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Journal articles on the topic 'Forced convection heat transfer'

Author: Grafiati

Published: 4 June 2021

Last updated: 19 February 2022

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1

Zhang, Tong, Shanshan Geng, Xin Mu, Jiamin Chen, Junyi Wang, and Zan Wu. "Thermal Characteristics of a Stratospheric Airship with Natural Convection and External Forced Convection." International Journal of Aerospace Engineering 2019 (September 8, 2019): 1–11. http://dx.doi.org/10.1155/2019/4368046.

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Though convective heat transfer is one of the main factors that dominate the thermal characteristics of stratospheric airships, there is no specific correlation equations for the calculation of convective heat transfer of airships. The equations based on flat plate and sphere models are all in use. To ameliorate the confusing situation of diverse convective heat transfer equations and to end the misuse of them in the thermal characteristic analysis of stratospheric airships, a multinode steady-state model for ellipsoid airships is built. The accuracy of the five widely accepted equations for natural convective heat transfer is compared and analysed on the proposed large-scale airship model by numerical simulation, so does that of the five equations for external forced convective heat transfer. The simulation method is verified by the available experimental data. Simulation results show that the difference of the five natural convection equations is negligible, while that of the five external forced convection equations must be considered in engineering. Forced convection equations with high precision and wide application should be further investigated.

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2

Dietrich, M., R. Blo¨chl, and H. Mu¨ller-Steinhagen. "Heat Transfer for Forced Convection Past Coiled Wires." Journal of Heat Transfer 112, no. 4 (1990): 921–25. http://dx.doi.org/10.1115/1.2910500.

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Heat transfer coefficients were measured for forced convection of isobutanol in crossflow past coiled wires with different coil geometries. Flow rate and heat flux have been varied over a wide range to include laminar and turbulent flow for convective sensible and subcooled boiling heat transfer. To investigate the effect of coil geometry on heat transfer, the wire diameter, coil diameter, and coil pitch were varied systematically. The measured data are compared with the predictions of four correlations from the literature.

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3

Ma, S. W., and F. M. Gerner. "Forced Convection Heat Transfer From Microstructures." Journal of Heat Transfer 115, no. 4 (1993): 872–80. http://dx.doi.org/10.1115/1.2911382.

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For many microstructures, which utilize forced convection cooling, the average thickness of the thermal boundary layer is of the same order as the length of the heated element. For these cases, thermal boundary layer theory is invalid. The elliptic energy equation for steady, two-dimensional incompressible flow over a finite flat plate with insulated starting and ending lengths is analyzed utilizing matched asymptotic expansions. A conventional Blasius technique transforms the energy equation into an elliptic-to-parabolic equation. A new technique is used that treats the boundary layer solution as the outer expansion of the elliptic-to-parabolic equation. The inner expansion, or leading-edge equation, is found by stretching to independent variables simultaneously. Trailing-edge effects are considered using superposition methods. A first-order composite formula is constructed based on the outer and inner expansions, which is uniformly valid over the entire surface of the plate. With the aid of statistics, a correlation is developed for the average Nusselt number Nu¯l=0.6626Pr1/3Rex0+l1/21−x0x0+l3/42/31+0.3981(x0/l)0.5987Pr0.3068Rex00.4675for0.5≤Pr≤100,x0/l≤50,andRex0≥100 where x0 and l represent the lengths of the insulated starting section and the heated element, respectively. This correlation is accurate to within 2 percent as compared with the entire composite solution.

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4

Babus'Haq, Ramiz F., and S. Douglas Probert. "Fundamentals of forced-convection heat-transfer." Applied Energy 47, no. 4 (1994): 381. http://dx.doi.org/10.1016/0306-2619(94)90045-0.

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5

Kumar, Mahesh, Pankaj Khatak, Ravinder Kumar Sahdev, and Om Prakash. "The effect of open sun and indoor forced convection on heat transfer coefficients for the drying of papad." Journal of Energy in Southern Africa 22, no. 2 (2011): 40–46. http://dx.doi.org/10.17159/2413-3051/2011/v22i2a3214.

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In this research paper, a simulation study has been carried out for the determination of convective heat transfer coefficients of papad under open sun drying and indoor forced convection drying modes. Experimental data obtained from open sun and indoor forced convection drying modes for papad were used to determine the values of the constants (C and n) in Nusselt number expression by using linear regression analysis, and consequently convective heat transfer coefficients were evaluated. The average values of convective heat transfer coefficients were found to be 3.54 and 1.56 W/m2 oC under open sun drying and indoor forced convection drying modes respectively. The experimental errors in terms of percent uncertainty were also evaluated.

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6

Chen, Chien-Hsin. "Forced convection heat transfer in microchannel heat sinks." International Journal of Heat and Mass Transfer 50, no. 11-12 (2007): 2182–89. http://dx.doi.org/10.1016/j.ijheatmasstransfer.2006.11.001.

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7

Benkhedda, F., T. Boufendi, and S. Touahri. "Prediction of Nanofluid Forced and Mixed Convection Heat Transfer through an Annular Pipe." International Journal of Materials, Mechanics and Manufacturing 5, no. 2 (2017): 87–91. http://dx.doi.org/10.18178/ijmmm.2017.5.2.296.

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8

Bunphet, Bongkot, Akihisa Toyoda, and Kouichi Kamiuto. "F214 Radial-Flow Forced-convection Heat Transfer in Narrow Open-Cellular Porous Channels." Proceedings of the Thermal Engineering Conference 2007 (2007): 367–68. http://dx.doi.org/10.1299/jsmeted.2007.367.

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9

Jani, Jaronie Mohd, Sunan Huang, Martin Leary, and Aleksandar Subic. "Analysis of Convective Heat Transfer Coefficient on Shape Memory Alloy Actuatorunder Various Ambient Temperatures with Finite Difference Method." Applied Mechanics and Materials 736 (March 2015): 127–33. http://dx.doi.org/10.4028/www.scientific.net/amm.736.127.

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The demand for shape memory alloy (SMA) actuators for technical applications is steadily increasing; however SMA may have poor deactivation time due to relatively slow convective cooling. Convection heat transfer mechanism plays a critical role in the cooling process, where an increase of air circulation around the SMA actuator (i.e. forced convection) provides a significant improvement in deactivation time compared to the natural convection condition. The rate of convective heat transfer, either natural or forced, is measured by the convection heat transfer coefficient, which may be difficult to predict theoretically due to the numerous dependent variables. In this work, a study of free convective cooling of linear SMAactuators was conducted under various ambient temperatures to experimentally determine the convective heat transfer coefficient. A finite difference equation (FDE) was developed to simulate SMA response, and calibrated with the experimental data to obtain the unknown convectiveheat transfer coefficient, h. These coefficients are then compared with the available theoretical equations, and it was found that Eisakhaniet. almodel provides good agreement with the Experiment-FDE calibrated results. Therefore, FDE is reasonably useful to estimate the convective heat transfer coefficient of SMA actuator experiments under various conditions, with a few identified limitations (e.g. exclusion of other associative heat transfer factors).

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10

Bergles, A. E. "Heat Transfer Enhancement—The Encouragement and Accommodation of High Heat Fluxes." Journal of Heat Transfer 119, no. 1 (1997): 8–19. http://dx.doi.org/10.1115/1.2824105.

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This review considers the many techniques that have been developed to enhance convective heat transfer. After introducing the techniques, the applications to most of the modes of heat transfer (single-phase forced convection, including compound techniques, pool boiling, convective boiling/evaporation, vapor-space condensation, and convective condensation) are described. Comments are offered regarding commercial introduction of this technology and the generations of heat transfer technology; advanced enhancement represents third-generation heat transfer technology.

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11

KASAO, Daisaku, and Takehiro ITO. "Forced convection heat transfer to supercritical helium." TEION KOGAKU (Journal of Cryogenics and Superconductivity Society of Japan) 21, no. 2 (1986): 70–77. http://dx.doi.org/10.2221/jcsj.21.70.

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12

Ramachandran, R. S., C. Kleinstreuer, and T. Y. Wang. "FORCED CONVECTION HEAT TRANSFER OF INTERACTING SPHERES." Numerical Heat Transfer, Part A: Applications 15, no. 4 (1989): 471–87. http://dx.doi.org/10.1080/10407788908944699.

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13

Vasil'yev, A. A. "Heat Transfer in Forced-Convection Film Boiling." International Journal of Fluid Mechanics Research 22, no. 2 (1995): 66–72. http://dx.doi.org/10.1615/interjfluidmechres.v22.i2.40.

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14

Bradley, Richard F., and James F. Hoburg. "Electrohydrodynamic Augmentation of Forced Convection Heat Transfer." IEEE Transactions on Industry Applications IA-21, no. 6 (1985): 1373–76. http://dx.doi.org/10.1109/tia.1985.349593.

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15

Cornelissen, M. C. M., and C. J. Hoogendoorn. "Forced convection heat transfer to supercritical helium." Applied Scientific Research 42, no. 2 (1985): 161–83. http://dx.doi.org/10.1007/bf02421348.

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16

Ward, S., J. M. V. Rayner, U. Möller, D. M. Jackson, W. Nachtigall, and J. R. Speakman. "Heat transfer from starlings sturnus vulgaris during flight." Journal of Experimental Biology 202, no. 12 (1999): 1589–602. http://dx.doi.org/10.1242/jeb.202.12.1589.

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Infrared thermography was used to measure heat transfer by radiation and the surface temperature of starlings (Sturnus vulgaris) (N=4) flying in a wind tunnel at 6–14 m s-1 and at 15–25 degrees C. Heat transfer by forced convection was calculated from bird surface temperature and biophysical modelling of convective heat transfer coefficients. The legs, head and ventral brachial areas (under the wings) were the hottest parts of the bird (mean values 6.8, 6.0 and 5.3 degrees C, respectively, above air temperature). Thermal gradients between the bird surface and the air decreased at higher air temperatures or during slow flight. The legs were trailed in the air stream during slow flight and when air temperature was high; this could increase heat transfer from the legs from 1 to 12 % of heat transfer by convection, radiation and evaporation (overall heat loss). Overall heat loss at a flight speed of 10.2 m s-1 averaged 11. 3 W, of which radiation accounted for 8 % and convection for 81 %. Convection from the ventral brachial areas was the most important route of heat transfer (19 % of overall heat loss). Of the overall heat loss, 55 % occurred by convection and radiation from the wings, although the primaries and secondaries were the coolest parts of the bird (2.2-2.5 degrees C above air temperature). Calculated heat transfer from flying starlings was most sensitive to accurate measurement of air temperature and convective heat transfer coefficients.

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17

Sahdev, Ravinder Kumar, Mahesh Kumar, and Ashwani Kumar Dhingra. "FORCED CONVECTION DRYING OF INDIAN GROUNDNUT: AN EXPERIMENTAL STUDY." Facta Universitatis, Series: Mechanical Engineering 15, no. 3 (2017): 467. http://dx.doi.org/10.22190/fume160812011s.

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In this paper, convective and evaporative heat transfer coefficients of the Indian groundnut were computed under indoor forced convection drying (IFCD) mode. The groundnuts were dried as a single thin layer with the help of a laboratory dryer till the optimum safe moisture storage level of 8 – 10%. The experimental data were used to determine the values of experimental constants C and n in the Nusselt number expression by a simple linear regression analysis and consequently, the convective heat transfer coefficient (CHTC) was determined. The values of CHTC were used to calculate the evaporative heat transfer coefficient (EHTC). The average values of CHTC and EHTC were found to be 2.48 W/m2 oC and 35.08 W/m2 oC, respectively. The experimental error in terms of percent uncertainty was also estimated. The experimental error in terms of percent uncertainty was found to be 42.55%. The error bars for convective and evaporative heat transfer coefficients are also shown for the groundnut drying under IFCD condition.

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18

Sukhotskii, A. B., and G. S. Sidorik. "EXPERIMENTAL STUDY OF HEAT TRANSFER OF A SINGLE-ROW BUNDLE OF FINNED TUBES IN MIXED CONVECTION OF AIR." ENERGETIKA. Proceedings of CIS higher education institutions and power engineering associations 60, no. 4 (2017): 352–66. http://dx.doi.org/10.21122/1029-7448-2017-60-4-352-366.

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The technique and results of experimental study of heat transfer of a single bundle consisting of bimetallic tubes with helically knurled edges, in natural and mixed convection of air are presented. Mixed convection, i.e. a heat transfer, when the contribution of free and forced convection is comparable, was created with the help of the exhaust shaft mounted above the heat exchanger bundle and forced air movement was created by the difference in density of the air in the shaft and the environment. The experimental dependence of the heat transfer of finned single row of bundles in the selected ranges of Grashof and Reynolds numbers has been determined. It is demonstrated that heat transfer in the mixed convection is 2.5−3 times higher than in free one and the growth rate of heat transfer with increasing Reynolds number is more than in the forced convection. Different forms of representation of results of experiments were analyzed and it was determined that the Nusselt number has a single power dependence on the Reynolds number at any height of the exhaust shafts. A linear dependence of the Reynolds number on the square root of the Grashof number was determined as well as the proportionality factors for different shaft heights. It is noted that the characteristics of the motion of air particles in the bundle in free convection is identical to the motion of particles in forced convection at small Reynolds numbers, i.e. a free convection flow smoothly flows into a forced convection one without the typical failures or surges if additional driving forces arise.

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19

Hireche, Zouhira, Lyes Nasseri, and Djamel Eddine Ameziani. "Heat transfer analysis of a ventilated room with a porous partition: LB-MRT simulations." European Physical Journal Applied Physics 91, no. 2 (2020): 20904. http://dx.doi.org/10.1051/epjap/2020200146.

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This article presents the hydrodynamic and thermal characteristics of transfers by forced, mixed and natural convection in a room ventilated by air displacement. The main objective is to study the effect of a porous partition on the heat transfer and therefore the thermal comfort in the room. The fluid flow future in the cavity and the heat transfer rate on the active wall have been analyzed for different permeabilities: 10−6 ≤ Da ≤ 10. The other control parameters are obviously, the Rayleigh number and the Reynolds number varied in the rows: 10 ≤ Ra ≤ 106 and 50 ≤ Re ≤ 500 respectively. The transfer equations write were solved by the Lattice Boltzmann Multiple Relaxation Time method. For flow in porous media an additional term is added in the standard LB equations, to consider the effect of the porous media, based on the generalized model, the Brinkman-Forchheimer-extended Darcy model. The most important conclusion is that the Darcian regime start for small Darcy number Da < 10−4. Spatial competition between natural convection cell and forced convection movement is observed as Ra and Re rise. The effect of Darcy number values and the height of the porous layer is barely visible with a maximum deviation less than 7% over the ranges considered. Note that the natural convection regime is never reached for low Reynolds numbers. For this Re values the cooperating natural convection only improves transfers by around 10% while, for the other Reynolds numbers the improvement in transfers due to natural and forced convections cooperation is more significant.

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20

Davalath, J., and Y. Bayazitoglu. "Forced Convection Cooling Across Rectangular Blocks." Journal of Heat Transfer 109, no. 2 (1987): 321–28. http://dx.doi.org/10.1115/1.3248083.

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Conjugate heat transfer for two-dimensional, developing flow over an array of rectangular blocks, representing finite heat sources on parallel plates, is considered. Incompressible flow over multiple blocks is modeled using the fully elliptic form of the Navier–Stokes equations. A control-volume-based finite difference procedure with appropriate averaging for the diffusion coefficients is used to solve the coupling between the solid and fluid regions. The heat transfer characteristics resulting from recirculating zones around the blocks are presented. The analysis is extended to study the optimum spacing between heat sources for a fixed heat input and a desired maximum temperature at the heat source.

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21

Gupta, Ritu, Parminder Singh, and R. K. Wanchoo. "Heat Transfer Characteristics of Nano-Fluids." Materials Science Forum 757 (May 2013): 175–95. http://dx.doi.org/10.4028/www.scientific.net/msf.757.175.

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Nanofluids are engineered colloids made of a base fluid and nanoparticles, which become potential candidate for next generation heat transfer medium. Nanofluids have higher thermal conductivity and single-phase heat transfer coefficients than their base fluids. The use of additives is a technique applied to enhance the heat transfer performance of base fluids. Recent articles address the unique features of nanofluids, such as enhancement of heat transfer, improvement in thermal conductivity, increase in surface volume ratio, Brownian motion, thermophoresis, etc. A complete understanding about the heat transfer enhancement in forced convection in laminar and turbulent flow with nanofluids is necessary for the practical applications. There are many controversies and inconsistencies in reported arguments and experimental results on various thermal characteristics such as effective thermal conductivity, convective heat transfer coefficient and boiling heat transfer rate of nanofluids. As of today, researchers have mostly focused on anomalous thermal conductivity of nanofluids. Although investigations on boiling, droplet spreading, and convective heat transfer are very important in order to exploit nanofluids as the next generation coolants, considerably less efforts have been made on these major features of nanofluids. This review summarizes recent research on fluid flow and heat transfer characteristics of nanofluids in forced and free convection flows and identifies opportunities for future research.

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22

Angirasa, Devarakonda. "Forced Convective Heat Transfer in Metallic Fibrous Materials." Journal of Heat Transfer 124, no. 4 (2002): 739–45. http://dx.doi.org/10.1115/1.1470491.

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A numerical study is reported for high Reynolds number forced convection in a channel filled with rigid metallic fibrous materials of high porosity. The effects of convective and form inertia, viscous shear, and thermal dispersion are all considered together. Inertia and thermal dispersion are modeled. The numerical results suggest that heat transfer rate increases with increasing Reynolds number within a range, but not significantly beyond that range. The heat transfer rate also increases with stagnant thermal conductivity, and decreases with Darcy number. The fiber thickness was found to have significant influence on thermal dispersion. The range of applicability of the local volume averaging in terms of the significant parameters is discussed.

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23

Rahman, M. M., M. M. Billah, and M. A. Alim. "Effect of Reynolds and Prandtl Numbers on Mixed Convection in an Obstructed Vented Cavity." Journal of Scientific Research 3, no. 2 (2011): 271–81. http://dx.doi.org/10.3329/jsr.v3i2.4344.

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A numerical investigation is conducted to analyze the steady flow and thermal fields as well as heat transfer characteristics in a vented square cavity with a built-in heat conducting horizontal solid circular obstruction. Hydrodynamic behavior, thermal characteristics and heat transfer results are obtained by solving the couple of Navier-Stokes and energy equations by using a weighted residuals Finite element method. The computation was made for different Reynolds number, Prandtl number ranging from 50 to 200 and from 0.71 to 7.1 at the three different convective regimes. Three different regimes are observed with increasing Ri: forced convection (with negligible free convection), mixed convection (comparable free and forced convection) and free convection dominated region (with higher free convection). The results are presented to show the effects of the Reynolds number, Prandtl number on flow pattern, thermal field and heat transfer characteristics at the three convective regimes. It is found that the flow and thermal field strongly depend on the Reynolds number, Prandtl number as well as Richardson number. As the Reynolds number and Prandtl number increase, the heat transfer rate increases but average fluid temperature in the cavity and temperature at the cylinder center decrease at the three convective regimes.Keywords: Mixed convection; Finite element method; Obstructed vented cavity; Prandtl number.© 2011 JSR Publications. ISSN: 2070-0237 (Print); 2070-0245 (Online). All rights reserved.doi:10.3329/jsr.v3i2.4344 J. Sci. Res. 3 (2), 271-281 (2011)

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Yu, D., T. A. Ameel, R. O. Warrington, and R. F. Barron. "Conjugate Heat Transfer With Buoyancy Effects From Micro-Chip Sized Repeated Heaters." Journal of Electronic Packaging 119, no. 4 (1997): 275–80. http://dx.doi.org/10.1115/1.2792249.

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Laminar mixed convection heat transfer across five in-line microchipsized heaters, surface mounted on printed circuit board (PCB), was investigated by the weighted residual finite element method. The effects of axial heat conduction within the PCB for both mixed convection and pure forced convection are reported. The flow regime considered was 200 ≤ Re ≤ 800 and 0 ≤ Gr ≤ 58,000. Internal heat generation was included in the microchip-sized blocks in order to accurately model the thermal response to predict the maximum temperature rise. On the outer PCB walls, convective heat transfer conditions were given. Thermophysical and transport properties based on materials used in the electronics industry, including orthotropic thermal conductivity in PCB, were used. The flow and solid domains were solved simultaneously. A sensitivity study of PCB heat transfer coefficients, isotropic thermal conductivity, thermal conductivity variations, and spacing effects was performed. The mixed convection transient heating process was compared with the steady-state formulation to estimate the influence of flow oscillation in heat transfer. It was found that the maximum temperature rise in the microchips predicted by pure forced convection was, at most, 10 percent higher than that predicted by mixed convection. The difference in maximum temperature between the trailing and leading chips in the array was 30 percent.

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MacDonald, M., N. Hutchins, and D. Chung. "Roughness effects in turbulent forced convection." Journal of Fluid Mechanics 861 (December 19, 2018): 138–62. http://dx.doi.org/10.1017/jfm.2018.900.

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We conducted direct numerical simulations of turbulent flow over three-dimensional sinusoidal roughness in a channel. A passive scalar is present in the flow with Prandtl number $Pr=0.7$, to study heat transfer by forced convection over this rough surface. The minimal-span channel is used to circumvent the high cost of simulating high-Reynolds-number flows, which enables a range of rough surfaces to be efficiently simulated. The near-wall temperature profile in the minimal-span channel agrees well with that of the conventional full-span channel, indicating that it can be readily used for heat-transfer studies at a much reduced cost compared to conventional direct numerical simulation. As the roughness Reynolds number, $k^{+}$, is increased, the Hama roughness function, $\unicode[STIX]{x0394}U^{+}$, increases in the transitionally rough regime before tending towards the fully rough asymptote of $\unicode[STIX]{x1D705}_{m}^{-1}\log (k^{+})+C$, where $C$ is a constant that depends on the particular roughness geometry and $\unicode[STIX]{x1D705}_{m}\approx 0.4$ is the von Kármán constant. In this fully rough regime, the skin-friction coefficient is constant with bulk Reynolds number, $Re_{b}$. Meanwhile, the temperature difference between smooth- and rough-wall flows, $\unicode[STIX]{x0394}\unicode[STIX]{x1D6E9}^{+}$, appears to tend towards a constant value, $\unicode[STIX]{x0394}\unicode[STIX]{x1D6E9}_{FR}^{+}$. This corresponds to the Stanton number (the temperature analogue of the skin-friction coefficient) monotonically decreasing with $Re_{b}$ in the fully rough regime. Using shifted logarithmic velocity and temperature profiles, the heat-transfer law as described by the Stanton number in the fully rough regime can be derived once both the equivalent sand-grain roughness $k_{s}/k$ and the temperature difference $\unicode[STIX]{x0394}\unicode[STIX]{x1D6E9}_{FR}^{+}$ are known. In meteorology, this corresponds to the ratio of momentum and heat-transfer roughness lengths, $z_{0m}/z_{0h}$, being linearly proportional to the inner-normalised momentum roughness length, $z_{0m}^{+}$, where the constant of proportionality is related to $\unicode[STIX]{x0394}\unicode[STIX]{x1D6E9}_{FR}^{+}$. While Reynolds analogy, or similarity between momentum and heat transfer, breaks down for the bulk skin-friction and heat-transfer coefficients, similar distribution patterns between the heat flux and viscous component of the wall shear stress are observed. Instantaneous visualisations of the temperature field show a thin thermal diffusive sublayer following the roughness geometry in the fully rough regime, resembling the viscous sublayer of a contorted smooth wall.

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Incropera, F. P. "Convection Heat Transfer in Electronic Equipment Cooling." Journal of Heat Transfer 110, no. 4b (1988): 1097–111. http://dx.doi.org/10.1115/1.3250613.

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To maintain the best possible thermal environment in electronic packages, the engineer must establish the most efficient path for heat transfer from the electronic devices to an external cooling agent. The path is typically subdivided into internal and external components, representing, respectively, heat transfer by conduction through different materials and interfaces separating the devices from the package surface and heat transfer by convection from the surface to the coolant. Depending on the scale and speed of the electronic circuits, as well as on constraints imposed by nonthermal considerations, the coolant may be a gas or a liquid and heat transfer may be by natural, forced, or mixed convection or, in the case of a liquid, by pool or forced convection boiling. In this paper a comprehensive review of convection cooling options is provided.

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W.Ezzat, Akram, and Hassan W. Zghaer. "Forced Convection Heat Transfer around Heated Inclined Cylinder." International Journal of Computer Applications 73, no. 8 (2013): 5–11. http://dx.doi.org/10.5120/12759-8631.

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SUZUKI, Kenjiro, Janusz S. SZMYD, and Hiromasa OHTSUKA. "Laminar forced convection heat transfer in eccentric annuli." Transactions of the Japan Society of Mechanical Engineers Series B 56, no. 531 (1990): 3445–50. http://dx.doi.org/10.1299/kikaib.56.3445.

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29

Ali, Mohamed, and O. Zeitoun. "Nanofluids forced convection heat transfer inside circular tubes." International Journal of Nanoparticles 2, no. 1/2/3/4/5/6 (2009): 164. http://dx.doi.org/10.1504/ijnp.2009.028749.

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30

Solanki, S. C., S. Prakash, J. S. Saini, and C. P. Gupta. "Forced convection heat transfer in doubly connected ducts." International Journal of Heat and Fluid Flow 8, no. 2 (1987): 107–10. http://dx.doi.org/10.1016/0142-727x(87)90007-5.

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31

Lin, Hsiao-Tsung, and Wen-Tong Cheng. "Rigorous solution of unsteady forced convection heat transfer." International Journal of Heat and Mass Transfer 38, no. 4 (1995): 748–52. http://dx.doi.org/10.1016/0017-9310(95)93008-6.

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32

Magen, M., B. B. Mikic, and A. T. Patera. "Bounds for conduction and forced convection heat transfer." International Journal of Heat and Mass Transfer 31, no. 9 (1988): 1747–57. http://dx.doi.org/10.1016/0017-9310(88)90189-5.

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33

Sucec, James, and David Radley. "Unsteady forced convection heat transfer in a channel." International Journal of Heat and Mass Transfer 33, no. 4 (1990): 683–90. http://dx.doi.org/10.1016/0017-9310(90)90167-s.

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34

Chang, S. W., and Y. Zheng. "Enhanced Heat Transfer with Swirl Duct Under Rolling and Pitching Environment." Journal of Ship Research 46, no. 03 (2002): 149–66. http://dx.doi.org/10.5957/jsr.2002.46.3.149.

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A detailed experimental investigation of heat transfer in a square duct fitted with twisted tape under a rolling and pitching environment is described, with particular reference to the heat transfer augmentation of shipping machinery. This study focuses on the development of an experimental procedure and methods for data processing, the parametric analysis and a selection of measurements that illustrate the manner by which the swinging forces and buoyancy interactively affect the local heat transfer. The swinging Coriolis force and buoyancy influence to a considerable extent the forced convection heat transfer in the swirl duct. Although enhancing the buoyancy level increases the heat transfer as the swirl duct rolls or pitches, the swinging Nusselt number is initially reduced relative to the stationary condition at the weak swinging oscillation, but tends to recover as the swinging force increases. The synergistic effects of harmonic and nonharmonic rolling and pitching oscillations reduce the heat transfer. Hot spots could develop in a swirl duct due to the slow rolling and/or pitching motions if the effect of the swinging oscillations on the heat transfer is not adequately considered. An empirical correlation has been developed for both single-axis and compound swinging conditions which permits the interactive effect of swinging Coriolis and buoyancy forces on forced convection to be quantified and which provides an evaluation of the local heat transfer in a swinging swirl duct.

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Sahdev, Ravinder Kumar. "Convective heat transfer coefficient for indoor forced convection drying of vermicelli." IOSR Journal of Engineering 02, no. 06 (2012): 1282–90. http://dx.doi.org/10.9790/3021-026112821290.

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Haryoko, Luthfi A. F., Jundika C. Kurnia, and Agus P. Sasmito. "Forced convection boiling heat transfer inside helically-coiled heat exchanger." IOP Conference Series: Earth and Environmental Science 463 (April 7, 2020): 012030. http://dx.doi.org/10.1088/1755-1315/463/1/012030.

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37

Schenone, C., and G. Tanda. "Forced heat convection heat transfer from shrouded staggered fin arrays." International Communications in Heat and Mass Transfer 17, no. 6 (1990): 747–58. http://dx.doi.org/10.1016/0735-1933(90)90020-k.

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38

Ma, Nancy, John Walker, David Bliss, and George Bryant. "Forced Convection During Liquid Encapsulated Crystal Growth With an Axial Magnetic Field." Journal of Fluids Engineering 120, no. 4 (1998): 844–50. http://dx.doi.org/10.1115/1.2820749.

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This paper treats the forced convection, which is produced by the rotation of the crystal about its vertical centerline during the liquid-encapsulated Czochralski or Kyropoulos growth of compound semiconductor crystals, with a uniform vertical magnetic field. The model assumes that the magnetic field strength is sufficiently large that convective heat transfer and all inertial effects except the centripetal acceleration are negligible. With the liquid encapsulant in the radial gap between the outside surface of the crystal and the vertical wall of the crucible, the forced convection is fundamentally different from that with a free surface between the crystal and crucible for the Czochralski growth of silicon crystals. Again unlike the case for silicon growth, the forced convection for the actual nonzero electrical conductivity of an indium-phosphide crystal is virtually identical to that for an electrically insulating crystal. The electromagnetic damping of the forced convection is stronger than that of the buoyant convection. In order to maintain a given balance between the forced and buoyant convections, the angular velocity of the crystal must be increased as the magnetic field strength is increased.

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Finn, D. P., P. F. Monaghan, and P. H. Oosthuizen. "Heat Transfer to Unfrosted Wind Convectors: Mathematical Modeling and Comparison With Experimental Results." Journal of Solar Energy Engineering 112, no. 4 (1990): 280–86. http://dx.doi.org/10.1115/1.2929935.

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Wind convectors are an alternative air source evaporator system for heat pumps. This paper describes a mathematical model that calculates the heat transfer to wind convectors when forced convection conditions prevail and when wind convector surface frost and rainfall are absent. The mathematical model is validated and predicts heat transfer to within 8 percent of experimental data based on a root mean square difference estimation. Further simulation studies show that heat transfer to wind convectors is dominated by sensible convection and latent heat transfer, that longwave radiation contributes less than 5 percent of total heat transfer and that solar radiation can contribute up to 25 percent of total heat transfer under optimum conditions.

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Nanri, Takayuki. "Forced-Convection Heat Transfer in a Combined Radiation and Convection Furnace." IEEJ Transactions on Fundamentals and Materials 111, no. 4 (1991): 305–14. http://dx.doi.org/10.1541/ieejfms1990.111.4_305.

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Dahl, S. D., and J. H. Davidson. "Mixed Convection Heat Transfer and Pressure Drop Correlations for Tube-ln-Shell Thermosyphon Heat Exchangers With Uniform Heat Flux." Journal of Solar Energy Engineering 120, no. 4 (1998): 260–69. http://dx.doi.org/10.1115/1.2888129.

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An important issue arising from prior studies of thermosyphon heat exchangers for use in solar water heaters is the need for heat transfer and pressure drop correlations for the laminar, mixed-convection regime in which these many of these heat exchangers operate. In this paper, we present empirical correlations for tube-in-shell heat exchangers with the thermosyphon flow on the shell side. The correlations are determined for uniform heat flux on the tube walls. Ranges of Reynolds and Grashof numbers are 130 to 2,000 and 4 × 105 to 8 × 107, respectively. Nusselt number correlations are presented in a form that combines the contributions of forced and natural convection. Mixed convection dominates forced convection heat transfer in these geometries. Pressure drop is not significantly affected by mixed convection.

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Kolev, Zhivko, and Seher Kadirova. "CFD simulation of forced heat transfer of gas in pipe." E3S Web of Conferences 112 (2019): 01008. http://dx.doi.org/10.1051/e3sconf/201911201008.

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This paper presents results from CFD simulation of heat transfer processes in ABAQUS. The investigations are realized at forced convection of air in steel pipe. Verification of the computing mesh and validation of the model, have been done. The average heat convection coefficients have been determined by methodology based on criteria equations, and on simulation methodology. Heat transfer processes between air flow in a steel pipe and the environment, have been experimentally accomplished. In order to analyze the processes of heat convection between the fluid and the internal surface of the pipe, numerical modelling is applied. A geometric model of the fluid flowing in the pipe is built. The computing mesh has been verified by increasing the number of cells and nodes. The numerical model has been validated based on experimentally measured temperature values and the simulation data. The heat convection coefficients have been investigated by analogy of the above. The results demonstrate that the numerical model is adequate and can be used to study similar heat transfer processes.

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Murata, K., and K. Hashizume. "Forced Convective Boiling of Nonazeotropic Refrigerant Mixtures Inside Tubes." Journal of Heat Transfer 115, no. 3 (1993): 680–89. http://dx.doi.org/10.1115/1.2910739.

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Forced convective boiling of nonazeotropic mixtures inside horizontal tubes was investigated experimentally. The heat transfer coefficient and pressure drop of pure refrigerant R123 and a mixture of R123 and R134a were measured in both a smooth tube and a spirally grooved tube. The heat transfer coefficient for the mixture was found to be lower than that for an equivalent pure refrigerant with the same phsycial properties, not only in the boiling-dominant region but also in the convection-dominant region. On the basis of this experiment, correlations were proposed for heat transfer coefficients in smooth and grooved tubes; the reduction in heat transfer coefficient for the mixture is attributed to the mixture effects on nucleate boiling and to the heat transfer resistance in the vapor phase. This heat transfer resistance is caused by the sensible heating of the vapor phase accompanying the rise in saturation temperature. These correlations are able to predict the heat transfer data within ± 20 percent

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Vairavan, Rajendaran, Vithyacharan Retnasamy, Zaliman Sauli, Hussin Kamarudin, Muammar Mohamad Isa, and Steven Taniselass. "Heat Sink Cooling Fan and Rotation Speed Effect Analysis on Heat Dissipation of High Power GaN LED Package." Advanced Materials Research 1082 (December 2014): 315–18. http://dx.doi.org/10.4028/www.scientific.net/amr.1082.315.

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In this work, thermal simulation analysis on high power LED is reported where the effect of the heat sink cooling fan and its rotation speed on the heat dissipation of the high power LED was evaluated. Ansys version 11 was utilized for the simulation. The thermal performance of the high power LED package was assessed in terms of operating junction temperature, von Mises stress and thermal resistance. The heat dissipation analysis was done under four types of convection condition:one natural convection conditionthree forced convection condition,. The forced convection condition was used to replicate the effect of a fan with various rotation speeds placed under the heat sink to increase the convective heat transfer coefficient. Results of the analysis showed that that the junction temperature, von Mises stress and thermal resistance of the GaN chip reduces with the increase of the fan rotation speed.

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Kang, B. H., Y. Jaluria, and S. S. Tewari. "Mixed Convection Transport From an Isolated Heat Source Module on a Horizontal Plate." Journal of Heat Transfer 112, no. 3 (1990): 653–61. http://dx.doi.org/10.1115/1.2910437.

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An experimental study of the mixed convective heat transfer from an isolated source of finite thickness, located on a horizontal surface in an externally induced forced flow, has been carried out. This problem is of particular interest in the cooling of electronic components and also in the thermal transport associated with various manufacturing systems, such as ovens and furnaces. The temperature distribution in the flow as well as the surface temperature variation are studied in detail. The dependence of the heat transfer rate on the mixed convection parameter and on the thickness of the heated element or source, particularly in the vicinity of the source, is investigated. The results obtained indicate that the heat transfer rate and fluid flow characteristics vary strongly with the mixed convection variables. The transition from a natural convection dominated flow to a forced convection dominated flow is studied experimentally and the basic characteristics of the two regimes determined. This transition has a strong influence on the temperature of the surface and on the heat transfer rate. As expected, the forced convection dominated flow is seen to be significantly more effective in the cooling of a heat dissipating component than a natural convection dominated flow. The location of the maximum temperature on the module surface, which corresponds to the minimum local heat transfer coefficient, is determined and discussed in terms of the underlying physical mechanisms. The results obtained are also compared with these for an element of negligible thickness and the effect of a significant module thickness on the transport is determined. Several other important aspects of fundamental and applied interest are studied in this investigation.

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Ho, C. J., and F. J. Tu. "Laminar Mixed Convection of Cold Water in a Vertical Annulus With a Heated Rotating Inner Cylinder." Journal of Heat Transfer 114, no. 2 (1992): 418–24. http://dx.doi.org/10.1115/1.2911290.

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A numerical investigation is made to evaluate the perturbing effect of forced convection due to axial rotation of the inner cylinder on natural convection heat transfer of cold water with density inversion effects in a vertical cylindrical annulus. The mixed convection heat and fluid flow structures in the annulus are found to be strongly affected by the density inversion effects. The centrifugally forced convection can result in significant enhancement of the buoyant convection heat transfer of cold water with the density inversion parameter being equal to 0.4 or 0.5; thus the slow axial rotation of the inner cylinder can be a viable means for heat transfer augmentation of cold water natural convection in a vertical annulus.

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Michiyoshi, I. "Boiling Heat Transfer in Liquid Metals." Applied Mechanics Reviews 41, no. 3 (1988): 129–49. http://dx.doi.org/10.1115/1.3151887.

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This article presents the state-of-the-art review of boiling heat transfer in various liquid metals paying attention to research papers published in the last 15 years. Particular emphasis is laid on the incipient boiling superheat, diagnosis of natural and forced convection boiling, nucleate pool boiling heat transfer in mercury, sodium, potassium, NaK, lithium, and so on at sub- and near atmospheric pressure, effect of liquid level on liquid metal boiling, subcooling effect due to hydrostatic head on liquid metal boiling, effect of magnetic field on liquid metal boiling, pool boiling crisis under various conditions and intermittent boiling of liquid metal, two-phase flow heat transfer, and natural and forced convection film boiling in saturated and subcooled liquid metals. In conclusion, there still remain some ambiguous and unsolved problems which are pointed out in this article. Further studies are of course required to clarify and solve them in future with both theoretical and experimental approaches.

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Angirasa, D., and G. P. Peterson. "Forced Convection Heat Transfer Augmentation in a Channel With A Localized Heat Source Using Fibrous Materials." Journal of Electronic Packaging 121, no. 1 (1999): 1–7. http://dx.doi.org/10.1115/1.2792656.

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A numerical model is developed for high Reynolds number forced convection heat transfer in a channel filled with randomly oriented, thin fibrous materials of high porosity. A localized isothermal heat source, flush with one of the channel walls is considered to simulate an electronic component. The inertial coefficient and the dispersion conductivity associated with high Reynolds number flows and convective heat transfer are empirically modeled from existing experimental and analytical studies. The resulting fluid flow and heat transfer relationships are presented for a relevant range of parameters, and the fundamental physical processes are explained.

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Jou, Rong Yuan. "Convective Heat Transfer Measurements of Die-Casting Heat Sinks." Key Engineering Materials 419-420 (October 2009): 345–48. http://dx.doi.org/10.4028/www.scientific.net/kem.419-420.345.

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For applications of high-power LED illumination and advanced CPU electronic cooling, since the traditional plate heat sinks by aluminum extrusion are simple geometry only and with limited thermal performance, a new design and new fabrication process of heat sink for high-density heat flux applications is inevitable. In this study, a heat sink fabricated by vacuum die-casting is analyzed. To evaluate the thermal performance of this heat sink, two experiments, free convection measurements in an enclosure and forced convection measurements in a wind tunnel, are conducted by two experimental methods of thermocouples and IR thermograph. As to free convection experiments, compared to the free convection over a plate, temperature decrement by the attached casting of pin-fin heat sink is 46.2% for the input power of 10W. In the case of 15W heating power, temperature distribution along center pin shows uniformly distributed temperature along length direction, but there is a temperature difference of 9.5°C,varied from 86.9°C to 77.4°C, at outer pin. As to the case of 10W heating power, there is a temperature difference of 6.5°C, varied from 69.2.9°C to 62.6°C, at the outer pin. Furthermore, forced convection experiments show that resistances of heat-sink casting are decreased when Reynolds numbers are increased, and a linear relationship between pressure drop and Reynolds number is noticed. Base on the measurement results, this heat sink casting can be a feasible thermal solution of LED and high-power chip products.

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Vafaei, Saeid, Jonathan A. Yeager, Peter Daluga, and Branden Scherer. "Forced Convection Nanofluid Heat Transfer as a Function of Distance in Microchannels." Materials 14, no. 11 (2021): 3021. http://dx.doi.org/10.3390/ma14113021.

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As electronic devices become smaller and more powerful, the demand for micro-scale thermal management becomes necessary in achieving a more compact design. One way to do that is enhancing the forced convection heat transfer by adding nanoparticles into the base liquid. In this study, the nanofluid forced convection heat transfer coefficient was measured inside stainless-steel microchannels (ID = 210 μm) and heat transfer coefficient as a function of distance was measured to explore the effects of base liquid, crystal phase, nanoparticle material, and size on heat transfer coefficient. It was found that crystal phase, characteristics of nanoparticles, the thermal conductivity and viscosity of nanofluid can play a significant role on heat transfer coefficient. In addition, the effects of man-made and commercial TiO2 on heat transfer coefficient were investigated and it was found that man-made anatase TiO2 nanoparticles were more effective to enhance the heat transfer coefficient, for given conditions. This study also conducted a brief literature review on nanofluid forced convection heat transfer to investigate how nanofluid heat transfer coefficient as a function of distance would be affected by effective parameters such as base liquid, flow regime, concentration, and the characteristics of nanoparticles (material and size).

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