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Research Papers: Natural and Mixed Convection

Experimental Investigation of Transitional Natural Convection in a Cube Using Particle Image Velocimetry—Part I: Fluid Flow and Thermal Fields

[+] Author and Article Information
Marios D. Georgiou

Department of Mechanical
Science and Engineering,
University of Illinois at Urbana-Champaign,
Urbana, IL 61801
e-mail: georgiou@illinois.edu

Aristides M. Bonanos

Energy, Environment and Water Center,
The Cyprus Institute,
Nicosia, Cyprus
e-mail: a.bonanos@cyi.ac.cy

Department of Mechanical
Science and Engineering,
University of Illinois at Urbana-Champaign,
Urbana, IL 61801
e-mail: georgia@illinois.edu

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received May 28, 2016; final manuscript received June 23, 2016; published online September 20, 2016. Assoc. Editor: Andrey Kuznetsov.

J. Heat Transfer 139(1), 012502 (Sep 20, 2016) (9 pages) Paper No: HT-16-1314; doi: 10.1115/1.4034166 History: Received May 28, 2016; Revised June 23, 2016

Abstract

An experimental investigation of transitional natural convection in an air filled cube was conducted in this research. The characteristic dimension of the enclosure is 0.35 m, and data were collected in the middle plane of the cavity. The Rayleigh number range examined is $5.0×107≤Ra≤3.4×108$. This was achieved by varying the temperature on the hot and cold walls. The velocity field in the middle plane is measured using particle image velocimetry (PIV). Temperature measurements in the core of the enclosure indicate a linear profile. The average Nu number is also presented and compared against other correlations in the literature. This study attempts to close the gap of available experimental data in literature and provide experimental benchmark data that can be used to validate computational fluid dynamics (CFD) codes since the estimated error from PIV measurements is within 1–2%.

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References

Yang, K. , 1988, “ Transitions and Bifurcations in Laminar Buoyant Flows in Confined Enclosures,” ASME J. Heat Transfer, 110(4b), pp. 1191–1204.
Batchelor, G. , 1954, “ Heat Transfer by Free Convection Across a Closed Cavity Between Vertical Boundaries at Different Temperatures,” Q. Appl. Math., 12(3), pp. 209–233.
Elder, J. , 1965, “ Laminar Free Convection in a Vertical Slot,” J. Fluid Mech., 23(8), pp. 77–98.
Elder, J. , 1965, “ Turbulent Free Convection in a Vertical Slot,” J. Fluid Mech., 23(8), pp. 99–111.
Gill, A. , 1966, “ The Boundary-Layer Regime for Convection in a Rectangular Cavity,” J. Fluid Mech., 26(10), pp. 515–536.
Ostrach, S. , 1972, “ Natural Convection in Enclosures,” Advances in Heat Transfer, J. Hartnett and T. Irvine , eds., Vol. 8, Elsevier, New York, pp. 161–227.
Davis, G. D. V. , 1983, “ Natural Convection of Air in a Square Cavity: A Bench Mark Numerical Solution,” Int. J. Numer. Methods Fluids, 3(3), pp. 249–264.
Markatos, N. , and Pericleous, K. , 1984, “ Laminar and Turbulent Natural Convection in an Enclosed Cavity,” Int. J. Heat Mass Transfer, 27(5), pp. 755–772.
Fusegi, T. , Hyun, J. , Kuwahara, K. , and Farouk, B. , 1991, “ A Numerical Study of Three-Dimensional Natural Convection in a Differentially Heated Cubical Enclosure,” Int. J. Heat Mass Transfer, 34(6), pp. 1543–1557.
Tric, E. , Labrosse, G. , and Betrouni, M. , 2000, “ A First Incursion Into the 3d Structure of Natural Convection of Air in a Differentially Heated Cubic Cavity, From Accurate Numerical Solutions,” Int. J. Heat Mass Transfer, 43(21), pp. 4043–4056.
Tian, Y. , and Karayiannis, T. , 2000, “ Low Turbulence Natural Convection in an Air Filled Square Cavity. Part I: The Thermal and Fluid Flow Fields,” Int. J. Heat Mass Transfer, 43(6), pp. 849–866.
Tian, Y. , and Karayiannis, T. , 2000, “ Low Turbulence Natural Convection in an Air Filled Square Cavity: Part II: The Turbulence Quantities,” Int. J. Heat Mass Transfer, 43(6), pp. 867–884.
Corvaro, F. , and Paroncini, M. , 2008, “ A Numerical and Experimental Analysis on the Natural Convective Heat Transfer of a Small Heating Strip Located on the Floor of a Square Cavity,” Appl. Therm. Eng., 28(1), pp. 25–35.
Corvaro, F. , and Paroncini, M. , 2009, “ An Experimental Study of Natural Convection in a Differentially Heated Cavity Through a 2d-PIV System,” Int. J. Heat Mass Transfer, 52(1–2), pp. 355–365.
Corvaro, F. , Paroncini, M. , and Sotte, M. , 2012, “ PIV and Numerical Analysis of Natural Convection in Tilted Enclosures Filled With Air and With Opposite Active Walls,” Int. J. Heat Mass Transfer, 55(23–24), pp. 6349–6362.
Butler, C. , Newport, D. , and Geron, M. , 2013, “ Natural Convection Experiments on a Heated Horizontal Cylinder in a Differentially Heated Square Cavity,” Exp. Therm. Fluid Sci., 44, pp. 199–208.
TSI, 2012, “ Insight 4G: Data Acquisition, Analysis, and Display Software Platform User Guide,” TSI, Inc., Shoreview, MN.
Kahler, C. , Sammler, B. , and Kompenhans, J. , 2004, “ Generation and Control of Tracer Particles for Optical Flow Investigations in Air,” Particle Image Velocimetry: Recent Improvements, Springer, Berlin, Germany, pp. 417–426.
Bejan, A. , 2013, Convection Heat Transfer, Wiley, New York, NY.
Catton, I. , 1978, “ Natural Convection in Enclosures,” 6th International Heat Transfer Conference, Vol. 6, pp. 13–31.
Gray, D. D. , and Giorgini, A. , 1976, “ The Validity of the Boussinesq Approximation for Liquids and Gases,” Int. J. Heat Mass Transfer, 19(5), pp. 545–551.
Mills, A. F. , 1999, Basic Heat and Mass Transfer, Pearson, New York.

Figures

Fig. 1

Schematic of the experimental setup: the main components of the experiment are the test cavity and the 2D-PIV system

Fig. 2

Top view of the enclosure: the profile probes were inserted through the top cavity wall. Location 1 and 3 were on the symmetry plane between the hot and the cold wall and location 2 was on the symmetry plane between the nonheated walls.

Fig. 3

Ensemble average velocity 〈U〉 in the horizontal direction: (a) Ra = 5.08 × 107, (b) Ra = 1.50 × 108, and (c) Ra = 3.40 × 108

Fig. 4

Ensemble average velocity 〈V〉 in the horizontal direction: (a) Ra = 5.08 × 107, (b) Ra = 1.50 × 108, and (c) Ra = 3.40 × 108

Fig. 5

Velocity profile lines: (a) Mean velocity curves 〈U〉 in the horizontal direction and (b) Mean velocity curves 〈V〉 in the vertical direction

Fig. 6

Velocity magnitude |〈U〉| in the enclosures: (a) Ra = 5.08 × 107, (b) Ra = 1.50 × 108, and (c) Ra = 3.40 × 108

Fig. 7

Gradient of the third velocity component (w): we observe that values for the derivative fluctuate between −0.0005 and 0.0005: (a) Ra = 5.08 × 107, (b) Ra = 1.50 × 108, and (c) Ra = 3.40 × 108

Fig. 8

Temperature measurements as a function of height in the core at locations 1 and 3. The filled symbols correspond to the profile probe in location 1, whereas the hollow symbols correspond to the probe in location 3.

Fig. 9

Nusslet number as a function of Ra over the range examined in the present work

Fig. 10

Cube: surface 1 is the hot side, surface 2 is the cold side, and surface 3 is the four Plexiglass sides

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