Abstract
A mathematical model is developed to simulate the performance of an R-744 (CO2) based air conditioning system operating under transcritical conditions, but near the critical point. The system is designed for summer, and operates in a transcritical mode under the designed summer conditions. However, as the ambient conditions change from summer to winter, the system can undergo a transition from transcritical to near critical and finally subcritical mode. The mathematical model is developed to analyze the effects of gas cooler air flow rate and refrigerant charge on the transition of cycle. The model is validated with experimental results. Further, the influence of refrigerant charge, gas cooler air flow rate on transition of the cycle from transcritical to subcritical mode is analyzed under different ambient conditions. Results show that decrease in total charge, ambient temperature or increase in gas cooler air flow rate, independently or in combination, can lead to a transition from transcritical to subcritical mode. Further, by increasing the refrigerant charge beyond 1100 gm, the system can be made to operate in transcritical mode when the ambient temperature is below 17°C. It is expected that the study is useful in the design of suitable control systems for optimal operation of the system subjected to widely varying ambient conditions.
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Abbreviations
- bw,m :
-
Slope of saturated air curve at mean water film temperature (kJ/kg-K)
- bR :
-
Slope of saturated air curve at wall and refrigerant temperature difference (kJ/kg-K)
- C:
-
Capacity ratio
- Cp :
-
Specific heat (kJ/kg-K)
- COP:
-
Coefficient of performance
- dAair :
-
Air side total area of tube for an element (m2)
- dAfin :
-
Area of the fin for an element (m2)
- dAtube,o :
-
Outside area of tube for an element (m2)
- dAref :
-
Refrigerant side heat transfer area of tube for an element (m2)
- h:
-
Enthalpy (kJ/kg)
- htc:
-
Heat transfer coefficient (kW/m2-K)
- kw :
-
Thermal conductivity of water film (kW/m-K)
- LMTD:
-
Log mean temperature difference (°C)
- LMED:
-
Log mean enthalpy difference (kJ/kg)
- \( \dot{\text{m}}\) :
-
Mass flow rate (kg/s)
- N:
-
Number of transfer unit
- P:
-
Pressure (kPa)
- PDR:
-
Piston displacement rate (m3/s)
- Qgc :
-
Heat rejection rate in gas cooler (kW)
- Qev :
-
Cooling capacity of evaporator (kW)
- t:
-
Temperature (°C)
- tsup :
-
Degree of superheat (K)
- U:
-
Overall heat transfer coefficient (kW/m2-K)
- \(\dot{V}_{gc}\) :
-
Volumetric air flow rate of gas cooler (m3/s)
- Wcomp :
-
Compressor power (kW)
- yw :
-
Water film thickness (m)
- ηoverall :
-
Overall surface efficiency for dry surface
- ηfin ,wet :
-
Efficiency of fin for wet surface
- ε:
-
Effectiveness of heat exchanger for an element
- air,sat,ref:
-
Evaluated for saturated air at refrigerant temperature
- air,sat,wall:
-
Evaluated for saturated air at tube wall temperature
- air,sat,w,m:
-
Evaluated for saturated air at mean water film temperature
- air,wet:
-
Evaluated for air at film temperature
- air,in:
-
Evaluated at air inlet condition
- air,out:
-
Evaluated at air outlet condition
- ev:
-
Evaporator
- gc:
-
Gas cooler
- ref:
-
Refrigerant
- w,m:
-
Evaluated at mean water film temperature
- wall :
-
Evaluated at tube wall
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Sharma, D.K., Pegallapati, A.S. & Ramgopal, M. Studies on an R-744 based air conditioning system operating near critical point. Sādhanā 48, 177 (2023). https://doi.org/10.1007/s12046-023-02230-z
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DOI: https://doi.org/10.1007/s12046-023-02230-z