CHAPTER 7 FREE CONVECTION 7.1 Introduction Applications: Solar collectors Pipes Ducts Electronic packages Walls and windows 7.2 Features and Parameters of Free Convection (1) Driving Force: Natural 1 Requirements: (i) Acceleration field, (ii) Density gradient Te g d g e (2) Governing Parameters: Two: (i) Grashof number GrL GrL β g(Ts T )L3 ν 2 (7.1) = coefficient of thermal expansion (compressibility), a property 1 T for ideal gas (2.21) 2 (ii) Prandtl number Pr Pr c p k Rayleigh number Ra L g(Ts T ) L3 g(Ts T ) L3 Ra L GrL Pr Pr = 2 (7.2) (3) Boundary Layer: laminar, turbulent or mixed Criterion: Ra x 104 (4) Transition: Laminar to Turbulent Flow Criterion for vertical plates: Transition Rayleigh number 3 Ra x t 109 (5) External vs. Enclosure free convection: (i) External: over: Vertical surfaces Inclined surfaces Horizontal cylinders Spheres (ii) Enclosure: in: 4 Rectangular confines Concentric cylinders Concentric spheres (6) Analytic Solution Rs u i n o e c , ma e o i 7.3 Governing Equations Approximations: (1) Density is constant except in gravity forces 5 (2) Boussinesq approximation: relate density change to temperature change (3) Negligible dissipation Assume: Steady state Two-dimensional Laminar Continuity: u v 0 x y (7.1) x-momentum: 6 u u 1 2u 2u u v g (T T ) ( p p ) v ( 2 2 ) x y x x y (7.2) y-momentum: v v 1 2v 2v u v ( p p ) v ( 2 2 ) x y y x y (7.3) Energy: 2T 2T T T u v 2 2 x y y x (7.4) NOTE: (1) Gravity points in the negative x-direction (2) Flow and temperature fields are coupled 7 7.3.1 Boundary Layer Equations • Velocity and temperature boundary layers • Apply approximation used in forced convection y-component of the Navier-Stokes equations reduces to ( p p ) 0 y (a) External flow: Neglect ambient pressure variation in x ( p p ) 0 x (b) Furthermore, for boundary layer flow 8 2u x 2 2u y 2 (c) x-momentum: u u 2u u v βg T T v 2 x y y (7.5) Neglect axial conduction 2T x 2 2T y 2 (d) Energy: (7.4) becomes T T 2T u v α 2 x y y (7.6) 9 7.4 Laminar Free Convection over a Vertical Plate: Uniform Surface Temperature Vertical plate Uniform temperature Ts Infinite fluid at temperatureT Determine: velocity and temperature distribution 7.4.1 Assumptions (1) Steady state (2) Laminar flow (3) Two-dimensional 10 (1) (2) (3) (4) (5) (9) Constant properties Boussinesq approximation Uniform surface temperature Uniform ambient temperature Vertical plate Negligible dissipation 7.4.2 Governing Equations Continuity: u v 0 x y (7.1) x-momentum: 11 u u 2u u v βg T T v 2 x y y (7.5) Energy: 2 u v α 2 x y y (7.7) where is a dimensionless temperature defined as T T Ts T (7.8) 7.4.3 Boundary Conditions Velocity: (1) u( x ,0) 0 (2) v ( x ,0) 0 12 (3) u( x , ) 0 (4) u( 0, y ) 0 Temperature: (5) ( x ,0) 1 (6) ( x , ) 0 (7) ( 0, y ) 0 7.4.4 Similarity Transformation Transform three PDE to two ODE Introduce similarity variable ( x , y ) y ( x, y) C x 1/ 4 (7.8) 13 βg Ts T C 4v 2 1/ 4 (7.9) (7.9) into (7.8)7 Grx η 4 1/ 4 y x (7.10) Local Grashof number: Grx β g(Ts T )x 3 ν 2 (7.11) Let ( x , y ) ( ) (7.12) Stream function satisfies continuity 14 u y (7.14) Using Blasius solution as a guide, for this problem is 1 4 Grx ψ 4v ξ η 4 (7.15) ( ) is an unknown function Introduce (7.15) into (7.13) and (7.14) Grx d u 2v x d (Grx )1 / 4 d v 1/ 4 3 x ( 4) d v (7.16) (7.17) 15 Combining (7.5), (7.7), (7.8), (7.12), (7.16), (7.17) d 3 d 3 3 d 2 d 2 2 d d 2 0 2 d d 2 3 Pr d 0 d (7.18) (7.19) NOTE x and y are eliminated (7.18) and (7.19) Single independent variable Transformation of boundary conditions: Velocity: 16 d (0) 0 (1) d (2) ( 0) 0 d ( ) (3) 0 d d ( ) 0 (4) d Temperature: (1) ( 0) 1 (2) ( ) 0 (3) ( ) 0 17 NOTE: (1) Three PDE are transformed into two ODE (3) Five BC are needed (4) Seven BC are transformed into five (5) One parameter: Prandtl number. 7.4.5 Solution • (7.18) and (7.19) are solved numerically • Solution is presented graphically • Figs. 7.2 gives u(x,y) • Fig. 7.3 gives T(x,y) 18 19 20 7.4.5 Heat Transfer Coefficient and Nusselt Number Start with T ( x ,0 ) k y h Ts T (7.20) Express in terms of and k dT d (0) h Ts T d d y Use (7.8) and (7.10) k Grx h x 4 1/ 4 d (0) d (7.21) 21 Define: local Nusselt number: hx Grx Nu x k 4 1/ 4 d ( 0 ) d (7.22) Average heat transfer coefficient 1 L h h( x )dx L 0 (2.50) (7.21) into (2.50), integrate 4 k GrL h 3 L 4 1/ 4 d ( 0 ) d (7.23) Average Nusselt number 22 hL 4 k GrL Nu L k 3 L 4 1/ 4 d (0) d T a b l e 7 . 1 [1 , 2 ] (7.24) 2 P d (0) d Ik f D V O d 2 (0) d 2 i s oP n a l iT 7 f n s d ( 0) d ( 0) 2 d d 0.01 0.03 0.09 0.5 0.72 0.733 se 1.0 1.5e 2.0 3.5a 5.0 7.0 10 100 1000 _ r 0.0806 0.9862 0.136 0.219 0.442 0.5045 0.676 0.508 0.6741 a no 0.5671 0.6421 u 0.6515 n r 0.7165 0.5713 r i na 0.8558 0.954 u 1.0542 r 1.1649 0.4192 2.191 0.2517 3.9660 0.1450 in Table 7.1 gives surface velocity gradient and shearing stress 23 Special Cases Nu x 0.600( PrRa x )1/4 , Nu x 0.503( PrGrx )1/4 , Pr 0 Pr (7.24) (7.25) Example 7.1: Vertical Plate at Uniform Surface Temperature 8cm 8cm vertical plate in air at 10 oC Uniform surface temperature = 70 oC Determine the following at x L = 8 cm: (1) u at y = 0.2 cm , (2) T at y = 0.2 cm (3) d , (4) d t 24 (5) Nu L , (6) h(L) (7) qs (L) , (8) qT Solution (1) Observations External free convection Vertical plate Uniform surface temperature • Check Rayleigh number for laminar flow If laminar, Fig. 7.2 for u(x,y) and Fig. 7.3 T(x,y) and d t Determine local Nu and h at x = L (2) Problem Definition 25 Determine flow and heat transfer characteristics for free convection over a vertical flat plate at uniform surface temperature. (3) Solution Plan Laminar flow? Compute Rayleigh number If laminar, use Figs. 7.2 and 7.3. Use solution for Nu and h (4) Plan Execution (i) Assumptions (1) Newtonian fluid (2) Steady state (3) Boussinesq approximations (4) Two-dimensional 26 (5) Laminar flow ( Rax 109 ) (6) Flat plate (7) Uniform surface temperature (8) No dissipation (9) No radiation. (ii) Analysis and Computation Compute the Rayleigh number: g(Ts T ) L3 Ra L (7.2) g gravitational acceleration = 9.81 m/s 2 L plate length = 0.08 m 27 Ra L Rayleigh number at the trailing end x L Ts surface temperature = 70o C T ambient temperature =10o C thermal diffusivity, m 2 /s coefficient of thermal expansion 1 / T f K -1 kinematic viscosity, m 2 /s Properties at T f Ts T (70 10)o C Tf 40o C 2 2 k thermal conductivity = 0.0271W/m o C Pr 0.71 16.96 106 m 2 /s 28 16.96 106 m 2 /s 23.89 106 m 2 /s Pr 0.71 1 40o C 273.13 0.0031934K -1 Substituting into (7.2) Ra L 0.0031934( K 1 )9.81(m/s2 )(70 10)(K)(0.08)3 (m 3 ) 16.96 106 (m 2 /s)23.89 106 (m 2 /s) 2.3752 106 Thus the flow is laminar (1) Axial velocity u: Grx d u 2v x d (7.10) 29 d Fig. 7.2: vs. d Grx η 4 1/ 4 y x (a) Ra L 2.3792 10 6 Grx GrL 3.351 10 6 Pr 0.71 Use (a), evaluate at x 0.08 m and y 0.002 m 3.351 10 η 4 6 1/ 4 0.0032( m ) 1.21 0.08( m ) Fig. 7.2, at 1.21 and Pr = 0.71, gives 30 d x u 0.27 d 2 Grx Solve for u u 2 GrL 0.27 L 0.27 2(16.96 10 6 2 6 )(m /s) 3.351 10 0.2096 m/s 0.08(m) (1) Temperature T: At 1.21 and Pr = 0.71, Fig. 7.3 gives T T 0.43 Ts T T T 0.43(Ts T ) 10(o C) 0.43(70 10)(o C) 35.8o C (3) Velocity B.L. thickness d: 31 At y d , axial velocity u 0, Fig. 7.2 gives GrL η( x , d ) 5 4 Solve for d 1/ 4 d L 4 d 5(0.08)(m ) 6 3.37321 10 1/ 4 0.0132 m 1.32 cm (4) Temperature B.L. thickness d t : At y d t , T T , 0. Fig. 7.3 gives GrL η( x , d t ) 4.5 4 1/ 4 d L 32 Solve for d t d t 4.5(0.08)(m ) 4 6 3.3511 10 1/4 0.0119 m 1.19 cm (5) Local Nusselt number: hx Grx Nux k 4 1/4 d (0) d (7.22) d (0) Table 7.1 gives at Pr = 0.71 d d (0) 0.5018 d Nusselt Number: Use (7.22), evaluate at x = L = 0.08 m 33 NuL hL k GrL 4 1/ 4 6 1 / 4 3.351 10 0.5018 d 4 d ( 0 ) 15.18 (6) Local heat transfer coefficient: at x = L = 0.08 m k 0.0271(W/m o C) h( L) NuL 15.18 5.14 W/m 2 o C L 0.08(m) (7) Heat flux: Newton’s law gives qs h(Ts T ) 5.14( W/m o C)(70 10)( o C) 308.4 W/m 2 (8) Total heat transfer: qT hA(Ts T ) 34 4 k GrL h 3 L 4 h 4 (0.0271)(W/m C) 3.351 10 o 3 0.08(m) 4 1/4 d (0) d 6 1/4 ( 0.5018) 6.86 W/m2 o C qT 6.86(W/m2 o C)0.08(m)0.08(m)(70 10)(o C) 2.63 W (iii) Checking Dimensional check: Units for u, T , d , d t , Nu, h, q and qT are consistent Quantitative check: 35 (i) h is within the range given in Table 1.1 (ii) d d t . This must be the case (5) Comments (i) Magnitudes of u and h are relatively small (ii) h( x ) h ( x ) 7.5 Laminar Free Convection over a Vertical Plate: Uniform Surface Heat Flux • Vertical Plate • Uniform surface heat flux • Infinite fluid at temperature T • Assumptions: Same as Section 7.4 36 • Governing equations: Same as Section 7.4 • Boundary conditions: Replace uniform surface temperature with uniform surface flux T ( x ,0 ) k q s y Surface temperature is variable and unknown: Ts ( x ) Objective: Determine Ts ( x ) and Nu x • Solution: Similarity transformation (Appendix F) • Results: (1) Surface temperature 37 (q s ) Ts ( x ) T 5 x 4 gk 2 (0) = constant, depends on Pr, 4 1/ 5 ( 0) given in Table 7.2 (2) Nusselt number gq s 4 Nu x 2 x 5 k 1/ 5 1 ( 0) (7.28) Correlation equation for (0) [5] 4 9 Pr 10 Pr ( 0) 2 5 Pr 1/2 (7.27) Table 7.2 [4] P 0.1 1.0 ( 0) 10 - 2.7507 - 1.3574 - 0.76746 100 - 0.46566 r 1/ 5 (7.29) 38 Example 7.2: Vertical Plate at Uniform Surface Flux 8cm 8cm vertical plate in air at 10 oC Uniform surface flux = 308.4 oC Determine the following at x 2, 4, 6 and 8 cm (1) Surface temperature (2) Nusselt number (3) Heat transfer coefficient Solution (1) Observations • External free convection • Vertical plate 39 • Uniform surface heat flux • Check Rayleigh number for laminar flow • If laminar: Equation (7.27) gives Ts ( x ) Equation (7.28) gives Nux Nux gives h(x) (2) Problem Definition Determine Ts ( x ) , in free convection Nux and h(x) for uniformly heated vertical plate (3) Solution Plan • Laminar flow? Compute Rayleigh number 40 Use (7.27) for Ts ( x ) Use (7.28) for Nux Nux gives h(x) (4) Plan Execution (i) Assumptions (10) Newtonian fluid (11) Steady state (12) Boussinesq approximations (13) Two-dimensional (14) Laminar flow ( Rax 10 ) 9 (15) Flat plate 41 (16) Uniform surface heat flux (17) No dissipation (18) No radiation (ii) Analysis Rayleigh number: g(Ts T ) L3 Ra L (7.2) Surface temperature: (q s ) Ts ( x ) T 5 x 4 gk 2 4 1/ 5 ( 0) (7.27) Nusselt number: 42 gq s 4 Nu x 2 x 5 k 1/ 5 1 ( 0) (7.28) Heat transfer coefficient k h( x ) Nu x x (a) Determine (0) : Table 7.2 or equation (7.29) 4 9 Pr 10 Pr ( 0) 2 5 Pr 1/ 2 1/ 5 (7.29) (iii) Computations Properties at T f 43 Ts T Tf 2 (b) where Ts ( L) Ts (0) Ts 2 (c) Ts (L) is unknown. Use iterative procedure: (1) Assume Ts (L) (2) Compute T f (3) Find properties at T f (4) Use (7.27) to calculate Ts (L) (5) Compare with assumed value in step (1) (6) Repeat until (1) and (5) agree 44 Assume Ts ( L) 130 C o Ts ( L) Ts (0) (130 10)(o C) Ts 70o C 2 2 Ts T (70 10)o C Tf 40o C 2 2 o Properties of air at 40 C : k 0.0271 W/m o C Pr 0.71 16.96 10 6 m 2 /s 45 16.96 106 m 2 /s 23.89 106 m 2 /s Pr 0.71 1 o 0.0031934 K -1 40 C 273.13 Substitute into (7.2) 0.0031934( K 1 )9.81(m/s 2 )(130 10)(K)(0.08) 3 (m 3 ) Ra L 16.96 10 6 (m 2 /s)23.89 10 6 (m 2 /s) 4.7504 106 • Flow is laminar Use (7.9) to determine ( 0) 46 4 9(0.71)1 / 2 10(0.71) ( 0) 2 5(0.71) 1/ 5 1.4928 Use (7.27) to compute Ts (L) o Ts (L) 10( C) 1/ 5 6 2 4 2 4 4 8 (16.96 10 ) (m /s )(308.4) (W /m ) o 5 (0.1)(m) ( 1 . 4928 ) 63 . 6 C 2 4 4 4 4 0.0031934(1/K)9.81(m/s )(0.0271) (W /m K Computed Ts (L) is lower than assumed value Repeat procedure until assume Ts (L) computedTs (L) Result: Ts ( L) 63.2o C 47 Thus, T f 23.3o C o Properties of air 23.3 C k 0.02601 W/m o C Pr 0.7125 25 15.55 10 6 m2 /s 21.825 10 6 m2 /s 0.003373K -1 (7.29) gives ( 0) (0) 1.4913 (7.27) gives Ts ( x ) 48 Ts ( L) 10( o C ) 6 (15.55 10 ) (m /s )(308.4) (W /m ) 5 2 4 4 4 4 0.003373 (1/K)9.81 (m/s )(0.02601) (W /m K 2 4 2 4 4 8 1/5 (x1)(m) ( 1.4913) (7.28) gives Nux 0.003373(1/K)9.81(m/s )308.4(W/m ) 4 4 Nux (x) (m ) 6 2 o 5(15.55 10 )(m /s)0.02601(W/m C) 2 2 1/ 5 1 1.4913 (e) (a) gives h(x) 49 k 0.02601(W/m o C) h( L) NuL NuL L x (m) (f) Use (d)-(f) to tabulate results at x = 0.02, 0.04, 0.06 and 0.08 m x(m) Ts ( x ) (o C) Nux 0.02 0.04 0.06 0.08 50.3 56.3 60.2 63.2 5.88 10.24 14.16 17.83 h( x )( W/m 2 o C) qs( W/m 2 ) 7.65 6.66 6.14 5.795 308.3 308.4 308.2 308.3 (iii) Checking 50 Dimensional check: Units for Ts , Nu and h are consistent. Quantitative check: (i) h is within the range given in Table 1.1 (ii) Compute q s using Newton’s law gives uniform surface flux (5) Comments (i) Magnitude of h is relatively small (ii) Surface temperature increases with distance along plate 7.6 Inclined Plates Two cases: 51 • • • Hot side is facing downward, Fig. 7.5a Cold side is facing upward, Fig. 7.5b Flow field: Same for both Gravity component = gcos • Solution: Replace g by gcos in solutions of Sections 7.4 and 7.5 • Limitations 60o 7.7 Integral Method 52 • Obtain approximate solutions to free convection problems • Example: Vertical plate at uniform surface temperature 7.7.1 Integral Formulation of Conservation of Momentum • Simplifying assumption ddt valid for Pr 1 (a) Apply momentum theorem in x-direction to the elementd dx 53 Fx M x (out ) M x (in ) Fx : • • • d x M d x d Wall stress Pressure Gravity (b) od d p d ( pd)d d d x d M xd g p d (p (p d d/2 /2 )d )d d d F 7 dM x dp d pd p dd pd pd dx o dx M x dx M x 2 dx dx (c) Simplify d dp o dx dW dM x dx dx (d) Wall stress: 54 o u x ,0 y (e) Weight: • Variable density Integrate weight of element dx dy dW dx d 0 gdy (f) x-momentum: • Constant density Mx d ( x) 0 u2dy (g) Substitute(e), (f) and (g) into (d) 55 d u x ,0 dp d d gdy u2dy y dx 0 dx 0 d (h) Combine pressure and gravity terms (B.L. flow) dp dp g dx dx (i) Rewrite d dp d gd gdy dx 0 (j) d u x ,0 d d 2 g ( )dy u dy y dx 0 0 (k) (j) into (h) Density change: 56 (T T ) (2.28) (2.28) into (k), assume constant d u( x ,0) d d 2 g (T T )dy u dy y dx 0 0 (7.30) NOTE: (1) no shearing force on the slanted surface (2) (7.30) applies to laminar and turbulent flow (3) (7.30) is a first order O.D.E. 7.7.2 Integral Formulation of Conservation of Energy Assume: 57 • • • • No changes in kinetic and potential energy Neglect axial conduction Neglect dissipation Properties are constant T x ,0 d y dx NOTE: d ( x) 0 u(T T )dy (7.31) I n t e g r a l f o r m u l a t i o n o f e n e r g y i s t h e s a m e f o r f r e e c o n v e c t i o n a n d f o r f o r c e d c o n v e c t i o n 7.7.3 Integral Solution 58 • Vertical plate Uniform temperature Ts Quiescent fluid at uniform temperature T Solution Procedure for Forced Convection: (1) Velocity is assumed in terms of d ( x ) 59 (1) Momentum gives d ( x ) (2) Temperature is assumed in terms d t ( x ) (3) Energy gives d t ( x ) Solution Procedure for Free Convection: dd S i n c e w e a s s u m e d t, d e i t h e r m o m e n t u m o r e n e r g y g i v e s t. T o s a t i s f y b o t h , i n t r o d u c e a n o t h e r u n k n o w n i n a s s u m e d v e l o c i t y 60 Assumed Velocity Profile u x , y a 0 ( x ) a 1 ( x ) y a 2 ( x ) y 2 a 3 ( x ) y 3 (a) Boundary conditions: (1) u( x ,0) 0 (2) u( x , d ) 0 (3) (4) u( x , d ) 0 y 2 u( x ,0) y 2 g (Ts T ) Setting y 0 in the x-component, (7.2), to obtain condition (4) 4 boundary conditions give a n 61 (a) gives g(Ts T ) y y2 u d y 1 2 2 2 d d 4 Rewrite as 2 g(Ts T ) 2 y y u d 1 2 d d 4 (b) Introduce a second unknown in (b). Define g(Ts T ) 2 uo ( x ) d 2 4 (c) (b) becomes 62 y y u uo ( x ) 1 d d 2 (7.32) Assumed Temperature Profile T ( x , y ) b0 ( x ) b1 ( x ) y b2 ( x ) y 2 (d) Boundary Conditions: (1) T ( x,0) Ts (2) T ( x , d ) T (3) T ( x , d ) 0 y 3 boundary conditions givebn 63 (d) becomes y T ( x , y ) T (Ts T ) 1 d 2 (7.33) Heat Transfer Coefficient and Nusselt Number T ( x ,0 ) y Ts T k h (7.20) (7.33) into (7.20) h 2k d ( x) (7.34) Local Nusselt number: 64 Nu x hx x 2 k d ( x) (7.35) Determine d ( x ) Solution Use momentum: substitute (7.32) and (7.33) into (7.30) uo d g (Ts T ) d 0 2 y d uo2 1 d dy dx 2 d d 0 4 y y 1 dy d 2 (e) Evaluating the integrals u 1 d 2 1 uo δ βg Ts T δ v o 105 dx 3 δ (7.36) Use energy: substitute(7.32) and (7.33) into (7.31) 65 d uo 2 (Ts T ) (Ts T ) d dx d 1 d ( x) 0 4 y y 1 dy d (f) Evaluating the integrals 1 d uod 1 60 dx d (7.37) The two dependent variables ared ( x ) and uo ( x ) (7.36) and (7.37) are two simultaneous first order O.D.E. Assume a solution of the form uo ( x ) Ax m (7.38) d ( x ) Bx n (7.39) Determine the constants A, B, m and n 66 Substitute (7.38) and (7.39) into (7.36) and (7.37) 2m n 2 2m n1 1 A A Bx g To T Bx n vx m n 105 3 B mn 1 ABx m n1 x n 210 B (7.40) (7.41) T o s a t i s f y ( 7 . 4 0 ) a n d ( 7 . 4 1 ) a t a l l v a l u e s o f x , x t h e e x p o n e n t s o f i n e a c h t e r m m u s t b e i d e n t i c a l (7.40) requires 2m n 1 n m n (g) Similarly, (7.41) requires that m n 1 n (h) 67 Solve (g) and (h) for m and n gives 1 1 m , n 2 4 (i) Introduce (i) into (7.40) and (7.41) 1 2 1 A A B g To T B v 85 3 B (j) 1 1 AB 280 B (k) Solve (j) and (k) for A and B 20 A 5.17 Pr 21 1 / 2 g(Ts T ) 2 1/ 2 (l) and 68 20 B 3.93 Pr -1/2 Pr 21 1/ 4 g(Ts T ) 2 1 / 4 (m) Substitute (i) and (m) into (7.39) d 20 1 3.93 1 x 21 Pr 1/ 4 ( Ra x ) 1 / 4 (7.42) Introduce(7.42) into (7.35) 20 1 Nu x 0.508 1 21 Pr 1 / 4 ( Ra x )1 / 4 (7.43) 7.7.4 Comparison with Exact Solution for Nusselt Number Exact solution: Gr Nu x x 4 1/ 4 d (0) d (7.22) 69 Rewrite above as Grx 4 1 / 4 20 1 Nux 0.508 1 21 Pr 1 / 4 (4 Pr )1 / 4 (7.45) Rewrite integral solution (7.43) as Grx 4 1 / 4 Nu x d (0) d (7.44) Compare right hand side of (7.45) with d (0) / d of exact solution (7.44) Comparison depends on the Prandtl number 70 Table 7.2 gives results Table 7.3 Limiting Cases Pr (1) Pr 0 Nu x exact 0.600 ( PrRa x )1/4 , Pr 0 (7.25a) Nu x integral 0.514( PrRa x )1 / 4 ,Pr 0 (7.46a) (2) Pr Nu x exact 0.503 ( Ra x )1/4 , 0.01 0.03 0.09 0.5 0.72 0.733 1.0 1.5 2.0 3.5 5.0 7.0 10 100 1000 _ d (0) d 0.0806 0.136 0.219 0.442 0.5045 0.508 0.5671 0.6515 0.7165 0.8558 0.954 1.0542 1.1649 2.191 3.9660 Pr Nu x integral 0.508( Ra x )1 / 4 , Pr 20 1 0.508 1 21 Pr 1 / 4 (4 Pr )1/4 0.0725 0.1250 0.2133 0.213 0.4627 0.5361 0.5399 0.6078 0.7031 0.7751 0.9253 1.0285 1.1319 1.2488 1.2665 4.0390 (7.25b) (7.46b) 71 NOTE: (1) Error ranges from 1% for Pr to 14% for Pr 0 (2) We assumed d d t ( Pr 1 ). Solution is reasonable for all Prandtl numbers 72