Heat transfer of impinging jet-array over convex-dimpled surface

Chang, Shyy Woei; Jan, Yih Jena; Chang, Shuen Fei

doi:10.1016/j.ijheatmasstransfer.2006.02.030

Cited by 27 publications

(8 citation statements)

References 40 publications

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“…In 2006, Chang et al [26] investigated the parameter of Rej, L/Dj, and EISH on the heat transfer performance of dimpled target of impinging jets (Rej = 5000-15,000, L/Dj = 0.5-11, El SH = 0-0.5, 6/D = 0.3, DJD = 0.29). In 2007, Chang et al [27] applied the impingement of dimple/protrusion an-ays on the cooling process of electronic devices (Rej = 5000-15,000).…”

Section: Introductionmentioning

confidence: 99%

Flow and Heat Transfer Characteristics of Single Jet Impinging on Dimpled Surface

Xie¹,

Li²,

Lan³

et al. 2013

Journal of Heat Transfer

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Flow and Heat Transfer Characteristics of Single Jet Impinging on Dimpled SurfaceBased on combined particle image velocimetry (PIV) and numerical simulation, the flow and heat transfer characteristics of a single jet impinging on a dimpled surface for D/ D = 0.318. 0.5. 1.045; ô/D = 0.1, 0.2, 0.3; Rej = 5000. 10.000,23,000, were investigated for the first time. The distance between jet nozzle and plate was fi.xed and equal to H/D = 2. The results show that the flow structures of the single jet impingement with dimpled target surface can be summarized into three typical conceptual flow structures. Particularly, the third flow structure in the form of a large toroidal vortex bound up with the dimple is the result of the centrifugal force of the flow deflection at the stagnation region and spherical centrifugal force of the deep dimple surface. The heat transfer area increases when the dimple relative depth increases. For the cases of D/D = 0.318 and 0.5. the area increasing dominate the heat transfer process, and the average Nusselt number increases with the increasing of dimple relative depth. For the cases with Dy/D = 1.045, the local Nusselt number reduction dominate the heat transfer process, the average Nusselt number decreases with the increasing of dimple relative depth. The average Nusselt number of the Dj/D = 0.318 and 0.5 cases is larger than the baseline case, while those of the DjiD = 1.045 cases are smaller than the baseline case. Furthermore, the correlative expressions of the local Nusselt number, stagnation points Nusselt number and average Nusselt number are obtained.

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Section: Introductionmentioning

confidence: 99%

Flow and Heat Transfer Characteristics of Single Jet Impinging on Dimpled Surface

Xie¹,

Li²,

Lan³

et al. 2013

Journal of Heat Transfer

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“…The maximum discrepancies of +10% between the experimental f measurements and the correlation results using Eqs. (11)- (14) are achieved for 96% of data. The f augmentations from the laminar and turbulent f 1 references for the present hexagonal test ducts are indexed by f/f 1 which are plotted against Re in Fig.…”

Section: Resultsmentioning

confidence: 95%

“…The test facilities, instrumentations, experimental procedures and data processing methods have been previously reported [14][15][16], which will be briefly described. The test sections and experimental program are illustrated in details.…”

Section: Experimental Facility and Test Sectionmentioning

confidence: 99%

Heat transfer and pressure drop in hexagonal ducts with surface dimples

Chang

Chiang

Chou

2010

Experimental Thermal and Fluid Science

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“…In addition, higher heat transfer coefficients were observed for deeper dimple, narrower channel or densely distributed dimple cases with the same dimple diameter. Chang et al [18] investigated the heat transfer of impinging jet-array over a convex-dimpled surface. Heat transfer variations caused by adjusting the jet Reynolds number (Re) and separation distance (S/D j ) over the ranges of 5000…”

Section: Introductionmentioning

confidence: 99%