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Research Papers

A Field Study of a Low-Flow Internally Cooled/Heated Liquid Desiccant Air Conditioning System: Quasi-Steady and Transient Performance

[+] Author and Article Information
Ahmed H. Abdel-Salam

Mem. ASME
Department of Mechanical Engineering,
University of Saskatchewan,
57 Campus Drive,
Saskatoon, SK S7N 5A9, Canada
e-mail: ahmed.abdel-salam@usask.ca

Chris McNevin

Department of Mechanical and
Materials Engineering,
Queen's University,
McLaughlin Hall,
Kingston, ON K7L 3N6, Canada
e-mail: 7cnrm@queensu.ca

Lisa Crofoot

Department of Mechanical and
Materials Engineering,
Queen's University,
McLaughlin Hall,
Kingston, ON K7L 3N6, Canada
e-mail: lisa.crofoot@gmail.com

Stephen J. Harrison

Department of Mechanical and
Materials Engineering,
Queen's University,
McLaughlin Hall,
Kingston, ON K7L 3N6, Canada
e-mail: harrison@me.queensu.ca

Carey J. Simonson

Department of Mechanical Engineering,
University of Saskatchewan,
57 Campus Drive,
Saskatoon, SK S7N 5A9, Canada
e-mail: carey.simonson@usask.ca

1Corresponding author.

Contributed by the Solar Energy Division of ASME for publication in the JOURNAL OF SOLAR ENERGY ENGINEERING: INCLUDING WIND ENERGY AND BUILDING ENERGY CONSERVATION. Manuscript received June 29, 2015; final manuscript received March 6, 2016; published online April 5, 2016. Assoc. Editor: Jorge E. Gonzalez.

J. Sol. Energy Eng 138(3), 031009 (Apr 05, 2016) (14 pages) Paper No: SOL-15-1202; doi: 10.1115/1.4033026 History: Received June 29, 2015; Revised March 06, 2016

The field performance of a low-flow internally cooled/heated liquid desiccant air conditioning (LDAC) system is investigated in this paper. The quasi-steady performance (sensible and latent heat transfer rates, coefficient of performance (COP), and uncertainties) of the LDAC system is quantified under different ambient air conditions. A major contribution of this work is a direct comparison of the transient and quasi-steady performance of the LDAC system. This paper is the first to quantify the importance of transients and shows that, for the environmental and operating conditions in this paper, transients can be neglected when estimating the energy consumption of the LDAC system. Another major contribution of this work is the development and verification of a new method that quantifies (with acceptable uncertainties) the quasi-steady performance of a LDAC system from transient field data using average data.

Copyright © 2016 by ASME
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References

Figures

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Fig. 1

Schematic diagram of the experimental setup for the LDAC system

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Fig. 2

Conceptual schematics for the direction of heat and mass transfer in the low-flow (a) internally cooled dehumidifier and (b) internally heated regenerator. The dehumidifier dries the process air stream, while the regenerator dries the liquid desiccant.

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Fig. 3

Photo showing the LDAC system [34]

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Fig. 4

Photos showing (a) the low-flow internally cooled dehumidifier and (b) a cross section view of a single dehumidifier plate showing the internal water passages [24]

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Fig. 5

Photo showing the low-flow internally heated regenerator

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Fig. 6

The influences of ambient air dry bulb temperature (Tamb,db) on the (a) temperature of air leaving the dehumidifier (Tair,deh,out), (b) humidity ratio of air leaving the dehumidifier (Wair,deh,out), (c) concentration of solution entering (Csol,deh,in) and leaving (Csol,deh,out) thedehumidifier, and (d) temperature of solution/water streams entering/leaving the dehumidifier

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Fig. 7

A psychrometric chart summarizes the influences ofambient air dry bulb temperature (Tamb,db) on the air and solution conditions entering/leaving the dehumidifier

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Fig. 8

The influence of ambient air dry bulb temperature (Tamb,db) on the heat transfer rate to heating water (qwat,heat) and from cooling water (qwat,cool)

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Fig. 9

The influence of ambient air dry bulb temperature (Tamb,db) on (a) the sensible (qsen), latent (qlat), and total (qtot) heat transfer rates and (b) the TCOP, ECOP, and COP of the LDAC system

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Fig. 10

The influences of ambient air humidity ratio (Wamb) on the (a) temperature of airleaving the dehumidifier (Tair,deh,out), (b) humidity ratio of air leaving the dehumidifier (Wair,deh,out), and (c) concentration of solution entering (Csol,deh,in) and leaving (Csol,deh,out) the dehumidifier

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Fig. 11

A psychrometric chart which summarizes the influences of ambient air dry humidity ratio (Wamb) on the air and solution conditions entering/leaving the dehumidifier

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Fig. 12

The influence of ambient air humidity ratio (Wamb) on the rate of heat transfer to heating water (qwat,heat) and from cooling water (qwat,cool)

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Fig. 13

The influence of ambient air humidity ratio (Wamb) on (a) the sensible (qsen), latent (qlat), and total (qtot) heat transfer rates and (b) the TCOP, ECOP, and COP of the LDAC system

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Fig. 14

Comparisons between quasi-steady and transient (a) conditions of air leaving the dehumidifier, (b) heat transfer rates, (c) cooling energy by the dehumidifier, and (d) primary energy consumption of the LDAC system during a complete test day on July 23

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Fig. 15

Comparison between performance evaluation using an average value of transients on July 17 and quasi-steady data at test condition T3 from Table 3. (a) Measured ambient air temperature and humidity ratio on July 17, (b) air, solution, and water inlet and outlet conditions from the dehumidifier, and (c) sensible, latent, and total cooling energy by the dehumidifier, and rate of primary energy consumption by the LDAC system.

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Fig. 16

Comparison between performance evaluation using an average value of transients on July 31 and quasi-steady data at test condition W2 from Table 3. (a) Measured ambient airtemperature and humidity ratio on July 31, (b) air, solution, and water inlet and outlet conditions from the dehumidifier, and (c) sensible, latent, and total cooling energy by the dehumidifier, and rate of primary energy consumption by the LDAC system.

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