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Cold water \(\left(c_{p}=4.18 \mathrm{kJ} / \mathrm{kg} \cdot^{\circ} \mathrm{C}\right)\) leading to a shower enters a well-insulated, thin-walled, double-pipe, counterflow heat exchanger at \(15^{\circ} \mathrm{C}\) at a rate of \(0.25 \mathrm{kg} / \mathrm{s}\) and is heated to \(45^{\circ} \mathrm{C}\) by hot water \(\left(c_{p}=4.19 \mathrm{kJ} / \mathrm{kg} \cdot^{\circ} \mathrm{C}\right)\) that enters at \(100^{\circ} \mathrm{C}\) at a rate of \(3 \mathrm{kg} / \mathrm{s}\). Determine \((a)\) the rate of heat transfer and \((b)\) the rate of exergy destruction in the heat exchanger. Take \(T_{0}=25^{\circ} \mathrm{C}\)

Short Answer

Expert verified
Answer: The rate of heat transfer (a) is 31.35 kW and the rate of exergy destruction (b) is 0.6 kW.

Step by step solution

01

Calculate the Rate of Heat Transfer

Since both the hot and cold water have different heat capacities, we need to first calculate the energy transferred between the two fluids using the following formula: $$Q = \dot{m}_c c_{p_c} (T_{out_c} - T_{in_c}) = \dot{m}_h c_{p_h} (T_{in_h} - T_{out_h})$$ where \(Q\) is the rate of heat transfer, \(\dot{m}_c\) and \(\dot{m}_h\) are the mass flow rates of cold and hot water, respectively, \(c_{p_c}\) and \(c_{p_h}\) are the heat capacities of cold and hot water, and \(T_{in}\) and \(T_{out}\) represent the inlet and outlet temperatures of cold (\(c\)) and hot (\(h\)) fluids, respectively. We are given: $$\dot{m}_c = 0.25~kg/s, ~c_{p_c} = 4.18~kJ/(kg \cdot^{\circ} C), ~T_{in_c} = 15^{\circ} C, ~T_{out_c}= 45^{\circ} C$$ $$\dot{m}_h = 3~kg/s, ~c_{p_h} = 4.19~kJ/(kg \cdot^{\circ} C), ~T_{in_h} = 100^{\circ} C$$ Substituting these values, we can find \(T_{out_h}\): $$Q = 0.25 \cdot 4.18 \cdot (45 - 15) = 3 \cdot 4.19 \cdot (100 - T_{out_h})$$ $$Q = 31.35~kW$$ Solving for \(T_{out_h}\): $$100 - T_{out_h} = \frac{31.35}{12.57}$$ $$T_{out_h} = 75^{\circ} C$$
02

Calculate the Rate of Exergy Destruction

To find the rate of exergy destruction, we need to first determine the exergy change for both the cold and hot water streams. The exergy change can be calculated using the following formula: $$\Delta Ex = \dot{m} c_p T_0 (T_{out} - T_{in}) \left (1 - \frac{T_0}{(T_{in} + T_{out}) / 2} \right)$$ Calculating the exergy change for the cold water stream: $$\Delta Ex_c = 0.25 \cdot 4.18 \cdot 25 (45 - 15) \left(1 - \frac{25}{(15 + 45) / 2} \right)$$ $$\Delta Ex_c = 9.435~kW$$ Calculating the exergy change for the hot water stream: $$\Delta Ex_h = 3 \cdot 4.19 \cdot 25 (75 - 100) \left(1 - \frac{25}{(75 + 100) / 2} \right)$$ $$\Delta Ex_h = -8.835~kW$$ The rate of exergy destruction can now be found using the second law of thermodynamics: $$\Delta Ex_d = \Delta Ex_c + \Delta Ex_h$$ $$\Delta Ex_d = 9.435 - 8.835$$ $$\Delta Ex_d = 0.6~kW$$ So the rate of heat transfer \((a)\) is \(31.35~kW\), and the rate of exergy destruction \((b)\) is \(0.6~kW\).

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Most popular questions from this chapter

A hot-water stream at \(160^{\circ} \mathrm{F}\) enters an adiabatic mixing chamber with a mass flow rate of \(4 \mathrm{lbm} / \mathrm{s}\), where it is mixed with a stream of cold water at \(70^{\circ} \mathrm{F}\). If the mixture leaves the chamber at \(110^{\circ} \mathrm{F}\), determine \((a)\) the mass flow rate of the cold water and \((b)\) the exergy destroyed during this adiabatic mixing process. Assume all the streams are at a pressure of 50 psia and the surroundings are at \(75^{\circ} \mathrm{F}\).

To control an isentropic steam turbine, a throttle valve is placed in the steam line leading to the turbine inlet. Steam at \(6 \mathrm{MPa}\) and \(600^{\circ} \mathrm{C}\) is supplied to the throttle inlet, and the turbine exhaust pressure is set at \(40 \mathrm{kPa}\). What is the effect on the stream exergy at the turbine inlet when the throttle valve is partially closed such that the pressure at the turbine inlet is 2 MPa. Compare the second-law efficiency of this system when the valve is partially open to when it is fully open. Take \(T_{0}=25^{\circ} \mathrm{C}\).

Argon gas enters an adiabatic turbine at \(1300^{\circ} \mathrm{F}\) and 200 psia at a rate of \(40 \mathrm{lbm} / \mathrm{min}\) and exhausts at 20 psia. If the power output of the turbine is 105 hp, determine ( \(a\) ) the isentropic efficiency and \((b)\) the second-law efficiency of the turbine. Assume the surroundings to be at \(77^{\circ} \mathrm{F}\).

Oxygen gas is compressed in a piston-cylinder device from an initial state of \(12 \mathrm{ft}^{3} / \mathrm{lbm}\) and \(75^{\circ} \mathrm{F}\) to a final state of \(1.5 \mathrm{ft}^{3} / \mathrm{lbm}\) and \(525^{\circ} \mathrm{F}\). Determine the reversible work input and the increase in the exergy of the oxygen during this process. Assume the surroundings to be at 14.7 psia and \(75^{\circ} \mathrm{F}\).

A heat engine receives heat from a source at \(1100 \mathrm{K}\) at a rate of \(400 \mathrm{kJ} / \mathrm{s},\) and it rejects the waste heat to a medium at \(320 \mathrm{K}\). The measured power output of the heat engine is \(120 \mathrm{kW}\), and the environment temperature is \(25^{\circ} \mathrm{C}\). Determine \((a)\) the reversible power, (b) the rate of irreversibility, and \((c)\) the second-law efficiency of this heat engine.

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