Approximate analytic solutions for mixed convection heat transfer from a shear-flow past a rotating cylinder

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1 Proceedings of the 5th IASME/WSEAS Int. Conference on Heat Transfer, Thermal Engineering and Environment, Athens, Greece, August 5-7, 7 Approximate analytic solutions for mixed convection heat transfer from a shear-flow past a rotating cylinder Kenzu Abdella Trent University Department of Mathematics 6 Wes Bank Dr., Peterborough, ON Canada, K9J-7B8 kabdella@trentu.ca Felicia Magpantay Trent University Department of Mathematics 6 Wes Bank Dr., Peterborough, ON Canada, K9J-7B8 feliciamagpantay@trentu.ca Abstract: Presented in this paper is an analytic approximation to the thermal-fluid problem involving mixed convective heat transfer from a rotating isothermal cylinder placed in a non-uniform stream shear flow. The approximation is obtained using a series expansion of the scaled boundary layer equations in terms of an appropriate boundary layer variable. The resulting approximation is valid both for small time and for moderate and large times for which the Reynolds number of the flow is sufficiently large. Key Words: shear-flow, mixed and forced convection, rotating cylinder, boundary layer, viscous flow, laminar. Introduction The steady and unsteady heat transfer problems involving fluid flows past a circular cylinder have been extensively studied numerically, and theoretically as well as experimentally for a comprehensive list of references, see [,]. In addition to their direct applications in science and engineering, such flows exhibit the main characteristics commonly observed in most industrial problems and therefore can serve as prototypes for simulating many fundamental fluid dynamics problems [3-4]. However, most studies have focussed on forced and mixed heat transfer problems associated with uniform stream flows [-7]. In the present study, the thermal-fluid flow problem involving mixed convective heat transfer from a rotating circular cylinder placed in a non-uniform stream of shear flow is considered. While the focus of previous studies involving shear flows past a cylinder has been on the flow characteristics such as vortex shedding, boundary-layer separation and hydrodynamic forces, the focus of the present study is on the convective heat transfer processes. This problem has a direct relevance in a wide range of scientific and engineering applications including atmospheric flows, heat exchanger systems, and energy conservation [8,9]. This study is a direct extension of the recent work of Abdella and Nalitolela [] which investigated the two-dimensional forced convective heat transfer problem of the unsteady shear flow of a viscous incompressible fluid past a rotating circular cylinder. The heat transfer process is investigated using an analytical approximation obtained using a series expansion of the flow variable in terms of a boundary layer variable λ = t measures time and Pe repre- 8t Pe sents the Peclet number. The analytic approximations are therefore valid for the initial stages of problems involving small and moderate Reynolds numbers as well as for moderate and large times of sufficiently large Reynolds number problems. Governing Equation Consider the problem of mixed convection heat transfer from an unsteady flow past a circular cylinder of radius a centred at the origin and rotating at an angular velocity of Ω. The flow is assumed to be viscous and incompressible. It is also assumed that the flow remains laminar and two-dimensional for all times and for all parameter values considered in this paper. The surface of the cylinder is kept at a constant temperature T while the approaching stream with constant shear Uy =γy U is kept at constant temperature T x and y are the usual Cartesian coordinates. The temperature difference δt = T T is assumed to be positive, giving rise to the buoyancy force and inducing fluid motion. Applying the Boussinesq approximation and neglecting the effects of viscous dissipation and radiation the governing equations are given by the equations of mo-

2 Proceedings of the 5th IASME/WSEAS Int. Conference on Heat Transfer, Thermal Engineering and Environment, Athens, Greece, August 5-7, 7 tion and the energy equation: ζ t u ζ x v ζ y = ν ζ = ζ x ζ y ψ x ψ y T t u T x v T y = κ T x T y αg T x 3 t is time, g is acceleration due to gravity, α is the thermal expansion coefficient, u = ψ y and v = ψ are the velocity components in the x and y x directions respectively, ζ = v x u is the vorticity, y ψ is the stream function, T is the temperature, ν is the kinematic viscosity and κ is the thermal diffusivity. Introducing the following non-dimensional quantities x = x a,y = y a,u = u U,v = v U,t = tu a ψ = ψ,ζ = aζ au,φ = T T U δt,v = v U, and using the modified polar coordinates ξ,θ ξ =lnr equations -3 become ξ ζ e = ψ ζ t ξ ψ ζ ξ ζ Re ξ ζ e ξ Gr Re cos θ φ φ sin θ 4 ξ e ξ ψ ζ = ξ ψ 5 ξ φ e t = ψ φ ξ ψ φ ξ φ Pe ξ φ 6 we have dropped the primes.here the Reynolds, Peclet and the Grashof numbers are defined respectively as Re = au, Pe = RePr, and Gr = RaPr ν Ra = gαδta3 is the Rayleigh number and νκ Pr = ν is the Prandtl number. We also use the κ Richardson number, Ri = Gr Re. Note that, it is convenient to introduce the new ξ,θ coordinate system which maps the surface of the cylinder to ξ = and the infinite region exterior to the cylinder to the semi-infinite rectangular strip ξ, θ. The boundary conditions on the surface of the cylinder for t> include the usual no-slip, the impermeability and isothermal conditions: ψ =, ψ ξ =Ω, andφ =, on ξ = 7 Ω = aω is a non-dimensional angular velocity. The free stream conditions far away from the U cylinder surface are: φ, ζ K, and 8 ψ K 4 eξ Ve ξ sinθ K 4 eξ cos θ as ξ 9 K = aγ is a dimensionless shear parameter U and V is the dimensionless centre-line velocity taking on the values, or - depending on the stream flow direction. Since the flow variables are periodic with respect to θ, we invoke the following periodicity condition: χξ,θ,t=χξ,θ, t, χ represents the flow variables ψ, ζ or φ. Note that, on the surface of the cylinder ψ is overdetermined since it has two boundary conditions while ζ is underdetermined. To resolve this, we apply Green s Second identity which is given by: D g h h g da = C g h n h g n ds g and h are twice differentiable functions in the region D, C is the closed curve representing the boundary of D and represents the normal deriva- n tive. Then using ψ for g and the harmonic functions e mξ sinmθ and e mξ cosmθ for h in Green s identity, we obtain the following global integral conditions: e mξ ζ sinmθdθdξ =Vδ,m, e mξ ζ cosmθdθdξ = Kδ,m, ξ e ξ ζdθdξ = Ke ξ Ω. 3 for m =,,..., and δ i,j is the Kronecker delta function which is zero when i j and when i = j.

3 Therefore, these integral conditions essentially convert the surface and the free stream boundary conditions into conditions that are valid throughout the entire domain of the problem. Finally, we have the following initial conditions: Γ= Prλ cos θ Φ Φ λ sin θ. 4Re We now use the following single series expansions in λ in order to obtain analytic approximate solutions of the governing equations and the accompanying initial and boundary conditions: Proceedings of the 5th IASME/WSEAS Int. Conference on Heat Transfer, Thermal Engineering and Environment, Athens, Greece, August 5-7, 7 3 ζξ,θ,t==, ζξ,θ,t==, 4 { if ξ = φξ,θ,t== 5 if ξ. Note that the initial temperature distribution is singular and therefore results in a thin boundary-layer region close to the surface of the cylinder. 3 Approximate analytic solutions The governing equations described in the previous section are highly nonlinear. Therefore, it is not possible to obtain analytical solution valid for all time and all flow parameter values. In this section we obtain approximate solutions for the early development of the flow and the heat transfer process using series expansion in terms of an appropriate boundary layer parameter. Recall that the structure of the flow field and heat transfer process in the initial stages of the flow is characterized by a thin boundary layer-region near the cylinder surface. By examining the dominant terms of the initial solutions, it can be shown that the thickness 8t of this boundary layer is given by λ = Pe which measures the diffusive growth of the boundary-layer structure and is used to rescale the space coordinate ζ and the flow variables via the changes of variables ξ = λz, ψ = λψ, ζ = ω λ, φ = Φ Hence the λ thin boundary-layer is stretched and the initial singularity is removed with this change of variables and the governing equation become: ω Pr eλz z ω ω = ω λeλz Pr λ λ ω Reλ Ψ ω e λz ω = Ψ Φ eλz z Φ Φ Peλ ω e λz RaΓ 6 Ψ λ Ψ Ψ Φ λz Φ =λe Ψ Φ, 7 λ λ Φ, 8 Ψ=Ψ λψ λ Ψ... 9 ω = ω λω λ ω... Φ=Φ λφ λ Φ... Note that λ is a small parameter not only when t is small but also when Re is large. Therefore, these approximations are valid not only for small times but also for large times for problems with large Re. While the double series expansion used in [] and [] simplifies the analytic calculations, it is more advantageous to use the single expansion used in this paper since the validity of the single expansion in λ would only require that λ be small which can be achieved for moderate and large times provided that Re is sufficiently large. However, the double series expansion is valid only for small times. Substituting the above single expansions into the boundary layer equations and equating like powers of λ results in a hierarchy of boundary value problems for the expansion coefficients. 3. Linear approximation for all values of Pr The O and Oλ boundary value problems for the mixed convection case turn out to be independent of Ra. Therefore, the O approximations which are valid for all values of Pr are identical to those found in [] for the forced convection case and are given by: Φ = and ω = A θfe fz Ψ =Ωz A θ zerffz efz f 3 f = and Pr A θ =. V sin θ K cos θ K Ω 4 Similarly the Oλ approximations are identical to the forced case obtained in []: Φ = erfcz. 5 ω = K A θerfcfz A θ 4 erfcfz

4 Proceedings of the 5th IASME/WSEAS Int. Conference on Heat Transfer, Thermal Engineering and Environment, Athens, Greece, August 5-7, 7 4 A θe fz f 3 z 3 fz. 6 Ψ = Kz 6f F mθ erffz f z erfcfz zefz 8f F pθ za θ f, 7 F p θ = A θ4a θ F m θ = A θ 4A θ A θ =V sin θ K cos θ. T z,θ cosmθdθdz =, m =,, ξ ω zω z ω dθdz =Kz. 35 T z,θ = ω mzω m z ω. Solving equation 8 with f =and with respect to the Φ boundary conditions yields 3. Higher order approximations for Pr= Since the second and higher order approximations turn out to be analytically intractable for general values of Pr, we assume that Pr= for these approximations. 3.. The Oλ approximation The second order approximation is obtained by collecting the Oλ terms resulting in the following boundary value problems: Φ z Φ Φ = 4z z Φ Φ Φ Φ Pe Ψ Φ Ψ Φ ω f z ω f ω = 4f z z ω ω ω ω 8 Ra cosθ Re ez 9 Ψ =z ω zω ω Ψ 3 subject to boundary conditions Ψ Ψ =, =, and Φ = on z =, 3 Φ and ω as z 3 and the integral conditions, T z,θ sinmθdθdz =, m =,, Φ = zerfcz z e z. 36 Similarly, solving equation 9 with f =subject to the free-stream condition on ω, gives: ω = A θz A 3 θe z zerfz A θz e z zerfz 4 A e z 9z z 4 z 6 zerfz ReΩA 6 θ 3A θ 4A θ 96 ReA θa θ 6zerf z 8ze z erfz3 6z e z 6ze z Ra cos θ z3 4Re Ra cos θ 8Re ez 37 A 3 θ = A θa θ 4A 6 θ 3A θ ReA θω A θ 38 Applying the integral condition given by equations then gives the function A θ: 4 A θ =a a i siniθb i cosiθ 39 i= a =, a = V, a = Re 6V 3K 4KΩ4V K, 6 a 3 =, a 4 = ReK 3, 6

5 Proceedings of the 5th IASME/WSEAS Int. Conference on Heat Transfer, Thermal Engineering 3K K Ω b = V Re, b =3K, 4z 3 and Environment, 4z z Φ Athens, Greece, Φ August 5-7, 7 5 Φ 44 3 b 3 = ReVK, b 4 =. 4 Re Ψ Φ Ψ Φ Ψ Φ Ψ Φ Finally, integrating equation 3 subject to the surface boundary condition for Ψ yields: subject to Φ 3 =, on z =, and Φ 3 as z. 45 Then, solving equation 44, we obtain the following expression for Φ 3 : Ψ = A 4 θz A 5 θk z3 3 A 3θ 9 3 z e z zerfz3z 48 6 z3 A θ A θ 9 64 z 3 4 zerfz 48z e z zerfz 9 ReA θerfz z 3 erfz 3 zerfz e z 4z e z 4 96 ReA θ ze z 3erf z 9 za θ erfzz 9 6 z 3 z A θe z 4z 3 96 ΩReA θz erfzz 3 e z z 6 za θ erfzf zze z Ra cos θ 3zerf z 3e z 48 Re Ra cos θ z Re 4 the functions A 4 θ and A 5 θ determined by applying the surface boundary conditions are given by A 4 θ = ReA θa θ, 4 48 A 5 θ = 6 A 3θ 4 ReΩA Higher order approximation The boundary value problems for ω n and Ψ n, associated with the third and higher order approximations are too complex to solve analytically. Therefore, we only consider the Φ 3 problem which is given by: Φ 3 z Φ 3 4Φ 3 = 8 3 z3 z Φ Φ Φ 3 = A 6 θf za 7 θf z 3z 7 7 erfz 3 6 zez z3 e z 6 ReA θzerfzez 3 6 z erfz z5 e z ReA θe z F zi zerfczi 3 z erfczerfiz 3 ReA θerf z zi e z 46 I z= z erfses ds, I z= z erfcses ds, and I 3 z = z erfcs e s ds, F z= z, F z=ze z F zerfz. It can be shown that I z= z F, ; 3, ; z,i z= erfiz- I z F is the generalized hypergeometric function. Then applying the boundary conditions of equation 45, we obtain A 6 θ = ReA θ,a 7θ = c c ReA θ C c = 5, c = 8 3, and C = erfc se s ds =.397. Note that there is no Ra term in the expression forφ 3. In fact, it turns out that the leading Ra dependence term is order five. It can be shown that the leading Ra dependence of Φ is given by: Φ 5 Ra = F zra sinθ 48 6 F z =f zf z e z f 4 ze z f 5 f 6 f z = 8 z z z z e z f z = z 9 9 7z7 9 7z5 z3 z erfz 3

6 Proceedings of the 5th IASME/WSEAS Int. Conference on Heat Transfer, Thermal Engineering and Environment, Athens, Greece, August 5-7, 7 6 f 3 x = 7z5 44 5z 6 3/ f 3a 48z 5 44 f 3a = 5z z 8 3/ 3z 3 8z 3/ f 4 z = z 8 5z8 z6 5z4 8 9z 3 3 erfz e z z z z 5 z 3 3 erfze z z8 8 3z z4 7 3z 6 z f 5 z = 8 5z8 z6 7z z erfz 3z 4z f 6 z = / z 4z 3 e z f 6a f 6a =4erf z 3 4 3z z 4 4 Results and Discussion In this section, we test the validity of the analytic solution at the initial stages of a moderate Re flow and at the fully developed stage of a high Re flow. The test is carried out by comparing the results of the analytic solution with those of a high-resolution numerical solution obtained using a spectral finite difference scheme []. In this numerical approach, the flow variables as well as the temperature function are approximated in terms of truncated Fourier series expansion of N terms in the angular direction. The resulting 6N3 two dimensional partial differential equations in time and in the radial variable are then integrated using a finite difference procedure. In order to gain insight into the patterns of the heat transfer rate, we compute the local Nusselt number and the average Nusselt number variations with respect to time and radial component. The local Nusselt number Nu and average Nusselt number Nu are respectively defined as: Nuθ, t = Φ λ 49 z= Nut = Nuθ, tdθ. 5 Using the analytic approximation of the temperature function Φ and taking the derivative with respect to z and then finding its value at z =yields: Nuθ, t = 4 λ λn θraλ 3 sinθn θ ReA N θ = 8 θ C 96 N θ = Similarly, the average Nusselt number is given by: Nut = 4 λ λ 7 6C Oλ 3. 5 We begin with Figure the time evolution of the numerically simulated and the analytically determined local Nusselt s number are depicted for Ri=, Re=, K =., Ω =.5 and t =.,.5, and.5. As we can see from the figures, there is excellent agreement between the analytic approximations and the numerical simulations for all times presented. Note that, since Re is moderately large, the analytic solution is in good agreement even at t =.5 This is because our expansion is valid in this limit as well. Similar results are obtained for Re=5 as depicted in Figure 3. However, we notice that the analytic accuracy is not as high in Figure for t =.5. In this case, the analytic solution is not valid except for small time t since Re is also small. The surface vorticity distribution which is given by K A θ ζ,θ,t= λ A θ 4 A Ra cos θ θ λa 3 θ 8Re λ 53 is depicted in Figures 3 and 4 for Ri=, K =., Ω=.5, t =.,.5,.5 for Re values of 5 and respectively. Again we notice that the analytic solution becomes less accurate as time increases and as Re decreases. The integrated average Nusselt numbers are also compared in Figure 5 for K =., Ω=.5, Ri= and Re values of 5 and. We see that there is excellent agreement between the two solutions for small

7 Proceedings of the 5th IASME/WSEAS Int. Conference on Heat Transfer, Thermal Engineering and Environment, Athens, Greece, August 5-7, 7 7 values of t. However, as t increases the two solutions tend to deviate from each other as expected. Note also that the effect of the increase in Re is to enhance the heat transfer. Finally, the dependency on the shear parameter K is demonstrated in Figure 6 for Re=, Ri= and Ω=.. We note that the vorticity distribution becomes less symmetric with increasing shear. The figure also shows that shear enhances the surface vorticity in the upper half of the cylinder there are faster moving fluid particles with the maximum occurring at the top tip of the cylinder. Again the analytic approximations are in excellent agreement with the numerically predicted solutions. This is consistent with the findings in [] for the forced convection case. 5 Conclusion In this paper analytic approximations to the thermalfluid problem involving mixed convective heat transfer from a rotating isothermal cylinder placed in a non-uniform stream shear flow are presented. A convenient coordinate system is first introduced in order to simplify the geometry of the problem. The flow variables are then scaled with respect to the boundary layer parameter λ resulting in a set of boundary layer equations subject to appropriate initial and boundary conditions. The analytic approximations for the boundary value problem are obtained via a Fourier series expansion in terms of the boundary layer variable. The resulting approximations are valid not only for small time but also for moderate and large times provided that the Reynolds number of the flow is sufficiently large. Acknowledgements K. Abdella s general research in Applied Mathematics and Mathematical Modelling is supported by the Natural Sciences and Engineering Research Council of Canada NSERC. The authors would like to thank Almas Naseem for providing the numerical results. References [] Zdravkovich, M.M.: 997, Flow Around Circular Cylinders. Vol. : Fundamentals, Oxford University Press. [] Zdravkovich, M.M.: 3, Flow Around Circular Cylinders. Vol. : Fundamentals, Oxford University Press. [3] Richardson, P.D.: 963, Heat and mass transfer in turbulent separated flows. Chem. Eng. Sci. 8, [4] Churchill, S.W. and Bernstein, M.: 977, A correlation equation for forced convection from gases and liquids to a circular cylinder in cross flow. J. Heat Transfer. 94, [5] Bretherton, F.P.: 96, Slow viscous motion round a cylinder in a simple shear. J. Fluid Mech., [6] Jordan, S.K. and Fromm, J.E.: 97, Oscillating drag, lift and torque on a circular cylinder in a uniform flow. Phys. Fluids. 5, [7] Kiya, M., Tamura, H. and Arie, M.: 98, Vortex shedding from a circular cylinder in moderate Reynolds number shear flow. J. Fluid Mech., [8] Teleki, C., Fand, R.M. and Kaye, J.: 96, Influence of vertical vibrations on the rate of heat transfer from a horizontal cylinder in air. Wright Air Development Command TN [9] Taneda, S.: 977, Visual study of unsteady separated flows around bodies. Prog. Aero. Sci. 7, [] Abdella, K. and Nalitolela P.: 6, Approximate analytic solutions for forced convection heat transfer from a shear-flow past a rotating cylinder. J. Heat Transfer. submitted. [] D Alessio, S.J.D., Saunders, M.G. and Harmsworth, D.L.: 3, Forced and mixed convective heat transfer from accelerated flow past an elliptic cylinder. Int. J. Heat and Mass Transfer. 46, [] Rohlf, K. and D Alessio, S.J.D.: 5, Uniform shear flow past a circular cylinder. Acta Mechanica.

8 Proceedings of the 5th IASME/WSEAS Int. Conference on Heat Transfer, Thermal Engineering and Environment, Athens, Greece, August 5-7, t=. 5 t=. Nusselt Number 5 Surface Vorticity t=.5 t=.5 5 t= Figure, Re=, Ri=, K=., Ω=.5, t=.,.5,.5 Figure 4, Re=, Ri=, K=., Ω=.5, t=., Re= 6 t=. 5 Nusselt Number 4 3 Nusselt Number 5 t=.5 Re=5 t= Figure, Re=5, Ri=, K=., Ω=.5, t=.,.5, Figure 5, Re=5, Ri=5, K=., Ω=.5, t=. 3 K=. 6 t=. K= 4 Surface Vorticity t=.5 Surface Vorticity Figure 3, Re=5, Ri=, K=., Ω=.5, t=.,.5 Figure 6, Re=, Ri=, K=,., Ω=, t=.

Approximate Analytic solutions for mixed and forced convection heat transfer from an unsteady no-uniform flow past a rotating cylinder

Approximate Analytic solutions for mixed and forced convection heat transfer from an unsteady no-uniform flow past a rotating cylinder Kenzu Abdella Trent University Department of Mathematics 6 Wes Bank