DOCSLIB.ORG

Simulation of Heat Transfer in the Multi-Layer Door of the Furnace U

Total Page：16

File Type：pdf, Size：1020Kb

Download full-text PDF Read full-text
Simulation of Heat Transfer in the Multi-Layer Door of the Furnace U World Academy of Science, Engineering and Technology International Journal of Mechanical and Mechatronics Engineering Vol:5, No:1, 2011 Simulation of Heat Transfer in the Multi-Layer Door of the Furnace U. Prasopchingchana workers [7] examined the combined conduction and mixed Abstract—The temperature distribution and the heat transfer convection flow field and temperature distribution in an rates through a multi-layer door of a furnace were investigated. The enclosure in the presence of vertical partition with finite inside of the door was in contact with hot air and the other side of the thickness and thermal conductivity. Nouanegue et al. [8] door was in contact with room air. Radiation heat transfer from the investigated conjugate heat transfer by natural convection, walls of the furnace to the door and the door to the surrounding area conduction and radiation in open cavities in which a uniform was included in the problem. This work is a two dimensional steady heat flux is applied to the inside surface of the solid wall state problem. The Churchill and Chu correlation was used to find local convection heat transfer coefficients at the surfaces of the facing the opening. Chiu and Yan [9] carried out a numerical furnace door. The thermophysical properties of air were the functions study in the radiation effect on the characteristics of the mixed of the temperatures. Polynomial curve fitting for the fluid properties convection fluid flow and heat transfer in inclined ducts. The were carried out. Finite difference method was used to discretize for effect of conduction of horizontal walls on natural convection conduction heat transfer within the furnace door. The Gauss-Seidel heat transfer in a square cavity is numerically investigated by Iteration was employed to compute the temperature distribution in Mobedi [10]. Molla and Hossain [11] examined the effect of the door. thermal radiation on a study two-dimensional mixed The temperature distribution in the horizontal mid plane of the convection laminar flow of viscous incompressible optically furnace door in a two dimensional problem agrees with the one thick fluid along a vertical wavy surface. dimensional problem. The local convection heat transfer coefficients This research aims to study the coupling between multi- at the inside and outside surfaces of the furnace door are exhibited. layer conduction, natural convection and surface radiation on Keywords—Conduction, heat transfer, multi-layer door, natural the multi-layer door of the furnace. The work used the convection Churchill and Chu [12] empirical correlation in the simulation to compute the average convection heat transfer coefficients. I. INTRODUCTION Later, the local convection heat transfer coefficients were EAT loss from a multi-layer door of a furnace is a determined. Then, radiation heat transfer coefficients were Hcombination problem of multi-layer conduction, natural computed. Finally, the temperature distribution and total heat convection and radiation. At present, several research works loss from the inside of the furnace to room air through the [1-11] have been devoted to investigate the conduction, multi-layer door of the furnace were investigated. natural convection and radiation phenomena. Prasopchingchana and Laipradit [1] performed a simulation of II. MODEL GOMETRY heat transfer in the glass panel of an oven using an empirical This research has been treated as a two dimensional steady- correlation for natural convection heat transfer on the surface state problem. There was hot air on the inside surface of the of the glass panel. Bilgen [2] carried out a numerical and multi-layer door and room air on the outside surface of the experiment study of conjugate heat transfer by conduction and multi-layer door. natural convection on a heated vertical wall. Simulation of natural convection and radiation in the gas cavity and heat Furnace conduction in the walls of an enclosure was performed by Kuznetsov and Sheremet [3]. Nouanegue and Bilgen [4] Tsur carried out a numerical study on vertical channel solar chimneys with a practical geometry, which consist of two Room air Hot air International Science Index, Mechanical and Mechatronics Engineering Vol:5, No:1, 2011 waset.org/Publication/1781 dimensional channel boarded by two solid walls. Xaman et al. T∞,2 [5] study laminar and turbulent natural convection combined T∞,1 with surface thermal radiation in a square cavity with a glass y wall. Zrikem et al. [6] numerically investigated coupled heat Tw Multi-layer door transfers by conduction, natural convection and radiation in x hollow structures heated from below or above. Oztop and co- Fig. 1 Model geometry The top and bottom sides of the multi-layer door were U. Prasopchingchana is with the Mechanical Engineering Department, assumed to be insulated. The multi-layer door of the furnace is Burapha University, Chonburi 20131 THAILAND (phone: 66-3810-2222 Ext. 50 cm. wide, 50 cm. high and 20.3 cm. thick. The multi-layer 3385 Ext. 104; fax: 66-3874-5806; e-mail: [email protected]). International Scholarly and Scientific Research & Innovation 5(1) 2011 229 scholar.waset.org/1307-6892/1781 World Academy of Science, Engineering and Technology International Journal of Mechanical and Mechatronics Engineering Vol:5, No:1, 2011 door of the furnace consists of 3 layers: fire clay brick, glass Radiation heat transfer from the furnace wall surfaces to the fiber insulation and steel sheet. The thermal conductivity inner door surface and from the outer door surface to the values [13] and the thickness values of each layer are shown surrounding area was included in the problem. The nonlinear in Table 1. equations of radiation heat transfer were linearized. Thus, the radiation heat transfer equations are TABLE I ⎛ ()k ⎞ qr,w = hr,1A⎜Tw − T ⎟ (6) PROPERTIES OF THE MULTI-LAYER DOOR ⎝ s,1 ⎠ Layer Material Thickness Thermal and (m) conductivity ⎛ ()k ⎞ (W/m⋅K) qr,sur = hr,2 A⎜T − Tsur ⎟ (7) ⎝ s,2 ⎠ 1 Fire clay brick 0.1 1.09 2 Glass fiber insulation 0.1 0.038 where hr,1 is the radiation heat transfer coefficient between the 3 Steel sheet 0.003 28 furnace wall surfaces and the furnace door surface, and hr,2 is the radiation heat transfer coefficient between the furnace door surface and the surrounding area. The radiation heat The emissivity values [13] at the surfaces of the multi-layer transfer coefficients are door inside and outside of the furnace are 0.75 and 0.066 ⎛ ()k −1 ⎞ 2 ()k −1 2 respectively. The temperatures at the furnace wall surfaces hr,1 = ε1σ ⎜Tw + T ⎟(Tw + []T ) (8) ⎝ s,1 ⎠ s,1 equaled the hot air temperatures in the cavity. Also, the and temperatures of the surrounding area equaled the room air 2 temperatures. ⎛ ()k −1 ⎞⎛ 2 ()k −1 ⎞ hr,2 = ε 2σ ⎜Tsur + T ⎟⎜Tsur + []Ts,2 ⎟ (9) ⎝ s,2 ⎠⎝ ⎠ III. MATHEMATICAL MODELS where ε is emissivity and σ is the Stefan-Boltzmann constant. Newton’s law of cooling was employed to determine the All properties of hot air and room air around the inside and the outside of the furnace door surfaces were obtained from heat transfer rates at the surfaces of the furnace door. To NIST (National Institute of Standards and Technology) determine the average Nusselt number, the work used the Standard Reference Database 23, Version 7.0 by polynomial Churchill and Chu empirical correlation [12]: curve fitting: 2 ⎧ 1/ 6 ⎫ 2 n−1 ⎪ 0.387Ra y ⎪ x = a1 + a2T f + a3T f + K + anT f (10) Nu y = ⎨0.825 + ⎬ (1) 9 /16 8/ 27 where x are the air properties, a are the polynomial curve ⎩⎪ []1+ ()0.492 / Pr ⎭⎪ n fitting coefficients and T is the film temperature of air. The where Ra is the Rayleigh number and Pr is the Prandtl f y errors of the properties derived from polynomial curve fitting number at the film temperatures. The film temperatures are are less than 0.1 percent. For all properties, n is 10. T f = (()Ts ave + T∞ )/ 2 (2) The volumetric thermal expansion coefficient is where ()Ts is the average temperature at the door surfaces 1 ⎛ ∂ ρ ⎞ ave β = - ⎜ ⎟ and T is the ambient temperature. The average convection ⎜ ⎟ ∞ ρ ⎝ ∂ T ⎠P heat transfer coefficients were obtained from 1 2 n−2 β = − (a2 + 2a3T f + 3a4T f + K + (n −1)anT ) (11) k f ρ f P h = Nu y (3) y y Within the thickness of the furnace door, the heat diffusion equation was used to calculate the temperature where kf is thermal conductivity of air. The local convection heat transfer coefficients could be obtained from distribution: ∂ 2T ∂ 2T 1 ⎛ y y+δy ⎞ + = 0 (12) h = ⎜ h δy + h δy⎟ 2 2 y+δy ⎜ ∫ y ∫ δy ⎟ ∂x ∂y y + δy ⎝ 0 y ⎠ The finite difference method was used to discretize Eq. (12) ⎛ 1 y ⎞ ⎛ 1 y+δy ⎞ and it yielded ()y + δy h = y⎜ ∫ h δy⎟ + δy⎜ ∫ h δy⎟ y+δy ⎜ y ⎟ ⎜ δy ⎟ ⎡ ⎤ ⎝ y 0 ⎠ ⎝ δy y ⎠ T ()k = Δy 2 ⎛T (k−1 )+ T ()k ⎞+ Δx 2 ⎛T (k−1 )+ T ()k ⎞ / International Science Index, Mechanical and Mechatronics Engineering Vol:5, No:1, 2011 waset.org/Publication/1781 ⎢ ⎜ ⎟ ⎜ ⎟⎥ i, j ⎣ ⎝ i+1, j i−1, j ⎠ ⎝ i, j+1 i, j−1 ⎠⎦ ()y + δy hy+δy = yhy + δyhδy 2()Δy 2 + Δx 2 (13) ()y + δy hy+δy − yhy The finite difference equation for the nodes close to the hδy = (4) δy interfaces as shown in Fig. 2 is Newton’s law of cooling was used to determine the convection heat transfer rates at the furnace door surfaces. The convection heat transfer rates at the furnace door surfaces are qδy = hδywδy(T∞ − Ts ) (5) where w is the furnace door width. International Scholarly and Scientific Research & Innovation 5(1) 2011 230 scholar.waset.org/1307-6892/1781 World Academy of Science, Engineering and Technology International Journal of Mechanical and Mechatronics Engineering Vol:5, No:1, 2011 ⎛ T (k) T (k−1) T (k) T (k−1) ⎞ ()k ⎡ kΔx ()k kΔx ()k−1 kΔy ()k−1 (k) ⎜ i−1, j i+1, j i, j−1 i, j+1 ⎟ T = ⎢ T + T + T Ti, j = ⎜ + + + ⎟ / 1, j ⎣2Δy 1,J −1 2Δy 1,J +1 Δx 2,J ⎜ R1 R2 R3 R3 ⎟ ⎝ ⎠ ⎤ + ()h1 j ΔyT∞,1 + ()hr,1 ΔyTw / ⎛ 1 1 1 1 ⎞ j ⎦⎥ ⎜ + + + ⎟ (14) ⎝ R1 R2 R3 R3 ⎠ ⎡kΔx kΔy ⎤ ⎢ + + ()h1 j Δy + ()hr,1 Δy⎥ (17) where R1, R2 and R3 are the thermal resistances.
Load more

Recommended publications
  • Chapter 6 Natural Convection in a Large Channel with Asymmetric
    Chapter 6 Natural Convection in a Large Channel with Asymmetric Radiative Coupled Isothermal Plates Main contents of this chapter have been submitted for publication as: J. Cadafalch, A. Oliva, G. van der Graaf and X. Albets. Natural Convection in a Large Channel with Asymmetric Radiative Coupled Isothermal Plates. Journal of Heat Transfer, July 2002. Abstract. Finite volume numerical computations have been carried out in order to obtain a correlation for the heat transfer in large air channels made up by an isothermal plate and an adiabatic plate, considering radiative heat transfer between the plates and different inclination angles. Numerical results presented are verified by means of a post-processing tool to estimate their uncertainty due to discretization. A final validation process has been done by comparing the numerical data to experimental fluid flow and heat transfer data obtained from an ad-hoc experimental set-up. 111 112 Chapter 6. Natural Convection in a Large Channel... 6.1 Introduction An important effort has already been done by many authors towards to study the nat- ural convection between parallel plates for electronic equipment ventilation purposes. In such situations, since channels are short and the driving temperatures are not high, the flow is usually laminar, and the physical phenomena involved can be studied in detail both by means of experimental and numerical techniques. Therefore, a large experience and much information is available [1][2][3]. In fact, in vertical channels with isothermal or isoflux walls and for laminar flow, the fluid flow and heat trans- fer can be described by simple equations arisen from the analytical solutions of the natural convection boundary layer in isolated vertical plates and the fully developed flow between two vertical plates.
    [Show full text]
  • Forced and Natural Convection
    FORCED AND NATURAL CONVECTION Forced and natural convection ...................................................................................................................... 1 Curved boundary layers, and flow detachment ......................................................................................... 1 Forced flow around bodies .................................................................................................................... 3 Forced flow around a cylinder .............................................................................................................. 3 Forced flow around tube banks ............................................................................................................. 5 Forced flow around a sphere ................................................................................................................. 6 Pipe flow ................................................................................................................................................... 7 Entrance region ..................................................................................................................................... 7 Fully developed laminar flow ............................................................................................................... 8 Fully developed turbulent flow ........................................................................................................... 10 Reynolds analogy and Colburn-Chilton's analogy between friction and heat
    [Show full text]
  • Convectional Heat Transfer from Heated Wires Sigurds Arajs Iowa State College
    Iowa State University Capstones, Theses and Retrospective Theses and Dissertations Dissertations 1957 Convectional heat transfer from heated wires Sigurds Arajs Iowa State College Follow this and additional works at: https://lib.dr.iastate.edu/rtd Part of the Physics Commons Recommended Citation Arajs, Sigurds, "Convectional heat transfer from heated wires " (1957). Retrospective Theses and Dissertations. 1934. https://lib.dr.iastate.edu/rtd/1934 This Dissertation is brought to you for free and open access by the Iowa State University Capstones, Theses and Dissertations at Iowa State University Digital Repository. It has been accepted for inclusion in Retrospective Theses and Dissertations by an authorized administrator of Iowa State University Digital Repository. For more information, please contact [email protected]. CONVECTIONAL BEAT TRANSFER FROM HEATED WIRES by Sigurds Arajs A Dissertation Submitted to the Graduate Faculty in Partial Fulfillment of The Requirements for the Degree of DOCTOR 01'' PHILOSOPHY Major Subject: Physics Signature was redacted for privacy. In Chapge of K or Work Signature was redacted for privacy. Head of Major Department Signature was redacted for privacy. Dean of Graduate College Iowa State College 1957 ii TABLE OF CONTENTS Page I. INTRODUCTION 1 II. THEORETICAL CONSIDERATIONS 3 A. Basic Principles of Heat Transfer in Fluids 3 B. Heat Transfer by Convection from Horizontal Cylinders 10 C. Influence of Electric Field on Heat Transfer from Horizontal Cylinders 17 D. Senftleben's Method for Determination of X , cp and ^ 22 III. APPARATUS 28 IV. PROCEDURE 36 V. RESULTS 4.0 A. Heat Transfer by Free Convection I4.0 B. Heat Transfer by Electrostrictive Convection 50 C.
    [Show full text]
  • Forced Convection Heat Transfer Convection Is the Mechanism of Heat Transfer Through a Fluid in the Presence of Bulk Fluid Motion
    Forced Convection Heat Transfer Convection is the mechanism of heat transfer through a fluid in the presence of bulk fluid motion. Convection is classified as natural (or free) and forced convection depending on how the fluid motion is initiated. In natural convection, any fluid motion is caused by natural means such as the buoyancy effect, i.e. the rise of warmer fluid and fall the cooler fluid. Whereas in forced convection, the fluid is forced to flow over a surface or in a tube by external means such as a pump or fan. Mechanism of Forced Convection Convection heat transfer is complicated since it involves fluid motion as well as heat conduction. The fluid motion enhances heat transfer (the higher the velocity the higher the heat transfer rate). The rate of convection heat transfer is expressed by Newton’s law of cooling: q hT T W / m 2 conv s Qconv hATs T W The convective heat transfer coefficient h strongly depends on the fluid properties and roughness of the solid surface, and the type of the fluid flow (laminar or turbulent). V∞ V∞ T∞ Zero velocity Qconv at the surface. Qcond Solid hot surface, Ts Fig. 1: Forced convection. It is assumed that the velocity of the fluid is zero at the wall, this assumption is called no‐ slip condition. As a result, the heat transfer from the solid surface to the fluid layer adjacent to the surface is by pure conduction, since the fluid is motionless. Thus, M. Bahrami ENSC 388 (F09) Forced Convection Heat Transfer 1 T T k fluid y qconv qcond k fluid y0 2 y h W / m .K y0 T T s qconv hTs T The convection heat transfer coefficient, in general, varies along the flow direction.
    [Show full text]
  • Chaotic Flow in a 2D Natural Convection Loop
    International Journal of Heat and Mass Transfer 61 (2013) 565–576 Contents lists available at SciVerse ScienceDirect International Journal of Heat and Mass Transfer journal homepage: www.elsevier.com/locate/ijhmt Chaotic flow in a 2D natural convection loop with heat flux boundaries ⇑ William F. Louisos a,b, , Darren L. Hitt a,b, Christopher M. Danforth a,c a College of Engineering & Mathematical Sciences, The University of Vermont, Votey Building, 33 Colchester Avenue, Burlington, VT 05405, United States b Mechanical Engineering Program, School of Engineering, The University of Vermont, Votey Building, 33 Colchester Avenue, Burlington, VT 05405, United States c Department of Mathematics & Statistics, Vermont Complex Systems Center, Vermont Advanced Computing Core, The University of Vermont, Farrell Hall, 210 Colchester Avenue, Burlington, VT 05405, United States article info abstract Article history: This computational study investigates the nonlinear dynamics of unstable convection in a 2D thermal Received 13 August 2012 convection loop (i.e., thermosyphon) with heat flux boundary conditions. The lower half of the thermosy- Received in revised form 1 February 2013 phon is subjected to a positive heat flux into the system while the upper half is cooled by an equal-but- Accepted 3 February 2013 opposite heat flux out of the system. Water is employed as the working fluid with fully temperature dependent thermophysical properties and the system of governing equations is solved using a finite vol- ume method. Numerical simulations are performed for varying levels of heat flux and varying strengths Keywords: of gravity to yield Rayleigh numbers ranging from 1.5 Â 102 to 2.8 Â 107.
    [Show full text]
  • Enhancement of Natural Convection Heat Transfer Coefficient by Using V-Fin Array
    International Journal of Engineering Research and General Science Volume 3, Issue 2, March-April, 2015 ISSN 2091-2730 Enhancement of Natural convection heat transfer coefficient by using V-fin array Rameshwar B. Hagote, Sachin K. Dahake Student of mechanical Engg. Department, MET’s IOE, Adgaon, Nashik (Maharashtra,India). Email. Id: [email protected], Contact No. +919730342211 Abstract— Extended surfaces known as fins are, used to enhance convective heat transfer in a wide range of engineering applications, and offer an economical and trouble free solution in many situations demanding natural convection heat transfer. Fin arrays on horizontal, inclined and vertical surfaces are used in variety of engineering applications to dissipate heat to the surroundings. Studies of heat transfer and fluid flow associated with such arrays are therefore of considerable engineering significance. The main controlling variables generally available to the designer are the orientation and the geometry of the fin arrays. An experimental work on natural convection adjacent to a vertical heated plate with a multiple V- type partition plates (fins) in ambient air surrounding is already done. Boundary layer development makes vertical fins inefficient in the heat transfer enhancement. As compared to conventional vertical fins, this V-type partition plate works not only as extended surface but also as flow turbulator. This V-type partition plate is compact and hence highly economical. The numerical analysis of this technique is done using Computational Fluid Dynamics (CFD) software, Ansys CFX , for natural convection adjacent to a vertical heated plate in ambient air surrounding. In numerical analysis angle of V-fin is further optimized for maximum average heat transfer coefficient.
    [Show full text]
  • Chapter 7. Convection and Complexity
    Chapter 7 Convection and complexity ... if your theory is found to be convection has been taken as the classic exam­ against the second law of ple of thermal convection, and the hexagonal planform has been considered to be typical of thermodynamics, I can give you no convective patterns at the onset of thermal con­ hope; there is nothing for it but to vection. Fifty years went by before it was real­ collapse in deepest humiliation. ized that Benard's patterns were actually driven from above, by surface tension. not from below by Eddington an unstable thermal boundary layer. Experiments Contrary to current textbooks ... the showed the san1.e style of convection when the fluid was heated from above, cooled from below observed world does not proceed or when performed in the absence of gravity. This from lower to higher "degrees of confirmed the top-down surface-driven nature of disorder", since when all the convection which is now called Marangoni or B€mard-Marangoni convection. gravitationally-induced phenomena Although it is not generally recognized as are taken into account the emerging such, mantle convection is a branch of the newly result indicates a net decrease in the renamed science of complexity. Plate tectonics may be a self-drivenfarjrom-equilibrium system that orga­ "degrees of disorder", a greater nizes itself by dissipation in and between the "degree of structuring" ... classical plates, the mantle being a passive provider of equilibrium thermodynamics ... has energy and material. Far-from-equilibrium sys­ to be completed by a theory of tems, particularly those in a gravity field, can locally evolve toward a high degree of order.
    [Show full text]
  • Convective Mass Transfer Correlations 5.9 Fluid Flow Through Pipes 5.10 Hot Wire Anemometer
    SCH1309 TRANSPORT PHENOMENA UNIT-V UNIT 5: Analogies for Transport processes Contents 5.1 Analogy for mass transfer 5.2 Application of dimensional analysis 5.3 Analogy among Mass, Heat and Momentum Transfer 5.4 Reynolds Analogy 5.5 Chilton Colburn analogy 5.6 Prandtl analogy 5.7 VanKarman analogy 5.8 Convective mass transfer correlations 5.9 Fluid flow through pipes 5.10 Hot wire anemometer 1 SCH1309 TRANSPORT PHENOMENA UNIT-V 5.1 Analogy of Mass Transfer Mass transfer by convection involves the transport of material between a boundary surface (such as solid or liquid surface) and a moving fluid or between two relatively immiscible, moving fluids. There are two different cases of convective mass transfer: 1. Mass transfer takes place only in a single phase either to or from a phase boundary, as in sublimation of naphthalene (solid form) into the moving air. 2. Mass transfer takes place in the two contacting phases as in extraction and absorption. Convective Mass Transfer Coefficient In the study of convective heat transfer, the heat flux is connected to heat transfer coefficient as Q A q h t s t m -------------------- (1.1) The analogous situation in mass transfer is handled by an equation of the form N A k c C As C A -------------------- (1.2) The molar flux N A is measured relative to a set of axes fixed in space. The driving force is the difference between the concentration at the phase boundary, CAS (a solid surface or a fluid interface) and the concentration at some arbitrarily defined point in the fluid medium, C A .
    [Show full text]
  • A Numerical Study of Natural Convection Properties of Supercritical Water (H2O) Using Redlich–Kwong Equation of State
    Sådhanå (2019) 44:37 Ó Indian Academy of Sciences https://doi.org/10.1007/s12046-018-1035-3Sadhana(0123456789().,-volV)FT3](0123456789().,-volV) A numerical study of natural convection properties of supercritical water (H2O) using Redlich–Kwong equation of state HUSSAIN BASHA1, G JANARDHANA REDDY1,* and N S VENKATA NARAYANAN2 1 Department of Mathematics, Central University of Karnataka, Kalaburagi 585 367, India 2 Department of Chemistry, Central University of Karnataka, Kalaburagi 585 367, India e-mail: [email protected]; [email protected]; [email protected] MS received 8 January 2018; revised 2 November 2018; accepted 16 November 2018; published online 25 January 2019 Abstract. In this article, the Crank-Nicolson implicit finite difference method is utilized to obtain the numerical solutions of highly nonlinear coupled partial differential equations (PDEs) for the flow of supercritical fluid (SCF) over a vertical flat plate. Based on the equation of state (EOS) approach, suitable equations are derived to calculate the thermal expansion coefficient (b) values. Redlich–Kwong equation of state (RK-EOS), Peng-Robinson equation of state (PR-EOS), Van der Waals equation of state (VW-EOS) and Virial equation of state (Virial-EOS) are used in this study to evaluate b values. The calculated values of b based on RK-EOS is closer to the experimental values, which shows the greater accuracy of the RK-EOS over PR-EOS, VW-EOS and Virial-EOS models. Numerical simulations are performed for H2O in three regions namely subcritical, supercritical and near critical regions. The unsteady velocity, temperature, average heat and momentum transport coefficients for different values of reduced pressure and reduced temperature are discussed based on the numerical results and are shown graphically across the boundary layer.
    [Show full text]
  • Viscosity Variation Effects on Heat Transfer and Fluid Flow Through Two-Layered Porous Media
    Journal of ChemicalBahadori Technology Fatemeh, and Sima Metallurgy, Rezvantalab 50, 1, 2015, 35-38 VISCOSITY VARIATION EFFECTS ON HEAT TRANSFER AND FLUID FLOW THROUGH TWO-LAYERED POROUS MEDIA Bahadori Fatemeh, Sima Rezvantalab Chemical Engineering Department, Received 10 June 2014 Urmia University of Technology, Urmia, Iran Accepted 24 November 2014 E-mail: [email protected] ABSTRACT Temperature dependent viscosity effects on natural convection in a composite cavity, isothermally heated from below and cooled from the opposing surface, are analyzed. The two-layered porous media was composed of two regions with different permeability. It is observed that viscosity reduction, due to temperature rising, affects heat transfer rate and fluid motion at the interface. Keywords: two layered porous media, viscosity, heat transfer, permeability ratio (Kr), streamline. INTRODUCTION tion for calculation of the overall Nusselt number for N horizontal sub layers. Lai and Kulacki [13] discussed Heat transfer in porous media has been extensively convection in a vertically divided rectangular cavity, of studied due to its numerous engineering and environ- the right hand side wall which was heated with constant mental applications. Oil recovery, underground spread heat flux. of pollutants, grain storage, geothermal systems, solar Egorov and Polezhaev [14] investigated a theoretical power collectors, optimal design of furnaces, compact model and showed that their numerical results are in the heat exchangers, packed-bed catalytic reactors and pas- line of their experimental data for multilayer insulation. sive thermal control devices are examples of applications In addition, Merrikh and Mohamad [15], Belghazi et al. of heat transfer in porous media. [16] and Ordo´n˜ez-Miranda and Alvarado-Gil [17] and Studies concerning natural convection in porous others, have investigated multilayered porous media.
    [Show full text]
  • Interferometric Study of Natural Convection Heat Transfer from a Vertical Flat Plate with Transverse Roughness Elements Sushil Hiroo Bhavnani Iowa State University
    Iowa State University Capstones, Theses and Retrospective Theses and Dissertations Dissertations 1987 Interferometric study of natural convection heat transfer from a vertical flat plate with transverse roughness elements Sushil Hiroo Bhavnani Iowa State University Follow this and additional works at: https://lib.dr.iastate.edu/rtd Part of the Mechanical Engineering Commons Recommended Citation Bhavnani, Sushil Hiroo, "Interferometric study of natural convection heat transfer from a vertical flat plate with transverse roughness elements " (1987). Retrospective Theses and Dissertations. 11669. https://lib.dr.iastate.edu/rtd/11669 This Dissertation is brought to you for free and open access by the Iowa State University Capstones, Theses and Dissertations at Iowa State University Digital Repository. It has been accepted for inclusion in Retrospective Theses and Dissertations by an authorized administrator of Iowa State University Digital Repository. For more information, please contact [email protected]. INFORMATION TO USERS While the most advanced technology has been used to photograph and reproduce this manuscript, the quality of the reproduction is heavily dependent upon the quality of the material submitted. For example: • Manuscript pages may have indistinct print. In such cases, the best available copy has been filmed. • Manuscripts may not always be complete. In such cases, a note will indicate that it is not possible to obtain missing pages. • Copyrighted material may have been removed from the manuscript. In such cases, a note will indicate the deletion. Oversize materials (e.g., maps, drawings, and charts) are photographed by sectioning the original, beginning at the upper left-hand comer and continuing from left to right in equal sections with small overlaps.
    [Show full text]
  • Investigation of the Natural Convection Boundary Condition in Microfabricated Structures
    International Journal of Thermal Sciences 47 (2008) 820–824 www.elsevier.com/locate/ijts Investigation of the natural convection boundary condition in microfabricated structures X. Jack Hu ∗, Ankur Jain 1, Kenneth E. Goodson Mechanical Engineering Department, Stanford University, Stanford, CA 94305, USA Received 26 March 2007; received in revised form 17 July 2007; accepted 18 July 2007 Available online 30 August 2007 Abstract Heat loss through surrounding air has an important thermal effect on microfabricated structures. This effect is generally modeled as a natural convection boundary condition. However, the correct procedure for the determination of the convective coefficient (h) at microscales continues to be debated. In this paper, a microheater is fabricated on a suspended thin film membrane. The natural convection on the microheater is investigated using 3-omega measurements and complex analytical modeling. It is found that the value of h that fits experimental data should have an apparently larger value than that at larger scales; however, it is also shown that the increased h is actually contributed by heat conduction instead of heat convection. A method of determining the correct h that can be used for microfabricated structures is proposed by using the heat conduction shape factor. © 2007 Elsevier Masson SAS. All rights reserved. Keywords: Microscale natural convection; Convective coefficient; 3-omega measurement; Micro-Electrical–Mechanical-System (MEMS) device; Micro fabricated structure; Microscale heat transfer 1. Introduction the relative change of importance of driving forces at the mi- croscale. Peirs et al. [1] have proposed a scaling law for natural 2 Natural convection is a frequently encountered boundary convective coefficient and suggested h ∼ 100 W/m K for air condition in the thermal design, testing and modeling of Micro- when the scale is less than 100 µm, which is 5–10 times larger Electrical–Mechanical-System (MEMS) devices.
    [Show full text]