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Devise a refrigeration cycle that works on the reversed Stirling cycle. Also, determine the COP for this cycle.

Short Answer

Expert verified
Answer: The formula for the COP is given by: \(COP = \frac{T_3 - T_2}{(T_2 - T_1) + (T_4 - T_3)}\)

Step by step solution

01

Understand the Stirling Cycle

The Stirling cycle consists of the following processes: 1. Isothermal compression 2. Isochoric heat removal 3. Isothermal expansion 4. Isochoric heat addition
02

Devise the Reversed Stirling Cycle

In a reversed Stirling cycle, the processes will be reversed. Thus the processes are: 1. Isothermal expansion 2. Isochoric heat addition 3. Isothermal compression 4. Isochoric heat removal The reversed Stirling cycle can be used to model a refrigeration cycle since it involves heat absorption (Isochoric heat addition) and heat rejection (Isochoric heat removal), along with thermodynamic work input (Isothermal compression).
03

Apply the First Law of Thermodynamics for Each Process

We will apply the first law of thermodynamics for each process to calculate the heat transfers and work inputs or outputs: 1. Isothermal expansion: \(\Delta Q_1 = W_1 = mC_v(T_2 - T_1)\) 2. Isochoric heat addition: \(\Delta Q_2 = mC_v(T_3 - T_2) = W_2 = 0\) 3. Isothermal compression: \(\Delta Q_3 = W_3 = mC_v(T_4 - T_3)\) 4. Isochoric heat removal: \(\Delta Q_4 = mC_v(T_4 - T_1) = W_4 = 0\)
04

Calculate the COP

The COP for the refrigeration cycle is given by: $$ COP = \frac{\text{Desired Output (Heat Absorption)}}{\text{Required Input (Work)}} = \frac{Q_2}{W_1 + W_3} $$ Substitute the heat transfers and work values from Step 3 into the equation: $$ COP = \frac{mC_v(T_3 - T_2)}{mC_v(T_2 - T_1) + mC_v(T_4 - T_3)} $$ To simplify the equation, observe that \(mC_v\) appears in all terms, and hence can be canceled out: $$ COP = \frac{T_3 - T_2}{(T_2 - T_1) + (T_4 - T_3)} $$ Now, we have derived the COP for the refrigeration cycle based on the reversed Stirling cycle.

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Most popular questions from this chapter

A reversible absorption refrigerator consists of a reversible heat engine and a reversible refrigerator. The system removes heat from a cooled space at \(-15^{\circ} \mathrm{C}\) at a rate of \(70 \mathrm{kW}\) The refrigerator operates in an environment at \(25^{\circ} \mathrm{C}\). If the heat is supplied to the cycle by condensing saturated steam at \(150^{\circ} \mathrm{C},\) determine \((a)\) the rate at which the steam condenses, and (b) the power input to the reversible refrigerator. (c) If the COP of an actual absorption chiller at the same temperature limits has a COP of \(0.8,\) determine the second-law efficiency of this chiller.

Air enters the compressor of an ideal gas refrigeration cycle at \(40^{\circ} \mathrm{F}\) and 10 psia and the turbine at \(120^{\circ} \mathrm{F}\) and 30 psia. The mass flow rate of air through the cycle is 0.5 lbm/s. Determine \((a)\) the rate of refrigeration, \((b)\) the net power input, and ( \(c\) ) the coefficient of performance.

A space is kept at \(-15^{\circ} \mathrm{C}\) by a vapor-compression refrigeration system in an ambient at \(25^{\circ} \mathrm{C}\). The space gains heat steadily at a rate of \(3500 \mathrm{kJ} / \mathrm{h}\) and the rate of heat rejection in the condenser is \(5500 \mathrm{kJ} / \mathrm{h}\). Determine the power input, in \(\mathrm{kW}\), the COP of the cycle and the second-law efficiency of the system.

Why is the reversed Carnot cycle executed within the saturation dome not a realistic model for refrigeration cycles?

An ideal vapor compression refrigeration cycle with \(\mathrm{R}-134 \mathrm{a}\) as the working fluid operates between the pressure limits of \(120 \mathrm{kPa}\) and \(700 \mathrm{kPa}\). The mass fraction of the refrigerant that is in the liquid phase at the inlet of the evaporator is \((a) 0.69\) (b) 0.63 \((c) 0.58\) \((d) 0.43\) \((e) 0.35\)

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