Chapter 9: Problem 11
What is the maximum possible thermal efficiency of a gas power cycle when using thermal energy reservoirs at \(1100^{\circ} \mathrm{F}\) and \(80^{\circ} \mathrm{F} ?\)
Chapter 9: Problem 11
What is the maximum possible thermal efficiency of a gas power cycle when using thermal energy reservoirs at \(1100^{\circ} \mathrm{F}\) and \(80^{\circ} \mathrm{F} ?\)
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Get started for freeSomebody claims that at very high pressure ratios, the use of regeneration actually decreases the thermal efficiency of a gas-turbine engine. Is there any truth in this claim? Explain.
In an ideal Otto cycle, air is compressed from \(1.20 \mathrm{kg} / \mathrm{m}^{3}\) and 2.2 to \(0.26 \mathrm{L},\) and the net work output of the cycle is \(440 \mathrm{kJ} / \mathrm{kg} .\) The mean effective pressure (MEP) for this cycle is \((a) 612 \mathrm{kPa}\) \((b) 599 \mathrm{kPa}\) \((c) 528 \mathrm{kPa}\) \((d) 416 \mathrm{kPa}\) \((e) 367 \mathrm{kPa}\)
The single-stage compression process of an ideal Brayton cycle without regeneration is replaced by a multistage compression process with intercooling between the same pressure limits. As a result of this modification, (a) Does the compressor work increase, decrease, or remain the same? (b) Does the back work ratio increase, decrease, or remain the same? \((c) \quad\) Does the thermal efficiency increase, decrease, or remain the same?
Electricity and process heat requirements of a manufacturing facility are to be met by a cogeneration plant consisting of a gas turbine and a heat exchanger for steam production. The plant operates on the simple Brayton cycle between the pressure limits of 100 and 1000 kPa with air as the working fluid. Air enters the compressor at \(20^{\circ} \mathrm{C}\). Combustion gases leave the turbine and enter the heat exchanger at \(450^{\circ} \mathrm{C},\) and leave the heat exchanger of \(325^{\circ} \mathrm{C},\) while the liquid water enters the heat exchanger at \(15^{\circ} \mathrm{C}\) and leaves at \(200^{\circ} \mathrm{C}\) as a saturated vapor. The net power produced by the gas-turbine cycle is \(1500 \mathrm{kW}\). Assuming a compressor isentropic efficiency of 86 percent and a turbine isentropic efficiency of 88 percent and using variable specific heats, determine \((a)\) the mass flow rate of air, \((b)\) the back work ratio and the thermal efficiency, and \((c)\) the rate at which steam is produced in the heat exchanger. Also determine \((d)\) the utilization efficiency of the cogeneration plant, defined as the ratio of the total energy utilized to the energy supplied to the plant.
An air-standard Diesel cycle has a compression ratio of \(18.2 .\) Air is at \(120^{\circ} \mathrm{F}\) and 14.7 psia at the beginning of the compression process and at \(3200 \mathrm{R}\) at the end of the heataddition process. Accounting for the variation of specific heats with temperature, determine \((a)\) the cutoff ratio, \((b)\) the heat rejection per unit mass, and ( \(c\) ) the thermal efficiency.
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