heat transfer is influenced by different factors which directly affect the energy balance of the ceiling.

**Radiative Heat Transfer** is the emission or absorption of electromagnetic radiation from surfaces. Unlike conduction or convection, it does not require contact or movement of molecules. Instead, it depends on a surface's emissivity, a measure of its ability to emit energy as thermal radiation. Higher emissivity means more heat loss, often undesirable in retaining a temperature balance.
- **Influencing Factors:**
  • Emissivity of the surface.
  • Temperature difference between surfaces involved.
  • Surface area exposure.

**Convective Heat Transfer** involves the transfer of heat between a surface and a fluid (air in this case) moving over it. This process is strongly influenced by the temperature difference between the ceiling and the air, the speed of air movement, characterized by the convection coefficient.
- **Influencing Factors:**
  • Temperature difference (\(T_c - T_{air}\)).
  • Velocity of surrounding air, impacting the convection coefficient.
  • Physical properties of the fluid, like viscosity.

Both these types of heat transfer are critical in determining whether the ceiling will experience a temperature drop leading to condensation. By controlling these variables—either through material choices that affect emissivity or architectural designs affecting air flow—it's possible to effectively manage the thermal profile of the rink's ceiling, ensuring a stable and safe skating environment.

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Most popular questions from this chapter

A novel infrared recycler has been proposed for reclaiming the millions of kilograms of waste plastics produced by the dismantling and shredding of automotive vehicles following their refirement. To address the problem of sorting mixed plastics into components such as polypropylene and polycarbonate, a washed stream of the mixed plastics is routed to an infrared heating system, where it is dried and stbsequently heated to a temperature for which one of the components begins to soften, while the others remain rigid. The mixed stream is then routed through steel rollers, to which the softened plastic sticks and is removed from the stream. Heating of the stream is then continued to facilitate removal of a second component, and the heating/removal process is repeated until all of the components are separated. Consider the initial drying stage for a system comprised of a cylindrical heater aligned coaxially with a rotating drum of diameter \(D_{d}=1 \mathrm{~m}\). Shortly after entering the drum, wet plastic pellets may be assumed to fully cover the bottom semicylindrical section and to remain at a temperature of \(T_{p}=\) \(325 \mathrm{~K}\) during the drying process. The surface area of the pellets may be assumed to correspond to that of the semicylinder and to have an emissivity of \(\varepsilon_{p}=0.95\). (a) If the flow of dry air through the drum maintains a convection mass transfer coefficient of \(0.024 \mathrm{~m} / \mathrm{s}\) on the surface of the pellets, what is the evaporation rate per unit length of the drum? (b) Neglecting convection heat transfer, determine the temperature \(T_{b}\) that must be maintained by a heater of diameter \(D_{\mathrm{b}}=0.10 \mathrm{~m}\) and emissivity \(\varepsilon_{h}=0.8\) to sustain the foregoing evaporation rate. What is the corresponding value of the temperature \(T_{d}\) for the top surface of the drum? The outer surface of the dram is well insulated, and its length-to-diameter ratio is large. As applied to the top \((d)\) or bottom \((p)\) surface of the drum, the view factor of an infinitely long semicylinder to itself, in the presence of a concentric, coaxial cylinder, may be expressed as $$ \begin{aligned} F_{U}=& 1-\frac{2}{\pi}\left\\{\left[1-\left(D_{d} / D_{d}\right)^{2}\right]^{1 / 2}\right.\\\ &\left.+\left(D_{k} / D_{d}\right) \sin ^{-1}\left(D_{h} / D_{d}\right)\right\\} \end{aligned} $$

The lower side of a \(400-\mathrm{mm}\)-diameter disk is heated by an electric furnace, while the upper side is exposed to quiescent, ambient air and sumoundings at \(300 \mathrm{~K}\). The radiant furnace (negligible convection) is of circular construction with the bottoen surface \(\left(\alpha_{1}-0.6\right)\) and cylindrical side surface \(\left(\varepsilon_{1}=1.0\right)\) maintained af \(T_{1}=T_{2}=500 \mathrm{~K}\). The surface of the disk facing the radiant furnace is black \(\left(\varepsilon_{d, 1}=1.0\right)\). while the upper surface has an emissivity of \(\varepsilon_{d, 2}=0.8\). Assume the plate and furnace surfaces to be diffuse and gray. (a) Determine the net heat transfer rate to the disk, \(q_{\text {nated, when }} T_{d}=400 \mathrm{~K}\). (b) Plot \(q_{\text {netd as a }}\) a function of the disk temperature for \(300 \leq T_{a} \leq 500 \mathrm{~K}\), with all other conditions remaining the same. What is the steady-state temperature of the disk?

A row of regularly spaced, cylindrical heating elements (1) is used to cure a surface coating that is applied to a large panel (2) positioned below the elements. A second large panel (3), whose top surface is well insulated, is positioned above the elements. The elements are black and maintained at \(T_{1}=600 \mathrm{~K}\). while the panel has an emissivity of \(\varepsilon_{2}=0.5\) and is maintained at \(T_{2}=400 \mathrm{~K}\). The cavity is filled with a nonparticipating gas and convection heat transfer occurs at surfaces 1 and 2 , with \(\bar{h}_{1}=10 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) and \(\bar{h}_{2}=2 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\). (Convection at the insulated panel may be neglected.) (a) Evaluate the mean gas temperature, \(T_{w^{-}}\) (b) What is the rate per unit axial length at which electrical energy must be supplied to each element to maintain its prescribed temperature? (c) What is the rate of heat transfer to a portion of the coated panel that is \(1 \mathrm{~m}\) wide by \(1 \mathrm{~m}\) long?

An electronic device dissipating \(50 \mathrm{~W}\) is attached to the inner surface of an isothermal cubical container that is \(120 \mathrm{~mm}\) on a side. The container is located in the much larger service bay of the space shuttle, which is evacuated and whose walls are at \(150 \mathrm{~K}\). If the outer surface of the container has an emissivity of \(0.8\) and the thermal resistance between the surface and the device is \(0.1 \mathrm{~K} / \mathrm{W}\), what are the temperatures of the surface and the device? All surfaces of the container may be assumed to exchange radiation with the service bay, and heat transfer through the container restraint may be neglected.

An opaque, diffuse, gray ( \(200 \mathrm{~mm} \times 200 \mathrm{~mm})\) plate with an emissivity of \(0.8\) is placed over the opening of a furnace and is known to be at \(400 \mathrm{~K}\) at a certain instant. The bottom of the fumace, having the same dimensions as the plate, is black and operates at \(1000 \mathrm{~K}\). The sidewalls of the fumace are well insulated. The top of the plate is exposed to ambient air with a convection coefficient of \(25 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) and to large surroundings. The air and surroundings are each at \(300 \mathrm{~K}\). (a) Evaluate the net radiative heat transfer to the bottom surface of the plate. (b) If the plate has mass and specific heat of \(2 \mathrm{~kg}\) and \(900 \mathrm{~J} / \mathrm{kg} \cdot \mathrm{K}\), respectively, what will be the change in temperature of the plate with time, \(d T_{p} / d r\) ? Assume convection to the bottom surface of the plate to be negligible. (c) Extending the analysis of part (b), generate a plot of the change in temperature of the plate with time, \(d T_{\rho} / d l\), as a function of the plate temperature for \(350 \leq T_{p} \leq 900 \mathrm{~K}\) and all other conditions remaining the same. What is the steady-state tem-

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