/*! 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 24 A firefighter's protective cloth... [FREE SOLUTION] | 91Ó°ÊÓ

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A firefighter's protective clothing, referred to as a turnout coat, is typically constructed as an ensemble of three layers separated by air gaps, as shown schematically. The air gaps between the layers are \(1 \mathrm{~mm}\) thick, and heat is transferred by conduction and radiation exchange through the stagnant air. The linearized radiation coefficient for a gap may be approximated as, \(h_{\text {rad }}=\sigma\left(T_{1}+T_{2}\right)\left(T_{1}^{2}+T_{2}^{2}\right) \approx 4 \sigma T_{\text {avg }}^{3}\), where \(T_{\text {avg }}\) represents the average temperature of the surfaces comprising the gap, and the radiation flux across the gap may be expressed as \(q_{\text {rad }}^{\prime \prime}=h_{\text {rad }}\left(T_{1}-T_{2}\right)\). (a) Represent the turnout coat by a thermal circuit, labeling all the thermal resistances. Calculate and tabulate the thermal resistances per unit area \(\left(\mathrm{m}^{2}\right.\). \(\mathrm{K} / \mathrm{W}\) ) for each of the layers, as well as for the conduction and radiation processes in the gaps. Assume that a value of \(T_{\mathrm{avg}}=470 \mathrm{~K}\) may be used to approximate the radiation resistance of both gaps. Comment on the relative magnitudes of the resistances. (b) For a pre-ash-over fire environment in which firefighters often work, the typical radiant heat flux on the fire-side of the turnout coat is \(0.25 \mathrm{~W} / \mathrm{cm}^{2}\). What is the outer surface temperature of the turnout coat if the inner surface temperature is \(66^{\circ} \mathrm{C}\), a condition that would result in burn injury?

Short Answer

Expert verified
When analyzing a firefighter's protective clothing, known as a turnout coat, we can represent it as a thermal circuit with three layers separated by two air gaps. To determine the outer surface temperature of the coat when exposed to a radiant heat flux of 0.25 W/cm², we first calculate the thermal resistance per unit area for each layer and air gap, using the given equations for conduction and radiation resistances. Then, we can calculate the total thermal resistance (sum of each individual resistance) and use the following equation to determine the outer surface temperature: \(T_{outer} = q'' \times R_{total} + T_{inner}\), where \(q''\) is the given heat flux and \(T_{inner}\) is the inner surface temperature.

Step by step solution

01

Develop the thermal circuit with resistances

To represent the turnout coat as a thermal circuit, we first identify the layers and air gaps. We have 3 layers separated by two air gaps. The thermal circuit would then look like this: ("Fire-side surface" -/-> [R_gap1] -/-> [R_layer1] -/-> [R_gap2] -/-> [R_layer2] -/-> [R_gap3] -/-> [R_layer3] -/-> "Inner surface") where R_gap1, R_gap2, and R_gap3 represent the thermal resistances of the air gaps between layers, and R_layer1, R_layer2, and R_layer3 represent the thermal resistances of the three layers themselves.
02

Calculate the thermal resistances

To determine the thermal resistances per unit area, we can use the following formulas for conduction and radiation resistances: Conduction Resistance: \(R_{cond} = \frac{t}{kA}\), where t is the thickness of the layer, k is the thermal conductivity, and A is the area. Radiation Resistance: \(R_{rad} = \frac{1}{h_{rad}A}\), where h_rad is the linearized radiation coefficient and A is the area. For the air gaps, the conduction and radiation resistances must be summed to get the total air gap resistance. Using the given equation for the linearized radiation coefficient: \(h_{rad} = 4 \sigma T_{avg}^3\) Assuming that a value of \(T_{avg} = 470 K\) may be used to approximate the radiation resistance of both gaps, calculate the resistances for each layer and gap using the appropriate formulas.
03

Comment on the relative magnitudes of the resistances

Once the resistances have been tabulated, compare the values to make observations about the relative magnitudes of the resistances. This will provide insights into the effectiveness of the material and design in protecting the firefighter from burn injuries.
04

Calculate the outer surface temperature

Now that we have the thermal resistances for each layer and gap, we can solve for the outer surface temperature when exposed to a radiant heat flux of 0.25 W/cm². To do this, we can use the thermal circuit that we developed in step 1. For a pre-ash-over fire environment, we know that the typical radiant heat flux on the fire-side surface of the coat is 0.25 W/cm², and that the inner surface temperature is 66 °C (a temperature that would result in burn injury). Using the thermal circuit and applying Ohm's law for heat transfer analogous to the electrical analogy, we have: \(q'' = \frac{T_{outer} - T_{inner}}{R_{total}}\) Because we know the heat flux, inner surface temperature, and the total thermal resistance (sum of each individual resistance), we can solve for the outer surface temperature of the coat: \(T_{outer} = q'' \times R_{total} + T_{inner}\)

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Key Concepts

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

Understanding Heat Transfer
When we talk about heat transfer in the context of materials like a firefighter's protective clothing, we're referring to the movement of thermal energy from one place to another. There are three main modes of heat transfer: conduction, convection, and radiation. In the case of a firefighter's turnout coat, heat is predominantly transferred through the layers by conduction and radiation.

Conductive heat transfer occurs when there is a physical contact between objects at different temperatures. It relies on the material's ability to conduct heat, which is quantified by its thermal conductivity. Essentially, higher thermal conductivity materials enable the heat to pass through more readily. Meanwhile, radiation heat transfer depends on the emission of infrared radiation from a hot surface, which can occur even across a vacuum where no physical contact is needed.

Understanding these heat transfer mechanisms is crucial when designing protective clothing to ensure that firefighters are not exposed to excessive heat, leading to burns or more serious injuries.
Exploring Thermal Circuits
A thermal circuit is a conceptual model used to simplify complex heat transfer problems. It is analogous to an electrical circuit, where heat transfer is represented in terms of resistances to heat flow, just as electrical resistances impede the flow of current. In a thermal circuit, the total thermal resistance is the sum of individual resistances, each corresponding to different materials or processes, such as conductive paths through materials or radiative paths across air gaps.

In our firefighter's turnout coat example, the thermal circuit involves multiple layers of fabric and air gaps, each with their own thermal resistance. By quantitatively analyzing such a circuit, engineers can design protective clothing that provides the necessary thermal insulation while maintaining comfort and mobility for the firefighter. This concept allows for the analysis and comparison of different materials and configurations in a clear and structured manner.
Radiation Heat Transfer in Action
Radiation heat transfer is one of the key modes through which heat can be transferred in the absence of a medium, such as across air gaps in protective clothing. It is the energy emitted by matter due to its temperature and occurs through electromagnetic waves or photons. The Stefan-Boltzmann law governs this emission, and materials emit radiation in amounts related to their surface temperature and emissivity.

In the example of the turnout coat, heat from a fire radiates towards the coat and is partly absorbed and partly reflected. The absorbed heat can then be transferred to the firefighter, which is undesirable. This is where the design using air gaps comes into play. The air itself doesn't conduct heat well, and the radiation exchange across these gaps can be quantified, as in the given exercise, using the radiation heat transfer coefficient. Understanding and calculating the radiation heat transfer coefficient is crucial because it defines the protective capabilities of the coat in high-temperature environments.
Conductive Heat Transfer in Protective Layers
Conductive heat transfer is the direct microscopic exchange of kinetic energy of particles through the boundary between two systems. In materials, such as the layers of a firefighter's turnout coat, conduction occurs as heat is transferred through the material itself. The rate of conductive heat transfer depends on the temperature gradient within the material, its cross-sectional area, thickness, and thermal conductivity.

The protective layers in turnout gear must have a low thermal conductivity to minimize the rate of heat transfer to the firefighter's body. For the turnout coat, calculating the conductive thermal resistance involves examining the thickness and thermal conductivity of each layer, as described in the steps of our exercise. By combining these calculations with those for radiation transfer, one can evaluate the performance of the turnout coat and ensure it offers sufficient protection against external heat sources while allowing internal heat from the firefighter's body to escape, thus maintaining a balance between protection and comfort.

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Most popular questions from this chapter

Consider the conditions of Problem \(3.149\) but now allow for a tube wall thickness of \(5 \mathrm{~mm}\) (inner and outer diameters of 50 and \(60 \mathrm{~mm}\) ), a fin-to-tube thermal contact resistance of \(10^{-4} \mathrm{~m}^{2} \cdot \mathrm{K} / \mathrm{W}\), and the fact that the water temperature, \(T_{w}=350 \mathrm{~K}\), is known, not the tube surface temperature. The water-side convection coefficient is \(h_{w}=2000 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\). Determine the rate of heat transfer per unit tube length \((\mathrm{W} / \mathrm{m})\) to the water. What would be the separate effect of each of the following design changes on the heat rate: (i) elimination of the contact resistance; (ii) increasing the number of fins from four to eight; and (iii) changing the tube wall and fin material from copper to AISI 304 stainless steel \((k=20\) \(\mathrm{W} / \mathrm{m} \cdot \mathrm{K})\) ?

Superheated steam at \(575^{\circ} \mathrm{C}\) is routed from a boiler to the turbine of an electric power plant through steel tubes \((k=35 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\) of \(300-\mathrm{mm}\) inner diameter and \(30-\mathrm{mm}\) wall thickness. To reduce heat loss to the surroundings and to maintain a safe-to-touch outer surface temperature, a layer of calcium silicate insulation \((k=0.10 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\) is applied to the tubes, while degradation of the insulation is reduced by wrapping it in a thin sheet of aluminum having an emissivity of \(\varepsilon=0.20\). The air and wall temperatures of the power plant are \(27^{\circ} \mathrm{C}\). (a) Assuming that the inner surface temperature of a steel tube corresponds to that of the steam and the convection coefficient outside the aluminum sheet is \(6 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\), what is the minimum insulation thickness needed to ensure that the temperature of the aluminum does not exceed \(50^{\circ} \mathrm{C}\) ? What is the corresponding heat loss(b) Explore the effect of the insulation thickness on the temperature of the aluminum and the heat loss per unit tube length. per meter of tube length?

In Problem 3.48, the electrical power required to maintain the heater at \(T_{o}=25^{\circ} \mathrm{C}\) depends on the thermal conductivity of the wall material \(k\), the thermal contact resistance \(R_{t, c}^{\prime}\) and the convection coefficient \(h\). Compute and plot the separate effect of changes in \(k\) \((1 \leq k \leq 200 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}), \quad R_{t, c}^{\prime} \quad\left(0 \leq R_{t, c}^{\prime} \leq 0.1 \mathrm{~m} \cdot \mathrm{K} / \mathrm{W}\right)\), and \(h\left(10 \leq h \leq 1000 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\right)\) on the total heater power requirement, as well as the rate of heat transfer to the inner surface of the tube and to the fluid.

Consider the composite wall of Example 3.7. In the Comments section, temperature distributions in the wall were determined assuming negligible contact resistance between materials A and B. Compute and plot the temperature distributions if the thermal contact resistance is \(R_{t, c}^{\prime \prime}=10^{-4} \mathrm{~m}^{2} \cdot \mathrm{K} / \mathrm{W}\).

A 40-mm-long, 2-mm-diameter pin fin is fabricated of an aluminum alloy \((k=140 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\). (a) Determine the fin heat transfer rate for \(T_{b}=50^{\circ} \mathrm{C}\), \(T_{\infty}=25^{\circ} \mathrm{C}, h=1000 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\), and an adiabatic tip condition. (b) An engineer suggests that by holding the fin tip at a low temperature, the fin heat transfer rate can be increased. For \(T(x=L)=0^{\circ} \mathrm{C}\), determine the new fin heat transfer rate. Other conditions are as in part (a). (c) Plot the temperature distribution, \(T(x)\), over the range \(0 \leq x \leq L\) for the adiabatic tip case and the prescribed tip temperature case. Also show the ambient temperature in your graph. Discuss relevant features of the temperature distribution. (d) Plot the fin heat transfer rate over the range \(0 \leq h \leq 1000 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) for the adiabatic tip case and the prescribed tip temperature case. For the prescribed tip temperature case, what would the

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