Hybrid compression absorption

Hybrid Compression Absorption Refrigeration System

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1

Mean 15.05StDev 0.7608N 50AD 0.535P-Value 0.163

Probability Plot of C1Normal

Outline

Text

TextText

Text

Text

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

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



Introduction

Text

TextText

Text

Text

• 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

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



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

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



Vapor Absorption System

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



Need of Vapor Compression Absorption Refrigeration System

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



Need of Vapor Compression Absorption Refrigeration System

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



Vapor Compression Absorption Refrigeration System

Sol Pump

Absorber

Desorber

EV

HX

WC

Single Stage Compression Absorption System (By P. K. Satapthy)

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1




Condenser Absorber

Desorber

Evaporator

WC

EV EV

Sol Pump

Sol HX

Double Lift Compression Absorption System (By P. K. Satapthy)

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1




Double Effect Compression Absorption System (By Pongsid Srikhrin et. al.)

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1




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.)

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1




Two Stage Compression Absorption Cycle (By P. K. Satapthy)

AII AI

D I D II

Comp

EV

Sol Pump

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1




Hybrid GAX Cycle Type A & Type B (By Yong Tae Kang et. al.)

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1




Hybrid GAX Cycle Type C & Type D (By Yong Tae Kang et. al.)

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1




Compression Absorption Cascade System (By Jose´

Fernańdez-Seara et. al)

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1




GAXAC System (By. A. Rameshkumar et. al)

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



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.

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



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

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



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.

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



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.

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



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).

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



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

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



Performance of Cascade System

Compression System COP (COPC) and Absorption System COP (COPa) and cascade system COP

(COPg) vs intermediate temperature level (By Jose´ Fernańdez-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.

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



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.

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



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

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



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.

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



References

•Jose´ Fernańdez-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.

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



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.

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



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

C1

Perc

ent

1716151413

99

95

90

80

70

605040

30

20

10

5

1



VCAS

Thanks

Mechanical Dept. Dr. BATU Lonere

Documents

Hybrid compression absorption