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At steady state, hot gaseous products of combustion from a gas turbine cool from \(3000^{\circ} \mathrm{F}\) to \(250^{\circ} \mathrm{F}\) as they flow through a pipe. Owing to negligible fluid friction, the flow occurs at nearly constant pressure. Applying the ideal gas model with \(c_{p}=0.3 \mathrm{Btu} / \mathrm{lb} \cdot{ }^{\circ} \mathrm{R}\), determine the exergy transfer accompanying heat transfer from the gas, in Btu per lb of gas flowing. Let \(T_{0}=80^{\circ} \mathrm{F}\) and ignore the effects of motion and gravity.

Short Answer

Expert verified
Pouring 3000ç defefgh (3-50045467)+++++=. 9,9..

Step by step solution

01

Convert Temperatures to Absolute Scale

To use the given values in the equations, convert Fahrenheit to Rankine (^{eq). The formula to convert Fahrenheit to Rankine is T_R = T_F + 459.67. Therefore: T_{initial} = 3000^{eq} F + 459.67 = 3459.67^{eq} R and T_{final} = 250^{eq} F + 459.67 = 709.67^{eq} R.
02

Convert Dead State Temperature to Absolute Scale

T_{0} = 80^{eq} F + 459.67 = 539.67^{eq} R.
03

Calculate Change in Exergy Transfer

The exergy transfer (Q_{ex}) associated with heat transfer can be determined using the formula: Q_{ex} = c_{p} * [(T_{0} * ln(T^{eq})/T_{0}) + (T_{inital} - T_{final}). Plug in the given values: c_{p} = (0.3 Btu/lb * ^{eq} R),T_0 = (539.67 ^{eq} RT_{initial} = (3459.67^{eq} R) and T_{last} = (709.67^{eq) R which gives us: Q_{ex} = 0.3 * [539.67 ln(709.67/539.67) + (3459.67-709.67).
04

Step 4

Calculate the numerical value by solving inside the parentheses first and then multiplying by c_{p} :ln(3459.67/539.67)=0.295(move the 0.3):Q_{ex}=0.3*539.67*0.295+++++, multiply and simplify, so the exergy transfer accompanying heat transfer is :Q_{ex}= <**9.5 B=tu/lb**> after all, final solution is,Q_{ex}=9.=

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Key Concepts

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

Ideal Gas Model
The ideal gas model is a simplification used in thermodynamics to describe the behavior of gases. In this model, gases are assumed to follow the Ideal Gas Law, which states that the product of pressure (P) and volume (V) is directly proportional to the product of the number of moles (n), the gas constant (R), and the temperature (T). Mathematically, it is represented as:
\[ PV = nRT \]
In the ideal gas model, gas molecules are assumed to occupy negligible volume and exert no intermolecular forces on each other. This model simplifies calculations by providing a straightforward relationship between the state variables of a gas.
In the context of the exercise, the ideal gas model allows us to use the specific heat capacity at constant pressure (\[ c_p \]) to calculate the exergy transfer. Remember, specific heat capacity (\[ c_p \]) is the amount of heat required to raise the temperature of 1 pound of gas by 1-degree Rankine (R).
Exergy Transfer
Exergy transfer is a measure of the usable energy that accompanies a process, such as heat transfer, within a thermodynamic system. It accounts for both the energy carried by the heat and the temperature at which this energy is transferred.
The formula for exergy transfer (\[Q_{ex}\]) associated with heat transfer is:
\[ Q_{ex} = c_p * \big( T_0 \times ln \big( \frac{T_{final}}{T_0} \big) + (T_{initial} - T_{final} ) \big) \]
In this equation:
  • \[c_p \] is the specific heat capacity.
  • T_0 is the dead state temperature (the reference temperature of the environment).
  • T_{initial} and T_{final} are the initial and final temperatures of the gas, respectively.
By incorporating the natural logarithm of the temperature ratio and the difference in temperatures, this formula helps us calculate the amount of exergy, in Btu per lb of gas flowing, transferred during the cooling process.
Steady State Heat Transfer
In steady state heat transfer, the temperatures and other properties of the system remain constant over time, even though heat is being transferred. This means any heat entering or leaving the system does so at a constant rate.
In the exercise, the hot gaseous products of combustion are at steady state as they cool from 3000°F to 250°F.
Ignoring fluid friction and assuming constant pressure, we can simplify our calculations significantly. Under these conditions, the first law of thermodynamics dictates that the rate of heat loss by the gas must equal the rate of heat gain by the surroundings.
Rankine to Fahrenheit Conversion
To work with temperatures in thermodynamic equations, it's often necessary to convert between different temperature units. The Rankine (°R) scale is the absolute scale associated with Fahrenheit (°F). The conversion between Fahrenheit and Rankine is straightforward:
\[ T_R = T_F + 459.67 \]
In this equation,
  • \[T_R \] is the temperature in Rankine
  • \[T_F \] is the temperature in Fahrenheit

For example,
  • The initial temperature in the exercise is 3000°F, which converts to 3459.67°R.
  • The final temperature is 250°F, converting to 709.67°R.
  • The dead state temperature of the environment, 80°F, converts to 539.67°R.

These conversions are vital, as thermodynamic equations require absolute temperatures (e.g., in Rankine) to ensure accurate calculations.

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Most popular questions from this chapter

Determine the specific exergy, in Btu, of one pound mass of (a) saturated liquid Refrigerant \(134 a\) at \(-5^{\circ} \mathrm{F}\) - (b) saturated vapor Refrigerant \(134 a\) at \(140^{\circ} \mathrm{F}\). (c) Refrigerant \(134 \mathrm{a}\) at \(60^{\circ} \mathrm{F}, 20 \mathrm{lbf} / \mathrm{in} .^{2}\) (d) Refrigerant \(134 \mathrm{a}\) at \(60^{\circ} \mathrm{F}, 10 \mathrm{lbf} / \mathrm{in}^{2}{ }^{2}\) In each case, consider a fixed mass at rest and zero elevation relative to an exergy reference environment for which \(T_{0}=\) \(60^{\circ} \mathrm{F}, p_{0}=15 \mathrm{lbt} / \mathrm{in}^{2}\)

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.

The sun shines on a \(300-\mathrm{ft}^{2}\) south-facing wall, maintaining that surface at \(98^{\circ} \mathrm{F}\). Temperature varies linearly through the wall and is \(77^{\circ} \mathrm{F}\) at its other surface. The wall thickness is 6 inches and its thermal conductivity is \(0.04 \mathrm{Btu} / \mathrm{h} \cdot \mathrm{ft}{ }^{\circ} \mathrm{R}\). Assuming steady state, determine the rate of exergy destruction within the wall, in Btu/h. Let \(T_{0}=77^{\circ} \mathrm{F}\).

Saturated water vapor at \(400 \mathrm{lbf} / \mathrm{in}^{2}\) enters an insulated turbine operating at steady state. At the turbine exit the pressure is \(0.6\) lbf/in. \({ }^{2}\) The work developed is 306 Btu per pound of steam passing through the turbine. Kinetic and potential energy effects can be neglected. Let \(T_{0}=60^{\circ} \mathrm{F}\), \(p_{0}=1 \mathrm{~atm}\). Determine (a) the exergy destruction rate, in Btu per pound of steam expanding through the turbine. (b) the isentropic turbine efficiency- (c) the exergetic turbine efficiency.

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.

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