Fully Developed Flow with Developing Temperature Profile
From ThermalFluidsPedia
(→Uniform Temperature) 
Yuwen Zhang (Talk  contribs) 

Line 82:  Line 82:  
{{EquationRef(9)}}  {{EquationRef(9)}}  
}  }  
  where ''ΔT'' is the difference between the temperature of the fluid at the wall, ''T  +  where ''ΔT'' is the difference between the temperature of the fluid at the wall, ''T<sub>s</sub>'', and at the tube entrance, ''T<sub>0</sub>'', i.e. <math>\Delta T={{T}_{0}}{{T}_{s}}</math>. 
==Uniform Heat Flux==  ==Uniform Heat Flux==  
Line 104:  Line 104:  
{{EquationRef(11)}}  {{EquationRef(11)}}  
}  }  
  
  
  
  
where the centerline symmetric and uniform inlet temperature conditions are the same as eqs. (7) and (8), respectively. However, the boundary condition at the wall is given by <math>\partial \theta /\partial {{r}^{+}}=1</math>.  where the centerline symmetric and uniform inlet temperature conditions are the same as eqs. (7) and (8), respectively. However, the boundary condition at the wall is given by <math>\partial \theta /\partial {{r}^{+}}=1</math>.  
An integral transform technique based on separation of variables was used by Tunc and Bayazitoglu <ref name="TB2001"/> to solve this problem. An appropriate integral transform pair was developed. Under the transformation, the variable ''x<sup>+</sup>'' was eliminated from the partial differential governing equation, which transformed the governing equation into an ordinary differential equation.  An integral transform technique based on separation of variables was used by Tunc and Bayazitoglu <ref name="TB2001"/> to solve this problem. An appropriate integral transform pair was developed. Under the transformation, the variable ''x<sup>+</sup>'' was eliminated from the partial differential governing equation, which transformed the governing equation into an ordinary differential equation.  
  +  [[Image:Fig5.22.pngthumb400 pxalt=Configuration for the slip boundary condition in a microchannel. Configuration for the slip boundary condition in a microchannel.]]  
  +  
  +  
  +  
Jeong and Jeong <ref name="JJ2006">Jeong, H.E., Jeong, J.T., 2006, “Extended Graetz Problem including Streamwise Conduction and Viscous Dissipation in Microchannel,” Int. J. Heat Mass Transfer, Vol. 49, pp. 21512157.</ref> extended the analysis for application to microchannels of rectangular crosssection, including axial conduction and viscous dissipation.  Jeong and Jeong <ref name="JJ2006">Jeong, H.E., Jeong, J.T., 2006, “Extended Graetz Problem including Streamwise Conduction and Viscous Dissipation in Microchannel,” Int. J. Heat Mass Transfer, Vol. 49, pp. 21512157.</ref> extended the analysis for application to microchannels of rectangular crosssection, including axial conduction and viscous dissipation.  
  The configuration for developed flow with developing temperature profile for rectangular microchannels is similar to  +  The configuration for developed flow with developing temperature profile for rectangular microchannels is similar to the figure on the right. The fluid temperature changes from the value ''T<sub>0</sub>'' at the entrance, to the value ''T<sub>s</sub>'' on the walls. The governing energy equation and boundary conditions, including axial conduction and viscous dissipation, for laminar flow are: 
{ class="wikitable" border="0"  { class="wikitable" border="0"  
Line 132:  Line 125:  
    
 width="100%" <center>   width="100%" <center>  
  <math>T={{T}_{0}}\text{ at }x=0</math>  +  <big><big><math>T={{T}_{0}}\text{ at }x=0</math></big></big> 
</center>  </center>  
{{EquationRef(13)}}  {{EquationRef(13)}}  
Line 234:  Line 227:  
<center><math>{{C}_{2}}=\frac{2{{F}_{t}}}{{{F}_{t}}}\frac{2\gamma }{\gamma +1}\frac{\text{Kn}}{\text{Pr}}</math></center>  <center><math>{{C}_{2}}=\frac{2{{F}_{t}}}{{{F}_{t}}}\frac{2\gamma }{\gamma +1}\frac{\text{Kn}}{\text{Pr}}</math></center>  
  +  The effects of the Knudsen number on the Nusselt number variation along a rectangular microchannel neglecting axial conduction and viscous dissipation are studied by Jeong and Jeong<ref name="JJ2006"/>. For Kn = 0, the fully developed Nusselt number is approximately 7.54, which is the result for a pipe of conventional size (classic Graetz problem). The Nusselt number decreases as Kn increases due to the temperature jump at the wall.  
  +  
  +  
  +  
  The effects of the Knudsen number on the Nusselt number variation along a rectangular microchannel neglecting axial conduction and viscous dissipation are  +  
  +  
When the channel is subjected to a constant wall temperature, as <math>{{x}^{+}}\to \infty </math>, the Nusselt number for <math>\text{Br}\ne 0</math> is independent of Br and different from that for <math>\text{Br}=0</math>. The thermally fully developed Nusselt number was obtained from the fully developed temperature profile for constant wall temperature and heat flux by <ref name="JJ2006"/>.  When the channel is subjected to a constant wall temperature, as <math>{{x}^{+}}\to \infty </math>, the Nusselt number for <math>\text{Br}\ne 0</math> is independent of Br and different from that for <math>\text{Br}=0</math>. The thermally fully developed Nusselt number was obtained from the fully developed temperature profile for constant wall temperature and heat flux by <ref name="JJ2006"/>. 
Current revision as of 09:05, 27 July 2010
Convective heat transfer for steady state, laminar, hydrodynamically developed flow and developing temperature profile in microchannels with both uniform temperature and uniform heat flux boundary conditions were solved by Tunc and Bayazitoglu ^{[1]}^{[2]} using the integral transform technique that is presented below.
Uniform Temperature
The energy equation assuming fully developed flow, including viscous dissipation and neglecting axial conduction^{[3]}, is
The boundary and inlet conditions for constant wall temperature are:



The fully developed velocity profile with slip boundary condition is used. The slip boundary condition is also used to express the wall temperature jump. The following nondimensional variables are introduced: for temperature (θ), radial coordinate (r^{+}), axial coordinate (x^{+}), and velocity (u^{+}):

The nondimensional energy equation and boundary conditions are obtained through use of the above variables:




where the Graetz number (Gz) and the Brinkman number (Br) are defined as:

where ΔT is the difference between the temperature of the fluid at the wall, T_{s}, and at the tube entrance, T_{0}, i.e. ΔT = T_{0} − T_{s}.
Uniform Heat Flux
For the case of constant heat flux at the wall, the following nondimensional variables are used:

Upon use of the above nondimensional variables, the nondimensional energy equation for constant wall heat flux can be obtained:

where the centerline symmetric and uniform inlet temperature conditions are the same as eqs. (7) and (8), respectively. However, the boundary condition at the wall is given by .
An integral transform technique based on separation of variables was used by Tunc and Bayazitoglu ^{[1]} to solve this problem. An appropriate integral transform pair was developed. Under the transformation, the variable x^{+} was eliminated from the partial differential governing equation, which transformed the governing equation into an ordinary differential equation.
Jeong and Jeong ^{[4]} extended the analysis for application to microchannels of rectangular crosssection, including axial conduction and viscous dissipation.
The configuration for developed flow with developing temperature profile for rectangular microchannels is similar to the figure on the right. The fluid temperature changes from the value T_{0} at the entrance, to the value T_{s} on the walls. The governing energy equation and boundary conditions, including axial conduction and viscous dissipation, for laminar flow are:

T = T_{0} at x = 0 


where H is half the microchannel height, and the wall length in the xdirection is L. The fully developed velocity profile in the rectangular microchannel is:

which satisfies the slip boundary condition:

Defining the following dimensionless variables:

Equations (16) and (20) are respectively nondimensionalized as:

and

where

The nondimensional boundary conditions are:



where
The effects of the Knudsen number on the Nusselt number variation along a rectangular microchannel neglecting axial conduction and viscous dissipation are studied by Jeong and Jeong^{[4]}. For Kn = 0, the fully developed Nusselt number is approximately 7.54, which is the result for a pipe of conventional size (classic Graetz problem). The Nusselt number decreases as Kn increases due to the temperature jump at the wall.
When the channel is subjected to a constant wall temperature, as , the Nusselt number for is independent of Br and different from that for Br = 0. The thermally fully developed Nusselt number was obtained from the fully developed temperature profile for constant wall temperature and heat flux by ^{[4]}. For constant wall temperature the Nusselt number as () is

And for constant heat flux

where
Unless Br is a large negative number, Nu, is always positive.
References
 ↑ ^{1.0} ^{1.1} Tunc, G., and Bayazitoglu, Y., 2001, “Heat Transfer in Microtubes with Viscous Dissipation,” Int. J. Heat Mass Transfer, Vol. 44, pp. 23952403.
 ↑ Tunc, G., and Bayazitoglu, Y., 2002, “Heat Transfer in Rectangular Microchannels,” Int. J. Heat Mass Transfer, Vol. 45, pp. 765773.
 ↑ Faghri, A., Zhang, Y., and Howell, J. R., 2010, Advanced Heat and Mass Transfer, Global Digital Press, Columbia, MO.
 ↑ ^{4.0} ^{4.1} ^{4.2} Jeong, H.E., Jeong, J.T., 2006, “Extended Graetz Problem including Streamwise Conduction and Viscous Dissipation in Microchannel,” Int. J. Heat Mass Transfer, Vol. 49, pp. 21512157.