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Research Papers: Flows in Complex Systems

Analysis of Turbulence Characteristics in Two Large Concentric Annular Ducts Through Particle Image Velocimetry

[+] Author and Article Information
Marlon M. Hernández-Cely

Industrial Multiphase Flow Laboratory (LEMI),
Mechanical Engineering Department,
São Carlos School of Engineering,
University of São Paulo (USP),
Trabalhador São Carlense 400,
São Carlos 13566-570, SP, Brazil
e-mail: marlonhc@usp.br

Victor E. C. Baptistella

Industrial Multiphase Flow Laboratory (LEMI),
Mechanical Engineering Department,
São Carlos School of Engineering,
University of São Paulo (USP),
Trabalhador São Carlense 400,
São Carlos 13566-570, SP, Brazil
e-mail: victor.baptistella@usp.br

Oscar M. H. Rodriguez

Industrial Multiphase Flow Laboratory (LEMI),
Mechanical Engineering Department,
São Carlos School of Engineering,
University of São Paulo (USP),
Trabalhador São Carlense 400,
São Carlos 13566-570, SP, Brazil
e-mail: oscarmhr@sc.usp.br

Contributed by the Fluids Engineering Division of ASME for publication in the JOURNAL OF FLUIDS ENGINEERING. Manuscript received May 17, 2018; final manuscript received October 16, 2018; published online December 10, 2018. Assoc. Editor: Pierre E. Sullivan.

J. Fluids Eng 141(6), 061102 (Dec 10, 2018) (18 pages) Paper No: FE-18-1352; doi: 10.1115/1.4041760 History: Received May 17, 2018; Revised October 16, 2018

An experimental study is presented on water single-phase flow in two 10.5 m-long annular ducts, with external pipe's internal diameter (De) of 155 mm and two concentric internal pipes of external diameters (Di) of 60 mm and 125 mm, i.e., radius ratio (α = Ri/e) of 0.39 and 0.80, respectively, with the aim of improving the understanding of flows in annular ducts. Particle image velocimetry (PIV) was applied to obtain instantaneous and averaged velocity measurements of the flow field. A charge-coupled device camera (2448 pixel × 2050 pixel, 5 Mpixel, 12-bit ) recorded pairs of images of the seeding particles and a double-pulsed PIV laser (Nd:YAG, frequency doubled to 532 nm), with a measured pulse intensity of 70 to 75 mJ/pulse, provided the illumination. Laminar flows were analyzed for validation purposes, experimental data on turbulent flows were compared with the classical law of the wall of the turbulent boundary-layer model, and the shear stresses derived from PIV data were compared with those calculated from the measured pressure drop. The effects of the Reynolds number and geometry on turbulent velocity profiles and Reynolds stresses are presented. The results suggest that the law of the wall for annular-duct flow is a function of radius ratio. The new experimental results are of great value for the development of computational fluid dynamics models and more refined pressure-drop prediction tools in annular-duct flow.

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Figures

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Fig. 3

(a) Particle image velocimetry setup and (b) time diagram, record of images synchronized with the pulse of the laser

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Fig. 2

Experimental apparatus, with concentric geometry of (a) radius ratio α = 0.39 in brown and (b) radius ratio α = 0.80 in blue

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Fig. 1

Schematic view of the visualization box in the annular duct test section with concentric geometry of (a) radius ratio α = 0.39 and (b) radius ratio α = 0.80

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Fig. 4

Particle image velocimetry and analytical axial velocity profiles, u/umax and ua/ua,max, respectively, normalized by maximum velocities in laminar annular-duct flow for a radius ratio α = 0.80, for a Reynolds number of 500

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Fig. 5

Laminar flow velocity profiles, u/umax, normalized by maximum velocities in laminar annular-duct flow comparison between the two geometries with radius ratio α = 0.39 and radius ratio α = 0.80, for a Reynolds number of 740 and 800, respectively

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Fig. 6

Comparison of PIV turbulent velocity profiles in annular duct, between the two geometries: (a) radius ratio α = 0.39 and Reynolds numbers from 8600 to 20,500 and (b) radius ratio α = 0.80 and Reynolds numbers from 8700 to 15,200

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Fig. 7

Dimensionless turbulent flow velocity profiles, u/umax, normalized by maximum velocities, comparison between the two geometries: radius ratio α = 0.39 circles for Reynolds numbers of 8600–20,500 and radius ratio α = 0.80 crosses for Reynolds numbers of 8700–15,200

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Fig. 10

(a) Axial and (b) radial velocity fluctuations, for radius ratio α = 0.80 and Reynolds numbers from 8700 to 15,200

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Fig. 8

Comparison of Reynolds stress tensors for the two geometries: (a) radius ratio α = 0.39 for Reynolds numbers of 8600–20,500 and (b) radius ratio α = 0.80 for Reynolds numbers of 8700–15,200

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Fig. 9

(a) Axial and (b) radial velocity fluctuations, for radius ratio α = 0.39 and Reynolds numbers from 8600 to 20,500

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Fig. 11

Modeling of shear stress in the annular duct with De = 155 mm and Di = 125 mm, radius ratio (α = 0.80) and bottom side of the annular duct

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Fig. 12

Comparison between analytical and experimental Reynolds shear stresses in annular channel for three Reynolds numbers of 8700, 11,900, and 15,200, radius ratio α = 0.80, using the measured pressure drop

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Fig. 13

Particle image velocimetry and logarithmic velocity profiles near the inner pipe wall (top) and outer pipe wall (bottom) of the annular channel in wall coordinates for radius ratio α = 0.39 for three different Reynolds numbers, 8600, 14,500, and 20,500

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Fig. 14

Particle image velocimetry and logarithmic velocity profiles near the inner pipe wall (top) and outer pipe wall (bottom) of the annular channel in wall coordinates for radius ratio α = 0.80 for three different Reynolds numbers, 8700, 11,900, and 1500

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Fig. 15

Noise in PIV measurements for (a) Re = 740, α = 0.39 and (b) Re = 800, α = 0.80

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Fig. 16

Gaussian distribution of the mean velocity with sample standard deviations, for each turbulent flow analyzed and α = 0.39

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Fig. 17

Gaussian distribution of the mean velocity with sample standard deviations, for each turbulent flow analyzed and α = 0.80

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