/*! 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

An experimental arrangement for measuring the thermal conductivity of solid materials involves the use of two long rods that are equivalent in every respect, except that one is fabricated from a standard material of known thermal conductivity \(k_{\mathrm{A}}\) while the other is fabricated from the material whose thermal conductivity \(k_{\mathrm{B}}\) is desired. Both rods are attached at one end to a heat source of fixed temperature \(T_{b}\), are exposed to a fluid of temperature \(T_{\infty}\), and are instrumented with thermocouples to measure the temperature at a fixed distance \(x_{1}\) from the heat source. If the standard material is aluminum, with \(k_{\mathrm{A}}=200 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\), and measurements reveal values of \(T_{\mathrm{A}}=75^{\circ} \mathrm{C}\) and \(T_{\mathrm{B}}=60^{\circ} \mathrm{C}\) at \(x_{1}\) for \(T_{b}=100^{\circ} \mathrm{C}\) and \(T_{\infty}=25^{\circ} \mathrm{C}\), what is the thermal conductivity \(k_{\mathrm{B}}\) of the test material?

The wind chill, which is experienced on a cold, windy day, is related to increased heat transfer from exposed human skin to the surrounding atmosphere. Consider a layer of fatty tissue that is \(3 \mathrm{~mm}\) thick and whose interior surface is maintained at a temperature of \(36^{\circ} \mathrm{C}\). On a calm day the convection heat transfer coefficient at the outer surface is \(25 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\), but with \(30 \mathrm{~km} / \mathrm{h}\) winds it reaches \(65 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\). In both cases the ambient air temperature is \(-15^{\circ} \mathrm{C}\). (a) What is the ratio of the heat loss per unit area from the skin for the calm day to that for the windy day? (b) What will be the skin outer surface temperature for the calm day? For the windy day? (c) What temperature would the air have to assume on the calm day to produce the same heat loss occurring with the air temperature at \(-15^{\circ} \mathrm{C}\) on the windy day?

In a test to determine the friction coefficient \(\mu\) associated with a disk brake, one disk and its shaft are rotated at a constant angular velocity \(\omega\), while an equivalent disk/shaft assembly is stationary. Each disk has an outer radius of \(r_{2}=180 \mathrm{~mm}\), a shaft radius of \(r_{1}=20 \mathrm{~mm}\), a thickness of \(t=12 \mathrm{~mm}\), and a thermal conductivity of \(k=15 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K}\). A known force \(F\) is applied to the system, and the corresponding torque \(\tau\) required to maintain rotation is measured. The disk contact pressure may be assumed to be uniform (i.e., independent of location on the interface), and the disks may be assumed to be well insulated from the surroundings. (a) Obtain an expression that may be used to evaluate \(\mu\) from known quantities. (b) For the region \(r_{1} \leq r \leq r_{2}\), determine the radial temperature distribution \(T(r)\) in the disk, where \(T\left(r_{1}\right)=T_{1}\) is presumed to be known. (c) Consider test conditions for which \(F=200 \mathrm{~N}\), \(\omega=40 \mathrm{rad} / \mathrm{s}, \tau=8 \mathrm{~N} \cdot \mathrm{m}\), and \(T_{1}=80^{\circ} \mathrm{C}\). Evaluate the friction coefficient and the maximum disk temperature.

An air heater consists of a steel tube \((k=20 \mathrm{~W} / \mathrm{m} \cdot \mathrm{K})\), with inner and outer radii of \(r_{1}=13 \mathrm{~mm}\) and \(r_{2}=16\) \(\mathrm{mm}\), respectively, and eight integrally machined longitudinal fins, each of thickness \(t=3 \mathrm{~mm}\). The fins extend to a concentric tube, which is of radius \(r_{3}=\) \(40 \mathrm{~mm}\) and insulated on its outer surface. Water at a temperature \(T_{\infty, i}=90^{\circ} \mathrm{C}\) flows through the inner tube, while air at \(T_{\infty, o}=25^{\circ} \mathrm{C}\) flows through the annular region formed by the larger concentric tube. (a) Sketch the equivalent thermal circuit of the heater and relate each thermal resistance to appropriate system parameters. (b) If \(h_{i}=5000 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) and \(h_{o}=200 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\), what is the heat rate per unit length? (c) Assess the effect of increasing the number of fins \(N\) and/or the fin thickness \(t\) on the heat rate, subject to the constraint that \(N t<50 \mathrm{~mm}\).

Finned passages are frequently formed between parallel plates to enhance convection heat transfer in compact heat exchanger cores. An important application is in electronic equipment cooling, where one or more air-cooled stacks are placed between heat-dissipating electrical components. Consider a single stack of rectangular fins of length \(L\) and thickness \(t\), with convection conditions corresponding to \(h\) and \(T_{\infty}\). (a) Obtain expressions for the fin heat transfer rates, \(q_{f, o}\) and \(q_{f, L}\), in terms of the base temperatures, \(T_{o}\) and \(T_{L}\). (b) In a specific application, a stack that is \(200 \mathrm{~mm}\) wide and \(100 \mathrm{~mm}\) deep contains 50 fins, each of length \(L=12 \mathrm{~mm}\). The entire stack is made from aluminum, which is everywhere \(1.0 \mathrm{~mm}\) thick. If temperature limitations associated with electrical components joined to opposite plates dictate maximum allowable plate temperatures of \(T_{o}=400 \mathrm{~K}\) and \(T_{L}=350 \mathrm{~K}\), what are the corresponding maximum power dissipations if \(h=150 \mathrm{~W} / \mathrm{m}^{2} \cdot \mathrm{K}\) and \(T_{\infty}=300 \mathrm{~K} ?\)

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