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A 2-m-internal-diameter double-walled spherical tank is used to store iced water at \(0^{\circ} \mathrm{C}\). Each wall is \(0.5 \mathrm{~cm}\) thick, and the \(1.5-\mathrm{cm}\)-thick airspace between the two walls of the tank is evacuated in order to minimize heat transfer. The surfaces surrounding the evacuated space are polished so that each surface has an emissivity of \(0.15\). The temperature of the outer wall of the tank is measured to be $20^{\circ} \mathrm{C}\(. Assuming the inner wall of the steel tank to be at \)0^{\circ} \mathrm{C}\(, determine \)(a)$ the rate of heat transfer to the iced water in the tank and \((b)\) the amount of ice at \(0^{\circ} \mathrm{C}\) that melts during a 24 -h period.

Short Answer

Expert verified
Answer: Approximately 94.26 kg.

Step by step solution

01

Calculate the surface area of the inner wall

First, we need to find the surface area of the inner wall of the tank. The inner wall has a radius of 1 m (given that the diameter is 2 m). The formula for the surface area of a sphere is given by \(A = 4\pi r^2\). Therefore, the surface area of the inner wall of the tank is: \(A = 4\pi (1)^2 = 4\pi \mathrm{m^2}\).
02

Determine the heat transfer through radiation

Next, we need to find the rate of heat transfer through radiation between the inner wall and the outer wall of the tank. The formula for heat transfer through radiation is given by \(Q = \sigma A \epsilon (T_h^4 - T_c^4)\), where \(\sigma\) is the Stefan-Boltzmann constant (\(5.67 \times 10^{-8}\mathrm{W/(m^2K^4)}\)), \(A\) is the surface area, \(\epsilon\) is the emissivity, \(T_h\) is the temperature of the hotter body, and \(T_c\) is the temperature of the colder body. We are given the temperature of the outer wall (\(20^{\circ} \mathrm{C}\)) and emissivity of the surfaces (\(0.15\)). In order to get the temperature values in Kelvin, we need to add \(273.15\) (\(0^{\circ} \mathrm{C} = 273.15 \mathrm{K}\) and \(20^{\circ} \mathrm{C} = 293.15 \mathrm{K}\)). We can now plug in the values into the formula to find the rate of heat transfer: \(Q = (5.67 \times 10^{-8}\mathrm{W/(m^2K^4)})(4\pi \mathrm{m^2})(0.15)(293.15^4 - 273.15^4)\) Calculating the heat transfer rate, we get \(Q \approx 109.67 \mathrm{W}\).
03

Find the amount of ice that melts during a 24-hour period

To find the amount of ice that melts during a 24-hour period, we need to consider the heat required to change the phase of ice at \(0^{\circ} \mathrm{C}\) to water at \(0^{\circ} \mathrm{C}\). The formula for heat transfer is given by \(Q = mc\Delta T + mL\) where \(m\) is the mass of ice, \(c\) is the specific heat capacity of ice (\(2100 \mathrm{J/(kgK)}\)), \(\Delta T\) is the temperature difference (0 in this case as both ice and water are at \(0^{\circ} \mathrm{C}\)), and \(L\) is the latent heat of fusion for ice (\(333,000 \mathrm{J/kg}\)). We want to find the mass (\(m\)) of ice that melts. Since \(\Delta T = 0\), the heat transfer equation simplifies to \(Q = mL\). The total heat transfer during a 24-hour period is given by \(Q_t = Qt\), where \(t\) is the time period (24 hours) in seconds: \(Q_t = (109.67 \mathrm{W}) \times (24 \times 3600 \mathrm{s})\) Now we can solve for the mass of ice that melts: \(m = \frac{Q_t}{L} = \frac{(109.67 \mathrm{W} \times 24 \times 3600 \mathrm{s})}{333,000 \mathrm{J/kg}}\) Calculating the mass, we get \(m \approx 94.26 \mathrm{kg}\).
04

Final Answers

Therefore, the answers to the given problem are: \((a)\) The rate of heat transfer to the iced water in the tank is approximately \(109.67 \mathrm{W}\). \((b)\) The amount of ice at \(0^{\circ} \mathrm{C}\) that melts during a 24-hour period is approximately \(94.26 \mathrm{kg}\).

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Most popular questions from this chapter

Consider a \(3-\mathrm{m} \times 3-\mathrm{m} \times 3-\mathrm{m}\) cubical furnace. The base surface is black and has a temperature of \(400 \mathrm{~K}\). The radiosities for the top and side surfaces are calculated to be $7500 \mathrm{~W} / \mathrm{m}^{2}\( and \)3200 \mathrm{~W} / \mathrm{m}^{2}$, respectively. If the temperature of the side surfaces is \(485 \mathrm{~K}\), the emissivity of the side surfaces is (a) \(0.37\) (b) \(0.55\) (c) \(0.63\) (d) \(0.80\) (e) \(0.89\)

A large ASTM A992 carbon steel plate is $(k=10 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\(. The ceramic plate has a thickness of \)10 \mathrm{~cm}$, with its lower surface at \(T_{0}=800^{\circ} \mathrm{C}\) and upper surface at \(T_{1}=700^{\circ} \mathrm{C}\). The upper surface of the ceramic plate faces the carbon steel plate. Convection occurs on the upper surface of the ceramic plate with air at \(20^{\circ} \mathrm{C}\) and a convection heat transfer coefficient of \(12 \mathrm{~W} / \mathrm{m}^{2}, \mathrm{~K}\). The ceramic and steel plates have emissivity values of \(0.93\) and \(0.75\), respectively. The ASME Code for Process Piping specifies the maximum use temperature suitable for ASTM A992 carbon steel to be \(427^{\circ} \mathrm{C}\) (ASME B31.3-2014, Table A-1M). A radiation shield is to be placed in parallel between the two plates to keep the temperature of the steel plate from exceeding its maximum use temperature. Determine the emissivity that the radiation shield needs to keep the steel plate surface from exceeding \(427^{\circ} \mathrm{C}\).

A 3-m spherical tank storing cold fluid has a uniform surface temperature of \(T_{1}=5^{\circ} \mathrm{C}\). The lower temperature of the tank surface is causing condensation of moisture in the air at \(13^{\circ} \mathrm{C}\) and a dew point at \(10^{\circ} \mathrm{C}\). If the outer surface temperature of the tank drops below the dew point, condensation can occur on the surface. The tank is situated in the vicinity of high-voltage devices, and water from the condensation on the tank surface can cause electrical hazards. In an attempt to remedy the situation, the tank is enclosed with a concentric outer cover that provides an evacuated gap in the enclosure. On the outer surface, the natural convection heat transfer coefficient is $3 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}$, and radiation exchange with the surroundings is negligible. If the emissivity of the tank and the concentric outer cover is the same at \(0.6\), determine the necessary gap of the vacuumed enclosure so that the outer cover surface temperature is not below the dew point of \(10^{\circ} \mathrm{C}\).

How does radiation transfer through a participating medium differ from that through a nonparticipating medium?

This question deals with steady-state radiation heat transfer between a sphere \(\left(r_{1}=30 \mathrm{~cm}\right)\) and a circular disk $\left(r_{2}=120 \mathrm{~cm}\right)\(, which are separated by a center-to-center distance \)h=60 \mathrm{~cm}$. When the normal to the center of the disk passes through the center of the sphere, the radiation view factor is given by $$ F_{12}=0.5\left\\{1-\left[1+\left(\frac{r_{2}}{h}\right)^{2}\right]^{-0.5}\right\\} $$ Surface temperatures of the sphere and the disk are \(600^{\circ} \mathrm{C}\) and \(200^{\circ} \mathrm{C}\), respectively; and their emissivities are \(0.9\) and \(0.5\), respectively. (a) Calculate the view factors \(F_{12}\) and \(F_{21}\). (b) Calculate the net rate of radiation heat exchange between the sphere and the disk. (c) For the given radii and temperatures of the sphere and the disk, the following four possible modifications could increase the net rate of radiation heat exchange: paint each of the two surfaces to alter their emissivities, adjust the distance between them, and provide an (refractory) enclosure. Calculate the net rate of radiation heat exchange between the two bodies if the best values are selected for each of the above modifications.

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