Heat transfer in microchannels
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Heat Transfer in Microchannels. Applications. Cooling of microelectronics. Inkjet printer. 11.1 Introduction:. Medical research. Micro-electro-mechanical systems (MEMS): Micro heat exchangers, mixers, pumps, turbines, sensors and actuators.

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Heat transfer in microchannels

Heat Transfer in Microchannels


Cooling of microelectronics

Inkjet printer

11.1 Introduction:

Medical research

  • Micro-electro-mechanical systems (MEMS): Micro heat exchangers, mixers, pumps, turbines, sensors and actuators

11.1.1 Continuum and Thermodynamic Equilibrium Hypothesis

Properties: (pressure, temperature, density, etc) are macroscopic manifestation of molecular activity

Continuum:material having sufficiently large number of molecules in a given volume to give unique values for properties

Validity of continuum assumption: the molecular-mean-free path, , is small relative to the characteristic dimension of the system

Mean-free-path: average distance traveled by molecules before colliding

(1.2) Hypothesis

= characteristic length



Knudson number Kn:

Gases: the criterion for the validity of the continuum assumption is:

Thermodynamic equilibrium: depends on collisions frequency of molecules. The condition for thermodynamic equilibrium is:

Microchannels: Hypothesis Channels where the continuum assumptionand/or thermodynamic equilibrium break down

(11.1) Hypothesis

9.1.2. Surface Forces. Examine ratio of surface to volume for tube:

  • For D = 1 m, A/V = 4 (1/m)

  • For D = 1 μm, A/V = 4 x 10 6 (1/m)

  • Consequence:

  • Surface forces may alter the nature of surface boundary conditions

(2) For gas flow, increased pressure drop results in large density changes. Compressibility becomes important

(11.2) Hypothesis

9.1.3 Chapter Scope

  • Classification

  • Gases vs. liquids

  • Surface boundary conditions

  • Heat transfer in Couette flow

  • Heat transfer in Poiseuille flow

9.2 Basic Consideration

9.2.1 Mean Free Path. For gases:


Kn increases

is very small, expressed in terms of the micrometer,

p = pressure

R = gas constant

T = temperature

μ = viscosity


(6.57) Hypothesis



11.2.2 Why Microchannels?

Nusselt number: fully developed flow through tubes at uniformsurface temperature


Water cooled microchips

(11.4) Hypothesis

11.2.3 Classification

Based on the Knudsen number:

Four important factors:

(1) Continuum

(2) Thermodynamic equilibrium

(3) Velocity slip

(4) Temperature jump

(1) HypothesisKn < 0.001: Macro-scale regime (previous chapters):

Continuum: valid

Thermodynamic equilibrium: valid

No velocity slip

No temperature jump

(2) 0.001<Kn < 0.1: Slip flow regime:

Continuum: valid

Thermodynamic equilibrium: fails

  • Velocity slip

  • Temperature jump

Continuity, Navier-Stokes equations, and energy equations are validNo-velocity slip and No-temperature jump conditions, conditions failReformulate boundary conditions

(3) Hypothesis 0.1< Kn<10: Transition flow:

Continuity and thermodynamic equilibrium fail Reformulate governing equations and boundary conditions Analysis by statistical methods

(4) Kn>10: Free molecular flow: analysis by kinetic theory of gases

11.2.4 Macro and Microchannels

Macrochannels: Continuum domain, no velocity slip, no temperature jump

Microchannels: Temperature jump and velocity slip, with or without failure of continuum assumption

Distinguishing factors: Hypothesis

(1) Two and three dimensional effects

(2) Axial conduction

(3) Viscous dissipation

(4) Compressibility

(5) Temperature dependent properties

(6) Slip velocity and temperature

(7) Dominant role of surface forces

(1) HypothesisMean free path:

11.2.5 Gases vs. Liquids

Macro convection:

  • No distinction between gases and liquids

  • Solutions for both are the same for the same geometry, governing parameters (Re, Pr, Gr,…) and boundary conditions

Micro convection:

  • Flow and heat transfer of gases differ from liquids

Gas and liquid characteristics:

  • Continuum assumption may hold for liquids but fail for gases

(2) Knudsen number: used as criterion for thermodynamic equilibrium and continuum for gases but not for liquids

(3) Onset of failure of thermodynamic equilibrium and continuum: not well defined for liquids

(4) Surface forces: liquid forces are different from gas forces

(5) Boundary conditions: differ for liquids from gases

(6) Compressibility: liquids are almost incompressible while gases are not

(7) Flow physics: liquid flow is not well known. Gas flow is well known

(8) HypothesisAnalysis: more complex for liquids than gases

11.3 General Features

  • Flow and heat transfer phenomena change as channel size is reduced:

Rarefaction: Knudsen number effect

Compressibility: Effect of density change due to pressure drop along channel

Viscous dissipation: Effect of large velocity gradient

Examine: Effect of channel size on:

  • Velocity profile

  • Flow rate

  • Transition Reynolds number

  • Nusselt number


Fully developed microchannel gas flow as the Knudsen number increases from the continuum through the slip flow domain

(11.5) Hypothesis

  • Define friction coefficient


11.3.1 Flow Rate

Slip flow: increased velocity and flow rate

e = determined experimentally

t = from macrochannel theory or correlation equations

11.3.2 Friction Factor f

= wall shear stress Hypothesis

= mean velocity


= pressure drop

  • Fully developed flow through channels: define friction factor f

D = diameter

L = length

(11.7) Hypothesis

Microchannels: compare experimental data,

, with

theoretical value,

, (macroscopic, continuum)

Macrochannels: fully developed laminar flow:

(1) f is independent of surface roughness

(2) Product of f and Reynolds number is constant for each channel geometry:

Po = Poiseuille number

(3) Po is independent of Reynolds number

(11.8) Hypothesis


departs from unity:


(2) Unlike macrochannels, Po for fully developed flow depends on the Re

(3) Conflicting findings due to: difficulties in measurements of channel size, surface roughness, pressure distribution, uncertainties in entrance effects, transition, and determination of properties

(6.1) Hypothesis

Factors affecting the determination of

11.3.3 Transition to turbulent flow

Macrochannels: smooth macrotubes

Microchannels: reported transition

  • Variation of fluid properties

  • Measurements accuracy

  • Surface roughness

(11.9) Hypothesis

11.3.4 Nusselt number. For fully developed conditions:

Macrochannel: Nusselt number is constant

Microchannels: In general, Nusselt number is not well established:

  • Nu varies along microchannels

  • Nu depends on:

  • Surface roughness

  • Reynolds number

  • Nature of gas

  • Widely different reported results:

= experimental Hypothesis

= macrochannel theory

Factors affecting the determination of


  • Variation of fluid properties

  • Measurements accuracy

Slip flow regime: Hypothesis

M =

11.4 Governing Equations

Factors to be considered:

  • Compressibility

  • Axial conduction

  • Dissipation

11.4.1 Compressibility: Expressed in terms of Mach number

(6.30) Hypothesis


  • Incompressible flow, M < 1

  • Linear pressure drop


  • Compressible flow

  • Non-linear pressure drop

  • Decrease in Nusselt number

11.4.2 Axial Conduction

Macrochannels: neglect axial conduction for

(11.10) Hypothesis

Pe = Peclet number

Microchannels: low Peclet numbers, axial conduction may be important, it increases the Nusselt number

11.4.3 Dissipation

Microchannels: large velocity gradient, dissipation may become important

11.5 Slip Velocity and Temperature Jump Boundary Conditions

Slip velocity for gases:

= fluid axial velocity at surface Hypothesis

surface axial velocity

= tangential momentum accommodating coefficient


= surface temperature

x = axial coordinate

n = normal coordinate measured from the surface

Temperature jump for gases

T(x,0) = fluid temperature at the boundary

, specific heat ratio Hypothesis

= energy accommodating coefficient


(1) Eq. (11.10) and (11.11) are valid for gases

(2) Eq. (11.10) and (11.11) are valid forKn < 0.1

(3) σu and σT, are:

  • Empirical factors

  • They depend on the gas, geometry and surface

  • Values range from zero (perfectly smooth) to unity

  • Values for various gases are approximately unity

11.4. 8 Analytic Solutions: Slip Flows Hypothesis

Two common flow types, extensive use in MEMS:

(1) Couette flow (shear driven): fluid is set in motion by a moving surface


(2) HypothesisPoiseuille flow (pressure driven): fluid is set in motion by an axial pressure gradient


Micro heat exchangers, mixers, microelectronic heat sinks


  • No pressure drop in Couette flow

  • Signifiant pressure drop in Poiseuille flow

Boundary conditions: two types:

(1) Uniform surface temperature

(2) Uniform surface heat flux

11.6.1 Assumptions Hypothesis

(1) Steady state

(2) Laminar Flow

(3) Two-dimensional

(4) Slip flow regime (0.001 < Kn < 0.1)

(5) Ideal gas

(6) Constant viscosity, conductivity and specific heats

(7) Negligible lateral variation of density and pressure

(8) Negligible dissipation (unless otherwise stated)

(9) Negligible gravity

(10) The accommodation coefficients are equal to unity, Hypothesis

11.6.2 Couette Flow with Viscous Dissipation:

Parallel Plates with Surface Convection

  • Infinitely large parallel plates

  • Gas fills gap between plates

  • Upper plate: moves with velocity us

  • Lower plate: stationary, insulated

  • Convection at the upper plate

  • Consider dissipation and slip conditions

(11.12) Hypothesis


(1) Velocity distribution

(2) Mass flow rate

(3) Nusselt number

Find flow field and temperature distribution

Flow Field

  • Normal velocity and all axial derivatives vanish

  • Axial component of the Navier-Stokes equations, (2.9), simplifies to

Boundary conditions: Hypothesis use (11.10), Set

  • Lower plate: n = y = 0 and

(11.10) gives




  • Upper plate: n = H – y, (9.10) gives


(11.13) Hypothesis

Kn is the local Knudsen number


(1) Fluid velocity at the moving plate: set y = H in (11.14)

Effect of slip:

  • Decrease fluid velocity at the moving plate

  • Increase fluid velocity at the stationary plate

(k) Hypothesis


(2) Velocity distribution is linear

(3) Setting Kn = 0 in (11.14) gives the no-slip solution

Mass Flow Rate m

W = channel width

Neglect variation of ρ along y, (11.14) into (11.15)

(11.16) Hypothesis



  • Flow rate is independent of the Knudsen number

  • Compare with macrochannel flow rate mo

(k) into (11.15)

This is identical to (11.16), thus

(l) Hypothesis

Nusselt Number

  • Equivalent diameter for parallel plates,De = 2H

  • Nusselt number

Heat transfer coefficient h:

(11.19) Hypothesis

k = conductivity of fluid

T = fluid temperature

Ts = plate temperature


(1) Fluid temperature at the moving plate, T (x,H), is not equal to surface temperature

(2) h is defined in terms of surface temperature Ts

(11.20) Hypothesis


(3) Use temperature jump, (11.11), to determine Ts

(4) For the upper plate, n =H – y, eq. (11.11) gives

  • Mean temperature Tm: defined in Section 6.6.2

  • Neglect variation of cp and ρ along y, use (11.14) . for u and (11.15) for m

(11.22) Hypothesis


Determine temperature distribution:

  • Use energy equation, (2.15)

  • Apply above assumptions, note that axial derivatives vanish, (2.15) gives

(2.17) gives the dissipation function Hypothesis

which simplifies to




(9.24) into (9.23)

Boundary conditions

Lower plate:

(n) Hypothesis


Upper plate:

Use (920) to eliminate Ts

Use velocity solution (9.14), solve for T

(p) Hypothesis




Velocity solution (11.14), temperature solution (11.26) giveTs , Tm and Nu

(11.27) Hypothesis

Note the following regarding the Nusselt number

(1) It is independent of Biot number

(2) It is independent of the Reynolds number

(3) Unlike macrochannels, it depends on the fluid

(4) First two terms in the denominator of (11.27) represent rarefaction (Knudsen number). The second term represents effect of temperature jump

(11.28) Hypothesis


(5) Nusselt number for macrochannels, Nuo: set Kn = 0 in (11.27):

Ratio of (11.27) and (11.28)

NOTE: Ratio is less than unity

11.6.3 Fully Developed Poiseuille Channel Flow: Uniform Surface Flux

  • Pressure driven flow between parallel plates

  • Fully developed velocity and temperature

  • Inlet and outlet pressures are pi and po


(1) Velocity distribution

(2) Pressure distribution

(3) Mass flow rate

(4) Nusselt number

Note: Hypothesis

(3) Invariant axial velocity

(4) Linear axial pressure

Major difference between macro and micro fully developedslip flow:

Macrochannels: incompressible flow

(1) Parallel streamlines

(2) Zero lateral velocity component (v = 0)

density changes Hypothesis

  • (2) Large axial pressure drop

compressible flow

(3) Rarefaction: pressure decreases


Kn increases with x

Microchannels: compressibility and rarefaction change above flow pattern:

  • (1) None of above conditions hold

  • (4) Axial velocity varies with axial distance

(5) Lateral velocity v does not vanish

  • (6) Streamlines are not parallel

(7) Pressure gradient is not constant

(3) Hypothesis



(1) Steady state

(2) Laminar flow

(4) Two-dimensional

(5) Slip flow regime (0.001 < Kn < 0.1)

(6) Ideal gas

(7) Constant viscosity, conductivity and specific heats

(8) Negligible lateral variation of density and pressure

(12) Negligible inertia forces: Hypothesis

= 0

(13) The dominant viscous force is


(10) Negligible dissipation

Flow Field

Additional assumptions:

(11) Isothermal flow

Navier-Stokes equations (2.9) simplify to:

(e) Hypothesis



Boundary conditions:

Symmetry at y = 0

For the upper plate, n = H – y

Solution to u

(11.33) Hypothesis


For an ideal gas

Pressure Distribution p:

To determine p(x), must determine vertical component v: start with continuity (2.2a)

Apply above assumptions

(h) Hypothesis



Use ideal gas to eliminate ρ:

(11.31) into (h), assuming constant temperature

(11.30) into (i)

(j) Hypothesis




Boundary conditions:

Multiply (j) by dy, integrate and using (k)

(11.32) Hypothesis



Evaluate the integrals

Determination of p(x): Apply boundary condition (l) to (11.32)

Express Kn in terms of pressure. Equations (11.2) and (11.13) give

(o) Hypothesis


Evaluate (n) at y = H/2, substitute (11.33) into (n) and integrate

Integrate again (T is assumed constant)

Solve for p

(q) Hypothesis


Pressure boundary conditions

Apply (q) to (p)

Substitute into (p) and normalize by po

(r) Hypothesis



Introduce outlet Knudsen number Knousing (11.2) and (11.13)

Substitute (11.34) into (r)

(11.36) Hypothesis


(1) Unlike macrochannel Poiseuille flow, pressure variation along the channel is non-linear

(2) Knudsen number terms represent rarefaction effect

(3) The terms (pi/po)2 and [1- (pi/po)2](x/L) represent the effect of compressibility

(4) Application of (11.35) to the limiting case of Kno =0 gives

This result represents the effect of compressibility alone

(s) Hypothesis



Mass Flow Rate

W = channel width

(11.30) in (s)

Density ρ :

(11.33) Hypothesis



(11.33) gives Kn(p)

(11.33) and (11.37) in (t)

(11.35) into (11.38) and let T=To

(11.40) Hypothesis


Compare with no-slip, incompressible macrochannel case:

Taking the ratio


(1) Microchannels flow rate is very sensitive to H

(2) (11.39) shows effect of rarefaction (slip) and compressibility on m

(11.41) shows that neglecting Hypothesis

(3) Since

compressibility and rarefaction underestimates m


For uniform surface flux


Nusselt Number

Substitute into (g)

(11.42) Hypothesis


Plate temperature Ts: use (11.11)

Mean temperatureTm:

Needu(x,y) and T(x,y)

Velocity distribution: (11.30) givesu(x,y)for isothermal flow

(15) No dissipation, Hypothesis

(16) No axial conduction,

(18) Nearly parallel flow,


Additional assumption:

(14) Isothermal axial velocity solution is applicable

(17) Negligible effect of compressibility on the energy equation

Energy equation: equation (2.15) simplifies to

(w) Hypothesis



Boundary conditions:

To solve (11.44), assume:

(19) Fully developed temperature

Solution:T(x,y) and Tm(x): Define

Fully developed temperature: Hypothesis

is independent of x




(11.45) and (11.46) give

(11.48) Hypothesis



Expanding and use (11.45)


Heat transfer coefficient h:

(z) Hypothesis


(11.42) gives Ts(x). (11.45) gives temperature gradient in (y)


(z) into (y), use (11.42) forTs(x)

(11.50) Hypothesis

Newton’s law of cooling:

Equate with (11.49)


Combine this with (11.48)

(11.51) Hypothesis

(11.51) replaces


in (11.44)




Conservation of energy for element:

= constant Hypothesis



Conservation of energy for element:



(bb) into (aa)

= constant Hypothesis




(11.52) into (11.51)

(11.53) into (11.44)

(cc) Hypothesis


Mean velocity:

(11.30) gives velocity u. (11.30) into (cc)


(11.56) Hypothesis



Combining (11.30) and (11.55)

(11.56) into (11.54)

Integrate twice

(11.58) Hypothesis

f(x) and g(x) are “constants” of integration

Boundary condition (w) gives

Solution (dd) becomes


  • Boundary condition (x) is automatically satisfied

(2) g(x) is determine by formulating Tm using two methods

(11.59) Hypothesis


Method 1: Integrate (11.52)


Evaluate the integrals

(11.61) Hypothesis


Method 2: Use definition of Tm. Substitute (11.30) and(11.58) into (11.43)

Evaluate the integrals

Equating (11.60) and (11.61) gives g(x)

(11.63) Hypothesis



(11.58) into (11.42) gives Ts

The Nusselt number is given in (v)

(11.61) and (11.63) into (v)

(11.65) Hypothesis


(1) Kn in (11.64) depends of local pressurep

(2) Pressure varies with x, Kn varies with x

(3) Unlike macrochannels, Nu is not constant

(4) Unlike macrochannels, Nu depends on the fluid

  • No-slip Nu for macrochannel flow, Nuo: set Kn = 0 in (11.64)

This agrees with Table 6.2 Hypothesis

(6) Rarefaction and compressibility decrease the Nusselt number

11.6.4 Fully Developed Poiseuille Channel Hypothesis Flow: Uniform Surface Temperature






Repeat Section 11.6.3 with plates at uniform surfacetemperature Ts

  • Flow field: same for both cases:

  • Energy equation: (11.44) is modified to include axial conduction

(11.66a) Hypothesis

Solve the Graetz channel entrance problem and set

to obtain the fully developed solution

  • Boundary conditions: different for the two cases

Nusselt number:

Need T(x,y) and Tm(x)

Solution approach:

(7.50) Hypothesis

Small Reynolds

Small Peclet number


conduction is important


Axial conduction: can be neglected for:


Include axial conduction: modify energy equation (11.44)

(11.68a) Hypothesis




Boundary and inlet conditions:

(11.56) Hypothesis

  • Specialize to fully developed: set

Axial velocity


  • Use method of separation of variables

Result: Fig. 11.11 shows Nu vs. Kn

(4) Limiting case: no-slip ( HypothesisKn = 0) and no axial conduction



Heat Transfer Rate,



(1) Nu decreases as the Kn is increased

(2) No-slip solution overestimates microchannels Nu

(3) Axial conduction increases Nu

This agrees with Table 6.2

Following Section 6.5

(6.14) Hypothesis


is determine numerically using (6.12)


Tm(x) is given by

11.6.5 Fully Developed Poiseuille Flow in Hypothesis Micro Tubes: Uniform Surface Flux


  • Poiseuille flow in micro tube

  • Uniform surface flux

  • Fully developed velocity and temperature

  • Inlet and outlet pressures are pi and po

Determine Hypothesis

(1) Velocity distribution

(2) Nusselt number

  • Rarefaction and compressibility affect flow and heat transfer

  • Velocity slip and temperature jump

  • Axial velocity variation

  • Lateral velocity component

  • Non-parallel stream lines

  • Non-linear pressure

(a) Hypothesis

= axial velocity


Apply the 19 assumptions of Poiseuille flow between parallel plates (Sections 11.6.3)

Flow Field

  • Follow analysis of Section 11.6.3

  • Axial component of Navier-Stokes equations in cylindrical coordinates:

(b) Hypothesis



Boundary conditions:

Assume symmetry and set σu= 1


(11.75) Hypothesis


Knudsen number

Mean velocity vzm

Use (11.74), integrate

(11.77) Hypothesis



(11.74) and (11.76)

Solution to axial pressure

(11.76) and (11.78) give m

(11.79b) Hypothesis


For incompressible no-slip (macroscopic)

Nusselt Number

  • Follow Section 11.6.3

Heat transfer coefficient h:

(e) Hypothesis



Substituting into (d)

Ts = tube surface temperature, obtained from temperaturejump condition (11.11)

Mean temperature:

(11.81) Hypothesis



Energy equation:

Boundary conditions:


(11.82) Hypothesis



Fully developed temperature:


(11.82) and (11.84) give

(11.85) Hypothesis



Expand (11.82)


Heat transfer coefficient h,:

Differentiate and evaluating at Hypothesis



Rewrite (11.81)

(j) into (i)

(11.86) Hypothesis

Newton’s law of cooling h

Equate with (k)


(11.87) Hypothesis

Will use (11.87) to replace

in (11.81) with

Combine with (11.85)

Conservation of energy to dx

(l) Hypothesis






(m) into (l)

(11.88) into (11.87)

(11.90) Hypothesis

(11.77) is used to eliminate

in the above



(11.89) into (11.81)


(11.92) Hypothesis

Condition (g) gives

Solution (n) becomes

Condition (h) is automatically satisfied

Determine g(z): Use two methods to determine Tm

Method 1: Integrate (11.88)

(11.93) Hypothesis



Evaluate the integral

Method 2: Use definition ofTm in (11.80). Substitute (11.74)and (11.92) into (11.80)

(11.95) Hypothesis



Equate (11.94) and (11.95), solve for g(z)

Use (f) and (11.92) to determine Hypothesis



Nusselt number: (11.95) and (11.97) into (e)

(11.99) Hypothesis

Results: Fig. 11.14

  • Fig. 11.14 gives Nu vs. Kn for air

  • Rarefaction and compressibility decrease the Nusselt number

  • Nusselt number depends on the fluid

  • Nu varies with distance along channel

  • No-slip Nusselt number,Nuo,is obtained by setting Kn = 0 in (11.97)

This agrees with (6.55) for macro tubes Hypothesis

11.9.6 Fully Developed Poiseuille Flow in Micro Tubes: Uniform Surface Temperature

  • Repeat Section 11.6.5 with the tube at surface temperatureTs

  • Apply same assumptions

  • Boundary conditions are different

  • Flow field solution is identical for the two cases

(11.100a) Hypothesis

Nusselt number:

  • DetermineT(r,z) and Tm(z)

  • Follow the analysis of Section 11.6.4

  • Solution is based on the limiting case of Graetz tube entrance problem

  • Axial conduction is taken into consideration

  • Energy equation (11.81) is modified to include axial conduction:

(11.102a) Hypothesis





Boundary and inlet conditions

(11.76) Hypothesis

  • Neglecting axial conduction: set

(11.76) gives axial velocity

  • Solution by the method of separation of variables

  • Solution is specialized for fully developed conditions at large z

  • Result for air shown in Fig. 11.16

  • Axial conduction increases the Nu


This agrees with (6.59)

  • Limiting case: no slip with axial conduction:at Kn =0and Pe = 0: