Local heat transfer from a hot plate to a water jet

Robidou, Herveline; Auracher, Hein; Gardin, Pascal; Lebouché, M.; Bogdanic, Laura

doi:10.1007/s00231-002-0335-6

Cited by 35 publications

(17 citation statements)

References 8 publications

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“…4 presents the boiling curves of wall heat flux versus temperature at x = 0. The transient boiling curve obtained from the DNS of quenching process matches well with the steady-state boiling curve obtained from the previous DNS study [24] under the constant wall temperature conditions, which is comparable to the experimental data of Robidou et al [3,4]. This is not consistent with the experimental observation reported in the literature [6][7][8][9][10][11] that the transient boiling curve has an initial boiling regime where the wall heat flux increases rapidly with decreasing wall temperature.…”

Section: Resultssupporting

confidence: 84%

“…The solid properties are varied as (ρc p ) s = 5 × 10 4 ∼ 5 × 10 6 J/m 3 K and λ s = 11 ∼ 44 W/mK to investigate their effects on the quenching process. We choose a nozzle width of W j = 1 mm, a jet velocity of V j = 0.8 m/s, a jet subcooling of T sat − T j = 16°C and an initial solid superheat of ΔT s,i = 400°C or 500°C, based on the experimental conditions of Robidou et al [3,4]. The computational domain is taken to be a two-dimensional region, as depicted in Fig.…”

Section: Resultsmentioning

confidence: 99%

“…Robidou et al [3,4] conducted steady-state experiments of entire boiling regimes in planar water jet impingement and presented steady-state boiling curves of wall heat flux versus temperature varying the jet velocity and subcooling. Under the conditions of a jet width of 1 mm, a jet velocity of 0.8 m/s and a subcooling of 16°C, the film boiling regime was observed to start at a wall temperature of about 450°C.…”

Section: Introductionmentioning

confidence: 99%

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Numerical simulation of the quenching process in liquid jet impingement

Lee

Son

Yoon

2015

International Communications in Heat and Mass Transfer

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Section: Resultssupporting

confidence: 84%

Section: Resultsmentioning

confidence: 99%

Section: Introductionmentioning

confidence: 99%

See 1 more Smart Citation

Numerical simulation of the quenching process in liquid jet impingement

Lee

Son

Yoon

2015

International Communications in Heat and Mass Transfer

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“…The surface heat flux curves are sharper and with higher peak for Re = 24,000, as compared to the wider curves with lower peak at Re = 5000. For a certain jet diameter, the effect of jet Reynolds number on surface cooling and heat flux can be attributed by [36][37][38][39]. This 'shoulder of flux' is due to periodic bubble oscillation at the hot wall surface due to hydrodynamic fragmentation of vapor spots by the jet.…”

Section: Effect Of Jet Reynolds Numbermentioning

confidence: 99%

Rewetting of hot vertical rod during jet impingement surface cooling

et al. 2015

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List of symbolsA Test-surface area (m 2 ) Bi Biot number, hD/2k s CHF Critical heat flux c p Specific heat of the surface material (kJ/kg K) d Jet diameter (m) D Test surface diameter (m) h Heat transfer coefficient (W/m 2 K) k Thermal conductivity (W/m K) l Downstream spatial location on test surface (m) Q Water flow rate (lpm) q Surface heat flux (W/m 2 ) Re Reynolds number (Ud/υ) Rw Rewetting number or dimensionless rewetting velocity (uD/2α) r Radial distance from the stagnation point (m) t Time (s) t d Wetting delay (s) T Temperature (°C) u Rewetting velocity (m/s) v Volume of test-section (m 3 ) z/d Dimensionless nozzle exit to test surface spacing Greek symbols υ Kinematic viscosity of water (m 2 /s) α Thermal diffusivity of surface (m 2 /s) ρ Density of surface material (kg/m 3 ) Subscripts B Bottom side downstream location e Experimental value i Initial value j Jet MFB Minimum film boiling m MaximumAbstract A stainless steel (SS-316) vertical rod of 12 mm diameter at 800 ± 10 °C initial temperature was cooled by normal impinging round water jet. The surface rewetting phenomenon was investigated for a range of jet diameter 2.5-4.8 mm and jet Reynolds number 5000-24,000 using a straight tube type nozzle. The investigation were made from the stagnation point to maximum 40 mm downstream locations, simultaneously for both upside and downside directions. The cooling performance of the vertical rod was evaluated on the basis of rewetting parameters i.e. rewetting temperature, wetting delay, rewetting velocity and the maximum surface heat flux. Two separate Correlations have been proposed for the dimensionless rewetting velocity in terms of rewetting number and the maximum surface heat flux that predicts the experimental data within an error band of ±20 and ±15 % respectively.

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“…Further, it has been recognized that the heat transfer during water cooling varies at the cooled surface in space and time [23,24]. In a number of publications two-dimensional inverse heat conduction model are used to identify heat flux and heat transfer coefficient [25][26][27][28][29]. Jha et al [27] and Sarkar et al [28] have assumed some simplifications such as adiabatic conditions at the surfaces that are not being cooled by jet impingement.…”

Section: Introductionmentioning

confidence: 99%

Implementation of one and three dimensional models for heat transfer coeffcient identification over the plate cooled by the circular water jets

et al. 2017

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A cooling rate affects the mechanical properties of steel which strongly depend on microstructure evolution processes. The heat transfer boundary condition for the numerical simulation of steel cooling by water jets can be determined from the local one dimensional or from the three dimensional inverse solutions in space and time. In the present study the inconel plate has been heated to about 900°C and then cooled by six circular water jets. The plate temperature has been measured by 30 thermocouples. The heat transfer coefficient and the heat flux distributions at the plate surface have been determined in time and space. The one dimensional solutions have given a local error to the heat transfer coefficient of about 35%. The three dimensional inverse solution has allowed reducing the local error to about 20%. The uncertainty test has confirmed that a better approximation of the heat transfer coefficient distribution over the cooled surface can be obtained even for limited number of thermocouples. In such a case it was necessary to constrain the inverse solution with the interpolated temperature sensors. List of symbols ATDAverage temperature difference between measured and computed temperature curves (°C)

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Local heat transfer from a hot plate to a water jet

Cited by 35 publications

References 8 publications

Numerical simulation of the quenching process in liquid jet impingement

Numerical simulation of the quenching process in liquid jet impingement

Rewetting of hot vertical rod during jet impingement surface cooling

Implementation of one and three dimensional models for heat transfer coeffcient identification over the plate cooled by the circular water jets

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