Introduction to CFX - dl.ptecgroup.irdl.ptecgroup.ir/.../cfd/ANSYS-CFX/CFX12_10_HeatTransfer.pdf · Heat Transfer 10-16 ANSYS, Inc. Proprietary © 2009 ANSYS, Inc. All rights reserved

Heat Transfer

10-1ANSYS, Inc. Proprietary

© 2009 ANSYS, Inc. All rights reserved.April 28, 2009

Inventory #002598

Training Manual



Inventory #002598

Chapter 10

Heat Transfer

Introduction to CFX

Heat Transfer



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Training ManualGoverning Equations

Continuity

Momentum

Energy

where

Conservation Equations

Heat Transfer



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Training Manual

• Heat transfer in a fluid domain is governed by the Energy

Transport Equation:

• The Heat Transfer Model relates to the above equation as follows

– None: Energy Transport Equation not solved

– Isothermal: The Energy Transport Equation is not solved but a temperature is

required to evaluated fluid properties (e.g. when using an Ideal Gas)

– Thermal Energy: An Energy Transport Equation is solved which neglects variable

density effects. It is suitable for low speed liquid flow with constant specific heats.

An optional viscous dissipation term can be included if viscous heating is significant.

– Total Energy: This models the transport of enthalpy and includes kinetic energy

effects. It should be used for gas flows where the Mach number exceeds 0.2, and

high speed liquid flows where viscous heating effects arise in the boundary layer,

where kinetic energy effects become significant.

SourcesViscous workConvectionTransient Conduction

Governing Equations

Etottot SUThU

t

p

t

h

)()() (

)(

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Training ManualGoverning Equations

• For multicomponent flows, reacting flows and radiation modeling

additional terms are included in the energy equation

• Heat transfer in a solid domain is modeled using the following

conduction equation

SourceTransient Conduction

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Training ManualSelecting a Heat Transfer Model

• The Heat Transfer model is selected

on the Domain > Fluid Models panel

• Enable the Viscous Work term

(Total Energy), or Viscous

Dissipation term (Thermal Energy),

if viscous shear in the fluid is large

(e.g. lubrication or high speed

compressible flows)

• Enable radiation model / submodels

if radiative heat transfer is

significant

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Training Manual

• Radiation effects should be accounted for whenis significant compared to

convective and conductive heat transfer rates

• To account for radiation, Radiative Intensity Transport Equations (RTEs) are solved

– Local absorption by fluid and at boundaries couples these RTEs with the energy equation

• Radiation intensity is directionally and spatially dependent

• Transport mechanisms for radiation intensity:– Local absorption

– Out-scattering (scattering away fromthe direction)

– Local emission

– In-scattering (scattering into the direction)

Radiation

)( 4

min

4

maxrad TTQ

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Training Manual

• Several radiation models are available which provide approximate solutions

to the RTE

• Each radiation model has its assumptions, limitations, and benefits

1) Rosseland Model (Diffusion Approximation Model)

2) P-1 Model (Gibb’s Model/Spherical Harmonics Model)

3) Discrete Transfer Model (DTM) (Shah Model)

4) Monte Carlo Model (not available in the ANSYS CFD-Flo product)

Radiation Models

Heat Transfer



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Training ManualChoosing a Radiation Model

• The optical thickness should be determined before choosing a

radiation model

– Optically thin means that the fluid is transparent to the radiation at

wavelengths where the heat transfer occurs

• The radiation only interacts with the boundaries of the domain

– Optically thick/dense means that the fluid absorbs and re-emits the

radiation

• For optically thick media the P1 model is a good choice

– Many combustion simulations fall into this category since combustion

gases tend to absorb radiation

– The P1 models gives reasonable accuracy without too much

computational effort

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Training ManualChoosing a Radiation Model

• For optically thin media the Monte Carlo or Discrete Transfer models

may be used

– DTM can be less accurate in models with long/thin geometries

– Monte Carlo uses the most computational resources, followed by DTM

– Both models can be used in optically thick media, but the P1 model uses

far less computational resources

• Surface to Surface Model

– Available for Monte Carlo and DTM

– Neglects the influence of the fluid on the radiation field (only boundaries

participate)

– Can significantly reduce the solution time

• Radiation in Solid Domains

– In transparent or semi-transparent solid domains (e.g. glass) only the

Monte Carlo model can be used

– There is no radiation in opaque solid domains

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Training Manual

• Inlet– Static Temperature

– Total Temperature

– Total Enthalpy

• Outlet– No details (except Radiation, see below)

• Opening– Opening Temperature

– Opening Static Temperature

• Wall– Adiabatic

– Fixed Temperature

– Heat Flux

– Heat Transfer Coefficient

• Radiation Quantities– Local Temperature (Inlet/Outlet/Opening)

– External Blackbody Temperature

(Inlet/Outlet/Opening)

– Opaque

• Specify Emissivity and Diffuse Fraction

Heat Transfer Boundary Conditions

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Training ManualDomain Interfaces

• GGI connections are

recommended for Fluid-Solid and

Solid-Solid interfaces

• If radiation is modelled in one

domain and not the other, set

Emissivity and Diffuse Fraction

values on the side which includes

radiation

– Set these on the boundary

condition associated with the

domain interface

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Training ManualThin Wall Modeling

• Using solid domains to model heat transfer through thin solids can present meshing problems

– The thickness of the material must be resolved by the mesh

• Domain interfaces can be used to model a thin material

– Normal conduction only; neglects any in-plane conduction

• Example: to model a baffle with heat transfer through the thickness

– Create a Fluid-Fluid Domain Interface

– On the Additional Interface Models tab set Mass and Momentum to No Slip Wall

• This makes the interface a wall rather than an interface that fluid can pass through

– Enable the Heat Transfer toggle and pick the Thin Material option

• Specify a Material and Thickness

• Other domain interface types (Fluid-Solid etc) can use the Thin Material option to represent coatings etc.

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Training ManualThermal Contact Resistance

• A Thermal Contact Resistance can be

specified using the same approach

as Thin Wall modeling

– Just select the Thermal Contact

Resistance option instead of the Thin

Material option

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Training ManualNatural Convection

• Natural convection occurs

when temperature differences in

the fluid result in density

variations

– This is one-type of buoyancy

driven flow

• Flow is induced by the force of

gravity acting on the density

variations

• As discussed in the Domains lecture, a source term

SM,buoy = ( – ref) g is added to the momentum equations

• The density difference ( – ref) is evaluated using either the Full

Buoyancy model or the Boussinesq model

• Depending on the physics the model is automatically chosen

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Training ManualSolution Notes

• When solving heat transfer

problems, make sure that you have

allowed sufficient solution time for

heat imbalances in all domains to

become very small, particularly

when Solid domains are included

• Sometimes residuals reach the

convergence criteria before global

imbalances trend towards zero

– Create Solver Monitors showing

IMBALANCE levels for fluid and

solid domains

– View the imbalance information

printed at the end of the solver

output file

– Use a Conservation Target when

defining Solver Control in CFX-Pre

Heat Transfer



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Training ManualHeat Transfer Variables

• The results file contains several variables related to heat transfer

– Variables starting with “Wall” are only defined on walls

)( refwallcw TThq

Where Tref is the Wall Adjacent

Temperature or the tbulk for htc

temperature if specified

Twallqw

Mesh

Control Volumes

• Temperature

– This is the local fluid temperature

– When plotted on a wall it is the temperature on the

wall, Twall

• Wall Adjacent Temperature

– This is the average temperature in the control

volume next to the wall

• Wall Heat Transfer Coefficient, hc

– By default this is based on Twall and the Wall

Adjacent Temperature, not the far-field fluid

temperature

– Set the expert parameter “tbulk for htc” to define

a far-field fluid temperature to use instead of the

Wall Adjacent Temperature

– Wall Heat Flux, qw

– This is the total heat flux into the domain by all

modes – convective and radiative (when modeled)

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Training ManualHeat Transfer Variables

• Heat Flux

– This is the total convective heat flux into the domain

• Does not include radiative heat transfer when a radiation model is used

• Convective heat flux contains heat transfer due to both advection and diffusion

– It can be plotted on all boundaries (inlets, outlets, walls etc)

• At an inlet it would represent the energy carried with the incoming fluid relative to the fluid

Reference Temperature (which is a material property, usually 25 C)

• Wall Radiative Heat Flux

– The net radiative energy leaving the boundary (emission minus incoming)

– Heat Flux + Wall Radiative Heat Flux = Wall Heat Flux

– Only applicable when radiation is modeled

• Wall Irradiation Flux

– The incoming radiative flux

– Only applicable when radiation is modeled

Documents

Introduction to CFX - dl.ptecgroup.irdl.ptecgroup.ir/.../cfd/ANSYS-CFX/CFX12_10_HeatTransfer.pdf · Heat Transfer 10-16 ANSYS, Inc. Proprietary © 2009 ANSYS, Inc. All rights reserved