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Using EES (or other) software, investigate the effect of reheat pressure on the performance of an ideal Rankine cycle. The maximum and minimum pressures in the cycle are \(15 \mathrm{MPa}\) and \(10 \mathrm{kPa}\) respectively, and steam enters both stages of the turbine at \(500^{\circ} \mathrm{C}\). The reheat pressure is varied from 12.5 to 0.5 MPa. Determine the thermal efficiency of the cycle and plot it against the reheat pressure, and discuss the results.

Short Answer

Expert verified
Answer: The reheat pressure affects the thermal efficiency of the ideal Rankine cycle by changing the work and heat transfer in the cycle components. By varying the reheat pressure, we can calculate the thermal efficiency for different reheat pressures. By plotting these values, it's possible to analyze and discuss the impact of reheat pressure on the performance of the Rankine cycle.

Step by step solution

01

Understand the Ideal Rankine Cycle with Reheat

An ideal Rankine cycle with reheat consists of four components: a boiler, a turbine, a condenser, and a pump. The working fluid undergoes a series of thermodynamic processes as it flows through these components. The reheat process is an additional step that aims to improve the cycle efficiency by reheating the working fluid before it enters the second stage of the turbine.
02

Determine the States of the Working Fluid

In order to analyze the Rankine cycle, we need to determine the state of the working fluid at each point in the cycle. The following conditions are given: 1. Maximum Pressure: \(P_{1} = 15 \mathrm{MPa}\) 2. Minimum Pressure: \(P_{4} = 10 \mathrm{kPa}\) 3. Temperature at turbine stages: \(T_{1} = 500^{\circ} \mathrm{C} = T_{2}\) We can find the following points in the cycle: 1. State 1: At the exit of the boiler and entrance to the high-pressure turbine, the fluid is at maximum pressure and temperature (\(T_{1}\) and \(P_{1}\)). 2. State 2: At the exit of the high-pressure turbine and entrance to the reheater, the fluid is at the reheat pressure \(P_{2}\) and temperature \(T_{2} = 500^{\circ} \mathrm{C}\). 3. State 3: At the exit of reheater and entrance to the low-pressure turbine, the fluid is at temperature \(T_{3} = T_{2}\) and pressure \(P_{3} = P_{2}\). 4. State 4: At the exit of the low-pressure turbine and entrance to the condenser, the fluid is at minimum pressure (\(P_{4}\)). We can assume it to be a saturated liquid-vapor mixture (\(x_{4}\), quality). Finding enthalpy at these points will help us find the work and heat of the cycle.
03

Calculate the Work and Heat of the Cycle

We can use the following equations to find the work and heat of the cycle: 1. Turbine Work (\(W_{T}\)): \(W_{T} = W_{T,1} + W_{T,2} = (h_{1} - h_{2}) + (h_{3} - h_{4})\) 2. Pump Work (\(W_{P}\)): \(W_{P} = v_{f} \cdot (P_{1} - P_{4})\) 3. Boiler Heat (\(Q_{B}\)): \(Q_{B} = Q_{B,1} + Q_{B,2} = (h_{1} - h_{f_{4}}) + (h_{3} - h_{2})\) Here, \(h_{i}\) represents the enthalpy at state \(i\), \(v_{f}\) is the specific volume of the saturated liquid at \(P_{4}\), and \(x_{4}\) is the quality of the working fluid at state 4.
04

Calculate the Thermal Efficiency of the Cycle

Thermal efficiency (\(\eta\)) of the cycle can be calculated using the following formula: \(\eta = \frac{W_{net}}{Q_{B}} = \frac{W_{T} - W_{P}}{Q_{B}}\)
05

Vary the Reheat Pressure and Plot the Results

By varying the reheat pressure (\(P_{2}\)) from 12.5 MPa to 0.5 MPa, we can calculate the thermal efficiency of the Rankine cycle for different reheat pressures. By plotting these values, we can analyze the impact of reheat pressure on thermal efficiency and discuss the results. To summarize, we have analyzed the ideal Rankine cycle with reheat, determined the states of the working fluid, calculated the work and heat of the cycle, and found the thermal efficiency. By plotting the thermal efficiency against various reheat pressures, we can discuss the impact of reheat pressure on the performance of the Rankine cycle.

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Most popular questions from this chapter

A textile plant requires \(4 \mathrm{kg} / \mathrm{s}\) of saturated steam at \(2 \mathrm{MPa},\) which is extracted from the turbine of a cogeneration plant. Steam enters the turbine at \(8 \mathrm{MPa}\) and \(500^{\circ} \mathrm{C}\) at a rate of \(11 \mathrm{kg} / \mathrm{s}\) and leaves at \(20 \mathrm{kPa}\). The extracted steam leaves the process heater as a saturated liquid and mixes with the feedwater at constant pressure. The mixture is pumped to the boiler pressure. Assuming an isentropic efficiency of 88 percent for both the turbine and the pumps, determine \((a)\) the rate of process heat supply, \((b)\) the net power output, and \((c)\) the utilization factor of the plant.

A steam Rankine cycle operates between the pressure limits of 1500 psia in the boiler and 2 psia in the condenser. The turbine inlet temperature is \(800^{\circ} \mathrm{F}\). The turbine isentropic efficiency is 90 percent, the pump losses are negligible, and the cycle is sized to produce \(2500 \mathrm{kW}\) of power. Calculate the mass flow rate through the boiler, the power produced by the turbine, the rate of heat supply in the boiler, and the thermal efficiency.

Consider a simple ideal Rankine cycle with fixed boiler and condenser pressures. If the cycle is modified with reheating, \((a)\) the turbine work output will decrease. \((b)\) the amount of heat rejected will decrease. \((c)\) the pump work input will decrease. \((d)\) the moisture content at turbine exit will decrease. \((e)\) the amount of heat input will decrease.

Consider a cogeneration power plant that is modified with reheat and that produces \(3 \mathrm{MW}\) of power and supplies \(7 \mathrm{MW}\) of process heat. Steam enters the high-pressure turbine at \(8 \mathrm{MPa}\) and \(500^{\circ} \mathrm{C}\) and expands to a pressure of 1 MPa. At this pressure, part of the steam is extracted from the turbine and routed to the process heater, while the remainder is reheated to \(500^{\circ} \mathrm{C}\) and expanded in the low-pressure turbine to the condenser pressure of 15 kPa. The condensate from the condenser is pumped to 1 MPa and is mixed with the extracted steam, which leaves the process heater as a compressed liquid at \(120^{\circ} \mathrm{C}\). The mixture is then pumped to the boiler pressure. Assuming the turbine to be isentropic, show the cycle on a \(T\) -s diagram with respect to saturation lines, and disregarding pump work, determine \((a)\) the rate of heat input in the boiler and \((b)\) the fraction of steam extracted for process heating.

How is the utilization factor \(\epsilon_{u}\) for cogeneration plants defined? Could \(\epsilon_{u}\) be unity for a cogeneration plant that does not produce any power?

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