Hybrid Compression Absorption Refrigeration System
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Outline
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1. Introduction
2. Vapor Absorption System
3. Need of Vapor Compression Absorption System
4. Vapor Compression Absorption Systems
5. Performance of Hybrid GAX
6. Performance of Cascade System
7. Summary
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Introduction
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• Montreal Protocol – Developed and Developing Countries signed it on 16th Sept 1987
• Total Phase Out of CFC group by 2010
• Total Phase Out of HCFC group by 2020
• High Demand of Electricity Charges
• Availability of waste heat from different industrial processes
• High requirements for Cooling
Has Renewed a Interest in Vapor Absorption System
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Introduction
• Ferdinand Carre in 1860 developed Aqua Ammonia Absorption Refrigeation
• Windhausen in 1878 used a principle of John Leslie for Absorption System
• Platen and Carl Munters in 1922 invented three fluid system that uses Hydrogen as no condensable gas heating based bubble pump was used
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Vapor Absorption System
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Need of Vapor Compression Absorption Refrigeration System
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Need of Vapor Compression Absorption Refrigeration System
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Vapor Compression Absorption Refrigeration System
Sol Pump
Absorber
Desorber
EV
HX
WC
Single Stage Compression Absorption System (By P. K. Satapthy)
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Vapor Compression Absorption Refrigeration System
Condenser Absorber
Desorber
Evaporator
WC
EV EV
Sol Pump
Sol HX
Double Lift Compression Absorption System (By P. K. Satapthy)
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Vapor Compression Absorption Refrigeration System
Double Effect Compression Absorption System (By Pongsid Srikhrin et. al.)
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Vapor Compression Absorption Refrigeration System
Combined cycle employing two combinations of working fluids i.e. NH3/H2O and H2O/KHO. The rectifier is absent and also the highest
pressure is decreased (By Pongsid Srikhrin et. al.)
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Vapor Compression Absorption Refrigeration System
Two Stage Compression Absorption Cycle (By P. K. Satapthy)
AII AI
D I D II
Comp
EV
Sol Pump
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Vapor Compression Absorption Refrigeration System
Hybrid GAX Cycle Type A & Type B (By Yong Tae Kang et. al.)
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Vapor Compression Absorption Refrigeration System
Hybrid GAX Cycle Type C & Type D (By Yong Tae Kang et. al.)
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Vapor Compression Absorption Refrigeration System
Compression Absorption Cascade System (By Jose´
Ferna´ndez-Seara et. al)
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Vapor Compression Absorption Refrigeration System
GAXAC System (By. A. Rameshkumar et. al)
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Performance of HGAX
COPC vs Absorber Pressure in Type A (By Yong Tae Kang et. al.)
It is found that the COPc in the HGAX Type A increases as high as 1.24 by controlling the absorber pressure, which is about 24% higher than the COPc in the standard GAX cycle with the same thermal conditions.
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Performance of HGAX
Te and COPC vs Evaporator Pressure in Type B (By Yong Tae Kang et. al.)
The COPc decreases due to the increasing compressor work and the decreasing latent heat of the refrigerant at a low evaporator pressure
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Performance of HGAX
COPc vs desorber pressure in type C (By Yong Tae Kang et. al.)
COPc in the HGAX Type C increases as high as 1.19 by controlling the desorber pressure, which is about 19% higher than the COPC in the standard GAX cycle with the same thermal conditions.
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Performance of HGAX
COPC vs Condenser Pressure in Type C (By Yong Tae Kang et. al.)
The COPC decreases with increasing the condenser pressure. This is because the Qd and Qe are almost kept constant while the compression work increases significantly as the condenser pressure increases.
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Performance of HGAX
COPh and Tout vs in Condenser Pressure type D (By Yong Tae Kang et. al.)
COPh decreases as low as 0.95 due to the increasing compression work. As the condenser pressure increases, the COPh,t decreases significantly from 1.65 to 1.25 while the COPh does not (1.05–0.95).
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Performance of HGAX
COPh and Tout vs in Condenser Pressure type D (By Yong Tae Kang et. al.)
As UA of the condenser increases, the heat capacity of the condenser Qc also increases leading to a high outlet temperature of the hot water. The maximum hot water temperature of 1060C is obtained from the HGAX-Type D
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Performance of Cascade System
Compression System COP (COPC) and Absorption System COP (COPa) and cascade system COP
(COPg) vs intermediate temperature level (By Jose´ Ferna´ndez-Seara et. al)
The intermediate temperature increase causes simultaneously a compression COP decrease and an absorption COP increase. The compression COP decrease is less significant as the evaporation temperature decreases.
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Performance of Cascade System
Compression System COP (COPC) and Absorption System COP (COPa) and cascade system COP
(COPg) vs intermediate temperature level
optimal intermediate temperature increases when the evaporation temperature increases with both refrigerants. However, the effect of the evaporation temperature on the optimal intermediate temperature is more significant with NH3 than with CO2.
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Conclusion
• COPc in the HGAX-Type A increases which is about 24% higher than the COPc in the standard GAX cycle
• HGAX-Type B, the evaporation temperature and the COPc decrease with decreasing the evaporator pressure
• The highest desorption temperature decreases as low as 1680C, and therefore the corrosion problem can be completely removed by adopting the HGAX-Type C COPc in the HGAX-Type C increases as high as 1.19 by controlling the desorber pressure, which is about 19% higher than the COPc in the standard GAX cycle with the same thermal conditions
• In HGAX-Type D, the maximum hot water temperature can be achieved
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References
•Z. Crepinsek, D. Goicanec, J. Krope, “Comparison of the performances of absorptionrefrigeration cycles”, WSEAS Transactions on Heat and Mass Transfer, 01 (2009), 65 – 76, Issue 3, ISSN: 1790-5079,•A. Rameshkumar, M. Udayakumar, R. Saravanan, Heat transfer studies on a GAXAC (generator-absorber-exchangeabsorption compression) cooler”, International Journal of Applied Energy, 86 (2009), 2056 – 2064.•Soteris Kalogirou “Recent Patents in Absorption Refrigeration System” Recent Patents in Mechanical Engineering”, 01 (2008), 58 – 64. •A. Ramesh kumar, M. Udayakumar, “Studies of Compressor Pressure Ratio Effect on GAXAC (generator–absorber–exchange absorption compression) cooler”, International Journal of Applied Energy, 85 (2008), 1163 – 1172. •Mark Brandon Shiflett et. al., “Hybrid Vapor Compression-Absorption Cycle”, US Patent 2007/0019708 A1, January, 27, 2007. World Intellectual Property, International Publication Number WO 2006/124776•L. Kairouani & E.Nehdi, “Cooling Performance and Energy Saving of a Compression- Absorption Refrigeration System Assisted by Geothermal Energy”, International Journal of Applied Thermal Engineering, 26 (2006) pp 288 – 294.
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References
•Jose´ Ferna´ndez-Seara *, Jaime Sieres, Manuel Va´zquez, “Compression Absorption Cascade Refrigeration System” International Journal of Applied Thermal Engineering, 26 (2006) pp 502 – 512•Mark Brandon Shiflett et. al., “Hybrid Vapor Compression-Absorption Cycle”, US Patent 2007/0019708 A1, January, 27, 2007. World Intellectual Property, International
Publication Number WO 2006/124776•L. Kairouani, E. Nehdi and R. Ben Iffa, “Thermodynamic Investigation of Two-Stage Absorption Refrigeration System Connected by a Compressor”, American Journal of
AppliedScience, 2(6), 1036 – 1041, 2005, ISSN 1546 – 9239.•Yong Tae Kang, Hiki Hong, Kyoung Suk Park, “Performance analysis of advanced hybrid
GAX cycles: HGAX”, International Journal of refrigeration, 27(2004), pp 442 – 448.• R. S. Agarwal “Montreal and Kyto Protocol and their impact on the refrigeration sector”
Proceedings of the workshop on an Alternative Refrigerants and Cycles” IIT Delhi, October 2002, 25-27,.
• Regulation (EC) No. 842/2006 of the European Parliament and of the Council.
<http://www.fluorocarbons.org/documents/library/Legislation/JO_L161_1_842_2006_Regulation.pdf>, May 1986.
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References
•Pongsid Srikhirin, Satha Aphornratana, Supachart Chungpaibulpatana, “A review of absorption refrigeration technologies” Renewable and Sustainable Energy Reviews 5 (2001) 343–372, 1364-0321/01/$ - see front matter @ 2001 Elsevier Science Ltd.PII: S13 64 -0321(01)00003-X
• R. Ayala, C. L. Heard and F. A. Holland. “Ammonia/Lithium Nitrate Absorption /Compression Refrigeration Cycle. Part I. Simulation”, Applied Thermal Engineering, 17 (1997), 223-233 No – 03,
• Silas W Clerk, “Compressor Assisted Absorption Refrigeration System”, US Patent 4171619, March 16, 1978
• Sgimoto et. al. “Cooling system having combination of compression and absorption type units”, US Patent 4471630, January, 27, 1983
• William T. Osbrone, “Combined Mechanical Refrigeration and Absorption Refrigeration Method and Apprats”, US Patent 5038574, October 26, 1990.
• Huen Lee, Jin Soo Kim, “Triple Effect Absorption Chillers with Vapor Compression Units” US Patent 6324865 B1, December 04, 2001.
• J. Swinney, W. E. Jones, J. A. Wilson, “A Novel Hybrid Compression Absorption Refrigeration cycle”, International Journal of refrigeration, 24(2001), pp 208 – 219.
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References
•Mitsuhiro Fukutaa,*, Tadashi Yanagisawaa, Hiroaki Iwatab, Kazutaka Tada, “Performance of compression/absorption hybrid refrigeration cycle with propane/mineral
oil combination” , International Journal of refrigeration, 25(2002), pp 907 – 915
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VCAS
Thanks
Mechanical Dept. Dr. BATU Lonere