Week 4 - CHT Analysis on Exhaust port

Aim: Steady-state CHT analysis on Exhaust port at an inlet velocity of 5m/sec

Objective: The objectives will mainly focus on

1. Give a brief description of why and where a CHT analysis is used.
2. Maintain the y+ value according to the turbulence model and justify the results.
3. Calculate the wall/surface heat transfer coefficient on the internal solid surface & show the velocity & temperature contours in appropriate areas.
4. How would you verify if the HTC predictions from the simulations are right? On what factors does the accuracy of the prediction depend?

Introduction: Conjugate heat transfer analysis is based on a mathematically structured problem, which describes the heat transfer between a body and a fluid flowing over or inside it as a result of interaction between two objects. At the matching interface, the details are provided for temperature distribution and heat flux along the interface eliminating the need of calculating the heat transfer coefficient. Moreover, the heat transfer coefficient can be calculated later.

One of the simplest ways to realize conjugation is through numerical methods. The boundary condition for the fluid and solid interface is set and solved through iteration methods. There are no right guesses for the values of the initial boundary condition for the convergence except through the hit and trial method.

Application: The conjugate heat transfer methods have become a more powerful tool for modeling and investigating nature phenomena and engineering systems in different areas ranging from aerospace and nuclear reactors to thermal goods treatment and food processing from the complex procedures in medicines to ocean thermal interaction in metrology.

CHT in recent years has significantly improved the cooling performance of electronic equipment such as the design of heat sinks and the design of heat exchangers for the waste treatment plant. One such application of CHT is the exhaust port system.

Solving and modeling approach

• The exhaust port was modeled into the Spaceclaim.
• The exhaust port is a three-dimensional model containing four inlets and one outlet. Despite having isothermal boundary conditions and a uniform flow rate at the four inlets, the model cannot be cut into two halves to save computational time because of its asymmetrical nature. Therefore the whole model is discretized and is considered for meshing.
• CHT analysis requires both the solid and the liquid volume under consideration, Spaceclaim gives an option of volume extract for selecting edges for fluid volume.
• Both the solid volume and liquid volume are copied into one component.
• Share topology is created.
• Spaceclaim gives an option for share coincident topology, when share coincident topology is selected and executed, the mesh from the fluid volume and the solid volume are said to be conformal with each other which is a requirement for CHT analysis.
• The exhaust port is loaded into the meshing window and then simulated for baseline mesh and the refined mesh.
• The named selections are created ( inlet, outlet, outer wall convection)
• The necessary contour images and graphs are studied to understand the behavior of temperature, velocity, and surface heat transfer coefficient at the interface.

Pre-processing and solver setting

Baseline mesh

The geometry is loaded into Spaceclaim

Fluid volume extraction

It is the process of extracting the fluid volume from the solid volume.

Share topology

It is the process of sharing information from fluid volume to solid volume. It plays important criteria in CHT analysis.

Meshing: It is the process of discretizing the geometry into a small number of volumes containing nodes. Since the geometry is complex and the mesh is unstructured therefore the finite volume scheme is used as a discretization scheme.

In this case, the default element size of ANSYS-FLUENT is used (150mm).

Mesh statistics

Number of elements	135747
Number of nodes	27104

Named selection

inlet boundary condition (velocity inlet) @ 5msec

Outlet (Pressure outlet) Gauge pressure 0Pa

Outer wall convection (Heat transfer coefficient 20 W/m^2K free stream temperature 300K

The flanges around the inlet and the component encompassing the outlet are adiabatic (no heat transfer takes place through these walls).

Setting up of physics and boundary conditions

The geometry orientation in the setup window. The blue-coloured lines are inlet, and the red-coloured lines are outlet.

Set up

The different boundary conditions are listed below

Inlet boundary condition

1. Type: Velocity inlet
2. Velocity magnitude : 5m/sec
3. Temperature: 700K

Outlet boundary condition

1. Type: Pressure outlet
2. Gauge pressure: 0Pa

Outer wall convection

1. Type: wall
2. Thermal condition: convection
3. Heat transfer coefficient: 20W/m^2K

The rest boundary condition values are set up as default values in ANSYS-FLUENT.

• Energy equation: It is turned on.
• Viscous model: It is set to k−epsilon

Material properties

Fluid

• Material Name: Air
• Density: 1.225kg/m^3
• Specific heat: 1006.43J/kgK
• Thermal conductivity: 0.0242W/mK
• Viscosity: 1.7894e−05kg/m−sec

Solid

• Material Name: Aluminium
• Specific heat: 871J/kgK
• Thermal conductivity: 202.4W/mK

SIMPLE METHOD

Residual plot

Surface heat transfer coefficient

Surface heat transfer coefficient value: -18.7213 W /m2K

CHT analysis of exhaust port with finer mesh

First refinement

Element size: 90mm

Since the value of the heat transfer coefficient takes the value of the first cell near the wall, so it can be inferred that the Y+ value will be in the viscous sub-layer which is taken to be 1.

Steps involved in calculating the first cell height.

Reynolds number= ρ∗v∗L/μ

=1.225∗5∗0.17/1.7894e−05

=58189.8960

The characteristics length is taken as the inlet dia.

Skin friction coefficient, Cf=0.058/Re^0.2

=0.00646

Wall shear stress formula, τw=0.5∗Cf∗ρ∗v^2

=0.5∗1.225∗25∗0.00646

=0.0989 Pa

Frictional velocity formula, uτ=(τw/ρ)^0.5

=0.2841msec

Now, Y+=△y∗uτ∗ρ/μ

Since Y+=1

Therefore △y=μuτ∗ρ

=0.0000514162m

=0.05141621mm

Inflation

Number of inflation layer:5

Growth rate: 1.2

Inflation option: total thickness

max thickness: =5 mm

Captured curvature is set to yes.

Residual plot

Surface heat transfer coefficient

Mesh statistics and surface heat transfer coefficient

Element size	90mm
Number of elements	241525
Number of nodes	85789
Y+	1
Heat transfer coefficient	-6.3125/m^2K

Second refinement

Element size: 80mm

Residual plot

Surface heat transfer coefficient

Mesh statistics and surface heat transfer coefficient

Element size	80mm
Number of elements	241524
Number of nodes	85784
Y+	1
Heat transfer coefficient	-6.2818W/m^2K

Final refinement

Element size: 70mm

Number of inflation layer: 5

Growth rate: 1.2

Residual plot

Surface heat transfer coefficient

Mesh statistics and surface heat transfer coefficient

Element size	70mm
Number of elements	241524
Number of nodes	85784
Y+	1
First cell height	0.05141621mm
Heat transfer coefficient	-6.251854 W/m^2K

Comparison of all cases

Element size	Number of elements	Number of nodes	First cell height	Y+	Inflation layer	Surface heat transfer coefficient.(Numerical value)
0.15m	135747	27104	N/A	N/A	N/A	-18.7213W/m^2K
0.09m	241525	85789	0.0000514162m	1	5	-6.3125W/m^2K
0.08m	241524	85784			5	-6.281W/m^2K
0.07m	241524	85784			5	-6.2578W/m^2K

Results

The temperature along plane-1 located at the exhaust section of the port.

The velocity along plane-1 located at the exhaust section of the port.

Temperature at outer convection wall.

Streamline representation of velocity

Surface heat transfer coefficient

Conclusion

• The CHT analysis on the exhaust port was simulated successfully on ANSYS-FLUENT.
• The pressure-based solver is used to discretize the whole geometry.
• Mesh refinement will cause the reduction of heat transfer coefficients.