Received 29 August 2015; accepted 5 May 2016; published 11 May 2016

ABSTRACT

The performance parameters of vapor compression refrigeration units that used the refrigerant R-404A were studied by developing a computer simulation algorithm. The various performance parameters investigated per one kilowatt of refrigeration capacity, such as the mass flow rate, the compressor power consumption, the condenser heat rejection rate, the compressor exit temperature and the coefficient of performance. Two refrigeration cycles were tested under various evaporating and condensing temperatures: the standard cycle and the ideal cycle with superheating and sub-cooling. The results of the present work reveal that the compressor power variation over the evaporating temperature range from −10˚C to 15˚C at Tc = 40˚C is decreased by 38.8% for standard cycle and by 43.8% for ideal cycle. The compressor power variation over the condensing temperature range from 30˚C to 50˚C at Te = 10˚C is increased by 122% for standard cycle and by 54.5% for ideal cycle. On the other hand, the COP for the ideal cycle with 5˚C superheating and sub- cooling is approximately 25% higher than that of the standard cycle at Te = 10˚C and Tc = 40˚C for the refrigerant R-404A.

Keywords:

Refrigeration Units, R-404A, Computer Simulation, Refrigeration Performance Parameters

1. Introduction

During the last period, several chlorofluorocarbons (CFCs) and hydrochlorofluorocarbons (HCFCs) are phasing out due to their negative influence on the environment. Alternative refrigerants such as R-404 A, which is a blend, colorless, odorless mixture of a near azeotropic blend (44% R125, 52% R143a and 4% R134a), are being used and introduced as a replacement for ozone depleting refrigerants. Motta et al. [1] investigated experimentally the critical flow of azeotropic mixtures R-407a and R-404A through adiabatic capillary tubes. The results were presented in both graphical and tabulated forms and were intended to be a contribution to the development of environmentally benign refrigeration systems. Zhang and Webb [2] developed a new correlation for two- phase friction pressure drop in small diameter tubes by modifying the Friedel correlation. Motta et al. [3] explored a visual study of R-404A/oil flow through adiabatic capillary tubes, with special emphasis on the behavior of the vaporization point. The results showed trends of mass flow rate, and gave some useful insights about the location of the vaporization point for various oil concentrations and operating conditions. Ould Didi et al. [4] predicted the two-phase pressure gradients of refrigerants during evaporation in two horizontal test sections for five refrigerants (R-134a, R-123, R-402A, R-404A and R-502). These data have then been compared against seven two-phase frictional pressure drop prediction methods. It was observed that the peak in the two- phase frictional pressure gradient at high vapor qualities coincided with the onset of dryout in the annular flow regime. Llopis et al. [5] presented the experimental performance evaluation, from an energy point of view, of R-404A and R507A refrigerant mixtures in an experimental double-stage vapor compression plant driven by a compound compressor. Zhou et al. [6] presented an experimental study on pulsed spray cooling with refrigerant R-404A in laser surgery. With a low boiling point (−45.5˚C at 1 atm) and high volatility, cryogen R-404A has the potential to replace current R-134a (−26.1˚C at 1 atm) for improved therapeutic outcome of dark skins in continuous laser treatment. Sapali and Pradeep [7] investigated experimentally the heat transfer during condensation of HFC-134a and R-404A inside of a horizontal smooth and micro-fin tube. New correlations based on the data gathered during the experimentation for predicting condensation heat transfer coefficients are proposed for wide range of operating conditions. Chena and Kruseb [8] developed simulation program to study concentration shift for the mixed refrigerants R-404A, R-32/134a, and R-407C in an air conditioning system. Furthermore, this program was used to predict the concentration shift and associated performance changes for the alternative refrigerant mixtures R-407C, R-32/134a and R-404A. The simulation technique was extensively used in testing refrigeration systems using different refrigerants with different conditions, which means the cost of using laboratory equipment for experimental tests and effort can be reduced.

Jung and Radermacher [9] performed a computer simulation of single-evaporator domestic refrigerators that charged with pure and mixed refrigerants had been in an attempt to screen out the best substitutes for R12. More efficient heat exchangers are recommended as one of the means of increasing energy efficiency. Alshqirate [10] used the computer simulation technique to investigate the performance of a window type air-conditioning unit that used the refrigerant R-407c instead of R-22. Joudi et al. [11] presented an experimental and computer performance study of an automotive air conditioning system with alternative refrigerants. The major part of this work was an experimental investigation for the use of R290/R600a as a drop-in alternative for R-12 in a prototype automotive air conditioning system. The results of this work showed good agreement with the experimental and theoretical results available in the literature. The DuPont [12] have been developed and presented tables of the thermodynamic properties of R-404A based on extensive experimental measurements.

The present work developed computer simulation software to study the various performance parameters in a refrigeration unit that used the refrigerant R-404A. The performance parameters are obtained using the saturated standard refrigeration cycle and the ideal cycle with super-heating and sub-cooling for various evaporator and condenser temperatures.

2. Refrigeration Cycle Calculations

The main components of the refrigeration cycle were shown in Figure 1.

Standard refrigeration cycle and ideal cycle with superheating and sub-cooling can be used to predict the performance of the vapor compression cycle, which requires a complete set of refrigerant thermodynamic properties. The standard vapor-compression cycle consist of isobaric heat transfer in condenser and evaporator, isentropic compression and irreversible adiabatic expansion as shown in Figure 2.

The states of ideal vapor-compression cycle with superheating and sub-cooling are shown in Figure 3.

The various performance parameters of the standard cycle are calculated per one kilowatt of refrigeration capacity i.e..

Referring to the figures, the refrigerant mass flow rate in (kg/s) per kW of refrigeration capacity, m, is obtained as follows:

(1)

where

h_e,o = Specific enthalpy leaving the evaporator and entering the compressor in kJ/kg.

h_e,i = Specific Enthalpy entering the evaporator and leaving the condenser in kJ/kg.

The compressor power, , in (kW) per kW of refrigeration is given as:

(2)

where

h_c,o = Specific enthalpy at compressor outlet and equal to enthalpy entering the condenser in kJ/kg.

The heat rejection, , in the condenser in (kW) per kilowatt of refrigeration is given as:

(3)

The coefficient of performance, COP, is obtained by dividing the refrigeration effect by the compressor work:

(4)

3. Thermodynamic Properties

In order to calculate the performance parameters of the refrigeration cycles considered in the present work using computer simulation, the thermodynamics properties of the used refrigerant should be presented in simple equation forms. As mentioned previously, The DuPont have been developed and presented tables of the thermodynamic properties of R-404A. All these data were manipulated and converted to simple equations. These equations are presented as follows:

1) Saturated vapor (T_g) temperature:

T_g = A₁₁ (P)³ + A₁₂ (P)² + A₁₃ (P) + A₁₄

2) Saturated vapor (P_g) and saturated liquid (P_f) pressure:

P_g = B₁₁ (T)³ + B₁₂ (T)² + B₁₃ (T) + B₁₄

P_f = B₂₁ (T)³ + B₂₂ (T)² + B₂₃ (T) + B₂₄

3) Saturated vapor (h_g), saturated liquid (h_f) and superheated (h_s) enthalpy:

h_g = C₁₁ (P)³ + C₁₂ (P)² + C₁₃ (P) + C₁₄

h_f = C₂₁ (P)³ + C₂₂ (P)² + C₂₃ (P) + C₂₄

h_s = C₃₁ + C₃₂ (T)

C₃₁ = C₃₃ + C₃₄ (P)

C₃₂ = C₃₅ + C₃₆ (P)

4) Saturated vapor (V_g) and superheated (V_s) specific volume:

V_g = D₁₁ (P)³ + D₁₂ (P)² + D₁₃ (P) + D₁₄

V_s = D₂₁ + D₂₂ (T)

D₂₁ = D₂₃ + D₂₄ (P)

D₂₂ = D₂₅ + D₂₆ (P)

5) Saturated vapor (S_g), saturated liquid (S_f) and superheated (S_s) entropy:

S_g = E₁₁ (P)³ + E₁₂ (P)² + E₁₃ (P) + E₁₄

S_f = E₂₁ (P)³ + E₂₂ (P)² + E₂₃ (P) + E₂₄

S_s = E₃₁ + E₃₂ (T)

E₃₁ = E₃₃ + E₃₄ (P)

E₃₂ = E₃₅ + E₃₆ (P)

The values of the above coefficients were presented in Table 1 as follows:

The temperature and pressure ranges that apply to the above equations are:

・ For temperatures from −50˚C to 60˚C.

・ For pressures from 80 to 2900 kPa.

4. Computer Algorithm

A computer simulation program was developed to calculate the thermodynamic properties and the performance parameters for the standard and the ideal cycles for the refrigerants R-404A. Matlab software was used as programming language.

5. Computer Program Codes

A different computer simulation program codes were developed to present a set of curves in each graph for the

performance parameters (mass flow rate in (kg/s) per kilowatt of refrigeration, heat rejection rate in (kW) per kilowatt of refrigeration, compressor power in kW per kilowatt of refrigeration, coefficient of performance, compressor discharge temperature in ˚C) with different conditions and for both standard and ideal cycles. Moreover, a comparison computer programs were developed to compare the results of each performance parameter at different conditions between standard and ideal cycles.

6. Results and Discussion of Results

The comparison between the ideal and the standard cycle for different values of evaporating temperature (Te) and different values of condensing temperature (Tc) are carried out as follows:

1) Figure 4 compares the variation of with Te and Tc, respectively, for the standard and the ideal cycles. This figure shows that the mass flow rate of the standard cycle is higher than that of the ideal cycle for all values of Te and Tc. This is due to the fact that specific enthalpy difference at the inlet and the outlet of the evaporator for Te and Tc variation results for the standard cycle is lower than that for the ideal cycle.

2) The compressor power, , consumed for the standard and the ideal cycles as Te and Tc increase shown in Figure 5. The for the standard cycle is higher than that for the ideal cycle. This difference in increases as Te or Tc increases, because the difference in for both cycles increases as Te or Tc increases.

3) Figure 6 shows the comparison of the heat rejection rate, , for the standard cycle with that for the ideal cycle with variation of Te and Tc, respectively. From this figure it can be noticed that the heat rejection rate for the standard cycle is slightly higher than that of the ideal cycle for all values of Te and Tc. This difference in increases as Te or Tc increases, because the difference in for both cycles increases as Te or Tc increases.

4) The discharge temperature in Figure 7 shows the comparison of the standard cycle with that of the ideal cycle for the variation of Te and Tc, respectively. The compressor discharge temperature of the ideal cycle is higher than that of the standard cycle for all values of Te and Tc due to the compressor inlet temperature rise because of superheating state, which increases the compressor exit temperature.

5) Figure 8 compares the coefficient of performance, COP, with Te and Tc, respectively, for the standard and the ideal cycles. The COP of the ideal cycle is higher than that of the standard cycle as seen from this figure. This is due to superheating and sub-cooling effect in the ideal cycle which cause the refrigeration effect Q_ref, to increase.

7. Conclusions

・ The compressor power variation over the evaporating temperature range from −10˚C to 15˚C at Tc = 40˚C is decreased by 38.8% for the standard cycle and by 43.8% for the ideal cycle. The compressor power variation over the condensing temperature range from 30˚C to 50˚C at Te = 10˚C is increased by 122% for the standard cycle and by 54.5% for the ideal cycle.

・ The coefficient of performance of the ideal cycle with 5˚C superheating and sub-cooling is approximately 25% higher than that of the standard cycle at Te = 10˚C and Tc = 40˚C for the refrigerant R-404A.

・ Based on the above conclusions, the simulation model can be used in testing refrigeration systems using the refrigerant under study with different conditions, which means that the cost of using laboratory equipment for experimental tests and effort can be reduced.

・ The previous results and the tested properties show that the refrigerant R-404A is a suitable alternative refrigerant to replace several chlorofluorocarbons and hydrochlorofluorocarbons due to their unfriendly influences on the environment.

Acknowledgements

This work has been carried out during sabbatical leave granted to the author Abed Alrzaq Sleman Alshqirate from Al-Balqa’ Applied University (BAU) during the academic year 2014/2015.

Cite this paper

Abed Alrzaq Sleman Alshqirate, (2016) Performance Study of Refrigeration Units That Use the Refrigerant R-404A by Using Computer Simulation. Modern Mechanical Engineering,06,67-75. doi: 10.4236/mme.2016.62008

References

Nomenclature