/*! 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 49 Air initially at 1 atm and \(500... [FREE SOLUTION] | 91Ó°ÊÓ

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Air initially at 1 atm and \(500^{\circ} \mathrm{R}\) with a mass of \(2.5 \mathrm{lb}\) is contained within a closed, rigid tank. The air is slowly warmed, receiving 100 Btu by heat transfer through a wall separating the gas from a thermal reservoir at \(800^{\circ} \mathrm{R}\). This is the only energy transfer. Assuming the air undergoes an internally reversible process and using the ideal gas model, (a) determine the change in exergy and the exergy transfer accompanying heat, each in Btu, for the air as the system. (b) determine the exergy transfer accompanying heat and the exergy destruction, each in Btu, for an enlarged system that includes the air and the wall, assuming that the state of the wall remains unchanged. Compare with part (a) and comment. Let \(T_{0}=90^{\circ} \mathrm{F}, p_{0}=1 \mathrm{~atm}\).

Short Answer

Expert verified
a) ΔX = 72.45 Btu, Q exergy = 31.25 Btu b) Xd = 41.2 Btu

Step by step solution

01

Identify Given Values

Mass, m = 2.5 lb. Initial Pressure, P = 1 atm. Initial Temperature, T1 = 500 °R. Heat transfer, Q = 100 Btu. Final Temperature, T2 = 800 °R. Ambient Temperature, T0 = 90 °F, which is equivalent to 550 °R.
02

Define the Ideal Gas Properties

Using the ideal gas model, the specific heat at constant volume (cv) for air is cv = 0.171 Btu/lb. °R and the specific heat at constant pressure (cp) is cp = 0.24 Btu/lb. °R.
03

Determine the Change in Internal Energy

Change in internal energy, ΔU = m * cv * (T2 - T1) = 2.5 lb * 0.171 Btu/lb.°R * (800 °R - 500 °R) = 128.25 Btu
04

Calculate the Exergy Change of the Air

Change in exergy ΔX = ΔU - T0 * ΔS To find ΔS: ΔS = m * cv * ln(T2/T1), ΔS = 2.5 lb * 0.171 Btu/lb.°R * ln(800/500) = 0.316 Btu/°R ΔX = 128.25 Btu - 550 °R * 0.316 Btu/°R ≈ 72.45 Btu
05

Determine the Exergy Transfer Accompanying Heat

Exergy transfer = Q * (1 - T0/T2) = 100 Btu * (1 - 550 °R / 800 °R) = 31.25 Btu
06

Determine the Exergy Destruction and compare with (a)

This includes the wall. Exergy destruction, Xd = ( ΔX air) + ( X transfer) + ( ΔX wall or surroundings) However, wall remains unchanged (no exergy change in surroundings) ΔX total = Q * (1 - T0/T2) = 31.25 Btu Thus, exergy destroyed, Xd = 72.45 Btu - 31.25 Btu = 41.2 Btu
07

Comment

The exergy destroyed accounts for the irreversibility within the process. Including the wall in the system removes the boundary effects but destruction remains because of temperature differential irreversibility.

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Key Concepts

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

Exergy Transfer
Exergy transfer refers to the transfer of available energy that can do useful work. It is a measure of energy quality. When heat is transferred, some of the energy can be converted into work, while some is dissipated as irreversibilities. In the given problem, 100 Btu of heat is transferred to the air, resulting in an exergy transfer of 31.25 Btu. This is calculated using the formula:
Exergy transfer = Q * (1 - T0/T2)
Where Q is the heat transfer, T0 is the ambient temperature, and T2 is the final temperature. Since T0 = 550 °R and T2 = 800 °R:
Exergy transfer = 100 Btu * (1 - 550/800) = 31.25 Btu
Understanding exergy transfer helps in identifying how much useful work can be extracted from a thermal system and how much is lost due to inefficiencies.
Ideal Gas Model
The ideal gas model is a simplified way to describe the behavior of gases. It assumes that gas particles are point masses that interact only through elastic collisions. In thermodynamics, the ideal gas model allows us to relate pressure, volume, and temperature through the equation of state:
PV = nRT
Where P is pressure, V is volume, n is the number of moles, R is the gas constant, and T is temperature. In the problem, air, treated as an ideal gas, undergoes heating. Using this model simplifies calculations for changes in internal energy and entropy. The specific heats at constant volume (cv) and constant pressure (cp) are essential in calculating these changes:
For air, cv = 0.171 Btu/lb.°R and cp = 0.24 Btu/lb.°R. These values help determine the change in internal energy and entropy during the heating process.
Internally Reversible Process
An internally reversible process is one in which no irreversibilities occur within the system. This means that the process can be reversed without leaving any net change in the system and surroundings. In the given problem, the air is heated in a manner that can be considered internally reversible. This assumption simplifies the analysis and allows us to use thermodynamic properties like entropy effectively.
The change in entropy (ΔS) during such a process can be calculated using:
ΔS = m * cv * ln(T2/T1)
Where m is the mass of the air, cv is the specific heat at constant volume, T2 is the final temperature, and T1 is the initial temperature. For the given values:
ΔS = 2.5 lb * 0.171 Btu/lb.°R * ln(800/500) = 0.316 Btu/°R
Understanding internally reversible processes helps us know how entropy changes without additional complexities.
Change in Internal Energy
The change in internal energy (ΔU) for a system describes the variation in energy contained within the substance as its temperature changes. This concept is crucial in thermodynamics because it provides insight into how much energy is being gained or lost by the system. For the given problem, the change in internal energy for the air while being heated is calculated as follows:
ΔU = m * cv * (T2 - T1)
Where m is the mass, cv is the specific heat at constant volume, T2 is the final temperature, and T1 is the initial temperature. Substituting the given values:
ΔU = 2.5 lb * 0.171 Btu/lb.°R * (800 °R - 500 °R) = 128.25 Btu
The change in internal energy indicates how much the energy content of the air has increased due to the heat transfer.

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Most popular questions from this chapter

Oxygen \(\left(\mathrm{O}_{2}\right)\) enters a well-insulated nozzle operating at steady state at \(80 \mathrm{lbf}\) in. \({ }^{2}, 1100^{\circ} \mathrm{R}, 90 \mathrm{ft} / \mathrm{s}\) At the nozle exit, the pressure is 1 lbf/in. \({ }^{2}\) The isentropic nozle efficiency is \(85 \%\). For the nozle, determine the exit velocity, in \(\mathrm{m} / \mathrm{s}\), and the exergy destruction rate, in Btu per lb of oxygen flowing. Let \(T_{0}=70^{\circ} \mathrm{F}, p_{0}=14.7 \mathrm{lbf} / \mathrm{in}^{2}\)

A stream of hot water at \(300^{\circ} \mathrm{F}, 500 \mathrm{lbf} / \mathrm{in}^{2}\), and a velocity of \(20 \mathrm{ft} / \mathrm{s}\) is obtained from a geothermal supply. Determine the specific flow exergy, in Btu/lb. The velocity is relative to the exergy reference environment for which \(T_{0}=77^{\circ} \mathrm{F}, p_{0}=\) \(1 \mathrm{~atm}\). Neglect the effect of gravity.

Refrigerant \(134 a\) enters a counterflow heat exchanger operating at steady state at \(-32^{\circ} \mathrm{C}\) and a quality of \(40 \%\) and exits as saturated vapor at \(-32^{\circ} \mathrm{C}\). Air enters as a separate sticam with a unass fluw 1 ate of \(5 \mathrm{~kg} / \mathrm{s}\) and is couleal al a constant pressure of 1 bar from 300 to \(250 \mathrm{~K}\). Heat transfer between the heat exchanger and its surroundings can be ignored, as can the effects of motion and gravity. (a) As in Fig. E7.6, sketch the variation with position of the temperature of each stream. Locate \(T_{0}\) on the sketch. (b) Determine the rate of exergy destruction within the heat exchanger, in \(\mathrm{kW}\). (c) Devise and evaluate an exergetic efficiency for the heat exchanger. Let \(T_{0}=300 \mathrm{~K}, p_{0}=1\) bar.

Air is compressed in an axial-flow compressor operating at steady state from \(27^{\circ} \mathrm{C}, 1\) bar to a pressure of \(2.1\) bar. The work required is \(94.6 \mathrm{~kJ}\) per \(\mathrm{kg}\) of air flowing. Heat transfer from the compressor occurs at an average surface temperature of \(40^{\circ} \mathrm{C}\) at the rate of \(14 \mathrm{~kJ}\) per \(\mathrm{kg}\) of air flowing. The effects of motion and gravity can be ignored. Let \(T_{0}=20^{\circ} \mathrm{C}, p_{0}=\) 1 bar. Assuming ideal gas behavior, (a) determine the temperature of the air at the exit, in \({ }^{\circ} \mathrm{C}\), (b) determine the rate of exergy destruction within the compressor, in kJ per \(\mathrm{kg}\) of air flowing, and (c) perform a full exergy accounting. in \(\mathrm{kJ}\) per \(\mathrm{kg}\) of air flowing, based on work input.

Air enters an insulated turbine operating at steady state with a pressure of 5 bar, a temperature of \(500 \mathrm{~K}\), and a volumetric flow rate of \(3 \mathrm{~m}^{3} / \mathrm{s}\). At the exit, the pressure is 1 bar. The isentropic turbine efficiency is \(76.7 \%\). Assuming the ideal gas model and ignoring the effects of motion and gravity, determine (a) the power developed and the exergy destruction rate, each in \(\mathrm{kW}\). (b) the exergetic turbine efficiency. Let \(T_{0}=20^{\circ} \mathrm{C}, p_{0}=1\) bar.

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