Experimental study of heat transfer coefficient with rectangular baffle fin of solar air heater

doi:10.1007/s11708-014-0321-y

Front. Energy

2014, Vol. 8

Issue (2) : 160-172 https://doi.org/10.1007/s11708-014-0321-y

RESEARCH ARTICLE

Experimental study of heat transfer coefficient with rectangular baffle fin of solar air heater

Foued CHABANE^1,^*(

),Nesrine HATRAF²,Noureddine MOUMMI¹

1. Mechanical Department and Mechanical Laboratory, University of Biskra, Biskra 07000, Algeria
2. Mechanical Department, University of Biskra, Biskra 07000, Algeria

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Abstract

This paper presents an experimental analysis of a single pass solar air collector with, and without using baffle fin. The heat transfer coefficient between the absorber plate and air can be considerably increased by using artificial roughness on the bottom plate and under the absorber plate of a solar air heater duct. An experimental study has been conducted to investigate the effect of roughness and operating parameters on heat transfer. The investigation has covered the range of Reynolds number Re from 1259 to 2517 depending on types of the configuration of the solar collectors. Based on the experimental data, values of Nusselt number Nu have been determined for different values of configurations and operating parameters. To determine the enhancement in heat transfer and increment in thermal efficiency, the values of Nusselt have been compared with those of smooth duct under similar flow conditions.

Keywords Nusselt number flow rate heat transfer heat transfer coefficient thermal efficiency forced convection

Corresponding Author(s): Foued CHABANE

Issue Date: 19 May 2014

Cite this article:

Foued CHABANE,Nesrine HATRAF,Noureddine MOUMMI. Experimental study of heat transfer coefficient with rectangular baffle fin of solar air heater[J]. Front. Energy, 2014, 8(2): 160-172.

URL:

https://academic.hep.com.cn/fie/EN/10.1007/s11708-014-0321-y
https://academic.hep.com.cn/fie/EN/Y2014/V8/I2/160

Fig.1 Thermal network of flat plate SAH

1–Coverglass; 2–Absorber plate; 3–Bottom; 4–Insulation; 5–Back plate

Fig.2 Schematic view of solar air collector

Fig.3 Composition of a solar box with baffle fin and smooth plate

Fig.4 Position of baffle fin on the bottom plate and under the absorber plate

Fig.5 Thermal efficiency as a function to air flow rate, corresponding to solar collectors with, and without using baffle

Fig.6 Average temperature of an absorber plate as a function to length of a solar collector for each flow rate from 40 m³/h to 80 m³/h, corresponding to smooth plate

(a) Mass flow rate of 40 m³/h; (b) mass flow rate of 60 m³/h; (c) mass flow rate of 80 m³/h

Tab.1 Average temperature of the absorber plate for each solar collector configuration, corresponding to the air flow rate of 40 m³/h, 60 m³/h and 80 m³/h, and the solar collector length from 0 m to 1.95 m with a tilt angle β = 34.8°

Fig.7 Average air temperature as a function to length of a solar collector for each flow rate from 40 to 80 (m³/h), corresponding to smooth plate

(a) Mass flow rate of 40 m³/h; (a) mass flow rate of 60 m³/h; (a) mass flow rate of 80 m³/h

Tab.2 Average air temperature of the absorber plate for each solar collector configuration, corresponding to the air flow rate of 40, 60 and 80 m³/h, and the solar collector length from 0 m to 1.95 m with a tilt angle β = 34.8°

Fig.8 Heat transfer coefficient as a function to length of solar collector, for each type of solar collector

(a) Mass flow rate of 40 m³/h; (a) mass flow rate of 60 m³/h; (a) mass flow rate of 80 m³/h

Tab.3 Heat transfer coefficient for each solar collector configuration, corresponding to the air flow rate of 40 m³/h, 60 m³/h and 80 m³/h, and solar collector length from 0 m to 1.95 m with a tilt angle β = 34.8°

Fig.9 Solar intensity and inlet, outlet and ambient temperatures as a function to air flow rate, corresponding to the solar collector with smooth plate

(a) Mass flow rate of 40 m³/h; (a) mass flow rate of 60 m³/h; (a) mass flow rate of 80 m³/h

Tab.4 Average temperature of the inlet, outlet and ambient for each solar collector configuration, corresponding to the air flow rate of 40 m³/h, 60 m³/h and 80 m³/h, and a solar collector length from 0 m to 1.95 m with a tilt angle of β = 34.8°

Fig.10 Nusselt number (Nu) as a function to length of solar collector, for each type of solar collector

Mass flow rate is 40 m³/h; (a) mass flow rate is 60 m³/h; (a) mass flow rate is 80 m³/h

Tab.5 Nusselt number for each solar collector configuration, corresponding to the air flow rate of 40 m³/h, 60 m³/h and 80 m³/h, a solar collector length from 0 m to 1.95 m with a tilt angle of β = 34.8°

Fig.11 Variation of collector efficiency with temperature parameters (T_in - T_a)/I at different mass flow rates

Tab.6 Results of collector test

Fig.12 Variation of solar radiation at different days

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