Experimental Investigation of R404A Indirect Refrigeration System Applied Internal Heat Exchanger: Part 2—Exergy Characteristics
Abstract
:1. Introduction
2. Test Apparatus and Data Analysis
2.1. Test Apparatus
2.2. Data Reduction
2.3. Uncertainties
3. Results
3.1. Effect of the DSP
3.1.1. Effect of the DSP of the R404A Cycle
3.1.2. Effect of the DSP of the R744 Cycle
3.2. Effect of the DSB
Effect of the DSB of the R404A Cycle
3.3. Effect of CT
3.4. Effect of the CET
3.5. Effect of IHX Efficiency
3.6. Comparison of Experimental and Performance Analysis Data
4. Conclusions
- In order to lower the system EDR, the DSP, DSB, IHX efficiency and CET of the R404A cycle must be increased to the maximum, and the DSP of the R744 cycle and CT must be reduced to the minimum.
- Under the given conditions, the smallest change in the system EDR according to the change in each parameter is the DSP of the R744 cycle (0.3–1%), followed by the DSB of the R404A cycle (6.1–8.8%), IHX efficiency of the R404A cycle (3.8–14.3%), DSP of the R404A cycle (11.7–15.9%), CET (29.4–41.9%), and CT (35–47%).
- Also, in terms of the EES, the largest value obtained was the DSP of the R404A cycle (2.4–12.7%), followed by the IHX efficiency of the R404A cycle (3–10.2%), CET (2.2–8.7%), CT (4–6.9%), DSB of the R404A cycle (2.7–6.2%), and DSP of the R744 cycle (0.04–1.2%).
- The DSP of the R744 cycle does not need to be considered when designing the R404A IRS using R744 as a secondary fluid because the changes in the EDR of the IRS and EES are insignificant, with ranges of 0.3–1% and 0.04–1.2%, respectively.
- Among the EDRs of the components of the IRS, the largest one is the compressor, followed by the expansion valve, condenser, evaporator, CHX, pump, and IHX. Therefore, from energy and environmental aspects, great efforts must be made to reduce the EDR in the compressor and expansion valve when designing the R404A IRS using R744 as a secondary fluid.
- The trend of the system EDR shows the exact opposite of that of the system exergy efficiency and COP. The EES and COP of the system increase with a decrease in the system EDR.
- The EES can replace the COP of the system.
- The position and size of energy inefficiency, which cannot be identified via COP analysis, can be identified by evaluating the EDR of each component, thereby making it possible to maximize energy efficiency.
- Energy efficiency can be maximized via detailed, quantitative, and advanced exergy analysis. This may be considered in future work.
- The R404A refrigerant is regulated in developed countries, including Europe. Therefore, novel alternatives such as R448A and R449A must be examined.
Author Contributions
Funding
Institutional Review Board Statement
Informed Consent Statement
Data Availability Statement
Conflicts of Interest
Nomenclature
ABBREVIATIONS | ||
CC | Cascade condenser | |
CE | Cascade evaporator | |
CET | Cascade evaporation temperature | |
CHX | Cascade heat exchanger | |
COP | Coefficient of performance | |
CRS | Cascade refrigeration system | |
CT | Condensation temperature | |
DSB | Degree of subcooling | |
DSP | Degree of superheating | |
DX | Direct expansion | |
EDR | Exergy destruction rate | |
EES | Exergy efficiency of the system | |
EHC | Evaporation heat capacity | |
ET | Evaporation temperature | |
EV | Expansion valve | |
IE | Inlet entropy | |
IHX | Internal heat exchanger | |
IRS | Indirect refrigeration system | |
IX | Indirect expansion | |
MFR | Mass flow rate | |
OE | Outlet entropy | |
PCC | Power consumption of the compressor | |
PCP | Power consumption of the pump | |
SYMBOLS | ||
Exergy rate | kW | |
Q | Heat capacity | kW |
T | Temperature | °C |
W | Power consumption | kW |
S | Entropy | kJ/(kg·K) |
GREEK SYMBOLS | ||
Difference | ||
Efficiency | ||
SUPERSCRIPTS | ||
M | Mechanical | |
T | Thermal | |
SUBSCRIPTS | ||
C | Condensation or condenser | |
CAS | Cascade heat exchanger | |
COM | Compression | |
D | Destruction | |
E | Evaporation or evaporator | |
Exergy | ||
Exergy rate | kW | |
EXP | Expansion valve | |
F | Fuel | |
IHX | Internal heat exchanger | |
P | Product | |
PUM | Pump | |
R404A | R404A cycle | |
R744 | R744 cycle | |
SUB | Degree of subcooling | |
SUP | Degree of superheating | |
SYS | Total indirect refrigeration system |
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Country | Year(s) | Annual Refrigerant Loss | References |
---|---|---|---|
The Netherlands | 1999 | 3.2% | Hoogen et al., 2002 [10] |
Germany | 2000–2000 | 5–10% | Birndt et al., 2000 [7]; Haaf and Heinbokel, 2002 [9] |
Denmark | 2003 | 10% | Pedersen, 2003 [11] |
Norway | 2002–2003 | 14% | Bivens and Gage, 2004 [8] |
Sweden | 1993 1998 2001 | 14% 12.5% 10.4% | Bivens and Gage, 2004 [8] |
United Kingdom | 1998 | 14.4% | Radford, 1998 [12] |
USA | 2000–2002 | 13% and 18%, 19% and 22% | Bivens and Gage, 2004 [8] |
USA | 2020 | 25% | [14] |
USA | 2019–2021 | 40%, 59%, and 46% | [15] |
Authors | Year | Primary Fluid | Secondary Fluid | Analysis Method |
---|---|---|---|---|
Sawalha and Palm [24] | 2003 | R404A | R744 | Experiment and Simulation |
Pachai [20] | 2004 | R290 + R170 | R744, PG | Experiment |
Pearson [19] | 2005 | - | R744 | Review |
Nilsson et al. [21] | 2006 | R744 | Experiment | |
Jahn [22] | 2008 | - | R744 | Experiment |
Hinde et al. [5] | 2008 | R404A, R507 | R744, PG | Experiment |
Kaga et al. [23] | 2008 | R600a | R744 | Experiment |
Cycle | Component | Range | Unit |
---|---|---|---|
R404A cycle | CT | 20, 30, 40 *, 50 | °C |
IHX efficiency | 0 *, 1, 2, 3, 4 | stage | |
DSB | 0 *, 5, 10, 15, 20 | °C | |
DSP | 10, 20 *, 30, 40 | °C | |
CET | −40, −30, −25 *, −20, −10, 0 | °C | |
Temperature difference of the cascade heat exchanger | 5 * | °C | |
R744 cycle | |||
ET and cascade CT | −35, −25, −20 *, −15, −5, 5 | °C | |
DSB | 1 * | °C | |
DSP | 10 *, 20, 30, 40 | °C |
Component | Characteristics |
---|---|
R404A compressor | Bock; model: HGX34P/380-4S. Displacement with 1450 min−1:33.1 m3 h−1. Number of cylinders: 4. Weight: 96 kg. Max. power consumption: 11.1 kW |
R744 magnetic drive gear pump | Micropump; model: Series 5000. Flow range: 0–13.5 L/min. Maximum system pressure: 103 bar (1500 psi). Temperature range: −46 to 121 °C |
Evaporator | Custom-built; type: horizontal double tube. Material: copper tube. Internal diameter of the inner tube: 11.46 mm. Internal diameter of the outer tube: 33.27 mm. Length of the evaporator: 8000 mm |
Condenser | Alfa Laval; model: ACH-70X-50H-F. Heat exchanged: 38.44 kW. Heat transfer area: 2.45 m2 |
Cascade heat exchanger | Alfa Laval; model: ACH-70X-50H-F. Heat exchanged: 10.86 kW. Heat transfer area: 2.45 m2 |
Cycle | Component | , kW | , kW | , kW |
---|---|---|---|---|
R404A cycle | Compressor (1→2) | (- | ||
Condenser (2→4) | () | |||
IHX (4→5, 8→1) | () | |||
EV (5→6) | ()() | |||
Cascade heat exchanger (6→8, 12→14) | () () | |||
R744 cycle | ||||
Pump (14→15) | () | |||
Evaporator (15→12) | () |
Parameter | Unit | Uncertainty |
---|---|---|
MFR | [kg/min] | 0.0100 |
PCC | [kW] | 0.0350 |
PCP | [W] | 0.2350 |
COP of the total IRS | [/] | 0.0135 |
EDR of the system | [kW] | 0.0175 |
Temperature | [°C] | 0.2000 |
[°C] | 0.4000 | |
Pressure | [kPa] | 5.2700 |
(Pressure drop) | [kPa] | 0.0100 |
MFR of coolant | [kg/h] | 7.5300 |
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Jeon, M.-J.; Lee, J.-H. Experimental Investigation of R404A Indirect Refrigeration System Applied Internal Heat Exchanger: Part 2—Exergy Characteristics. Energies 2024, 17, 4143. https://doi.org/10.3390/en17164143
Jeon M-J, Lee J-H. Experimental Investigation of R404A Indirect Refrigeration System Applied Internal Heat Exchanger: Part 2—Exergy Characteristics. Energies. 2024; 17(16):4143. https://doi.org/10.3390/en17164143
Chicago/Turabian StyleJeon, Min-Ju, and Joon-Hyuk Lee. 2024. "Experimental Investigation of R404A Indirect Refrigeration System Applied Internal Heat Exchanger: Part 2—Exergy Characteristics" Energies 17, no. 16: 4143. https://doi.org/10.3390/en17164143