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Research Papers

Double Duct Packed Bed Solar Air Heater Under Combined Single and Recyclic Double Air Pass

[+] Author and Article Information
Satyender Singh

Department of Mechanical Engineering,
National Institute of Technology,
Hamirpur, HP 177005, India
e-mail: satyender.nith@gmail.com

Prashant Dhiman

Department of Mechanical Engineering,
National Institute of Technology,
Hamirpur, HP 177005, India
e-mail: prashant_rec@yahoo.co.in

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 May 21, 2015; final manuscript received November 6, 2015; published online December 22, 2015. Assoc. Editor: Werner Platzer.

J. Sol. Energy Eng 138(1), 011009 (Dec 22, 2015) (7 pages) Paper No: SOL-15-1150; doi: 10.1115/1.4032142 History: Received May 21, 2015; Revised November 06, 2015

The present work intended to investigate thermal and thermohydraulic efficiencies of two different models of recyclic double pass packed bed solar air heaters experimentally. Model-I consists of single air pass through two glass covers as well as double air pass caused due to recycle of the air exiting from the packed bed duct formed between the absorber plate and the glass cover through another duct integrated between the absorber and back plates to inlet of the packed bed duct. On the other hand, model-II consists of only double air pass originated due to recycle operation constituted between the similar solar air heater elements as that of model-I. Twelve numbers of wire mesh screens to form 95% bed porosity were used. Both solar air heater models were tested under the range of packed bed Reynolds number from 300 to 1500 for air mass flow rate and recycle ratio of 0.01 kg/s to 0.025 kg/s and 0.3 to 1.8, respectively. Results revealed that thermal performance of model-I is found to be 15% higher than that of model-II. The optimum value of the recycle ratio for model-I and model-II are obtained as 0.9 and 1.2, respectively, at a mass flow rate of 0.025 kg/s that yields the best thermohydraulic efficiency of 77% and 67%, respectively. Moreover, optimum solution for recycle ratio and air mass flow rate during off sun shine hours are also obtained and presented in the current work.

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Figures

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Fig. 1

Experimental setup schematic diagram of (a) model-I: (1) air blower, (2) flexible pipe, (3) orifice meter, (4) air flow in, (5) glass covers, (6) by pass valve, (7) inclined manometer, (8) insulation, (9) back plate, (10) absorber plate, (11) packed bed, (12) outlet air, (13) solar simulator, and (14) air mixing chamber; (b) model-II: (1) air blower, (2) flexible pipe, (3) orifice meter, (4) air flow in, (5) glass covers, (6) by pass valve, (7) inclined manometer, (8) insulation, (9) back plate (10) absorber plate, (11) packed bed, (12) outlet air, (13) solar simulator, and (14) air mixing chamber

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Fig. 2

Photographs of experimental setup (a) model-I and (b) model-II

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Fig. 3

Equipments used in measurements

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Fig. 4

Effect of recycle ratio on the thermal and thermohydraulic efficiencies of both solar air heater models as a function of mass flow rate

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Fig. 5

Effect of recycle ratio on the outlet air temperature of both solar air heater models as a function of mass flow rate (a) packed bed duct and (b) duct between glass covers

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Fig. 6

Effect of recycle ratio on the pressure drop of both solar air heater models as a function of mass flow rate (a) packed bed duct, (b) duct between absorber and back plates, and (c) duct between glass covers

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Fig. 7

Effect of recycle ratio on the thermal and thermohydraulic efficiencies of (a) model-I and outlet air temperature of (b) packed bed duct (c) glazed duct as a function of mass flow rate, at I = 309 W/m2

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