The aim of this test case is to validate the calculation of following flow quantities:

Velocity

Pressure drop

using incompressible steady-state turbulent models applied to water flow through a straight pipe.

Two turbulence models were used: the k−ϵ

$k-\u03f5$

and the k−ωSST

$k-\omega \text{}SST$

. Simulation results from SimScale were compared to the analytical results [1]. The mesh was generated on the SimScale platform using the Hex-dominant parametric type of meshing operation.

A straight cylindrical pipe was chosen as the flow domain (see Fig.1.). Faces A, B and C represent the inlet, wall and outlet patches, respectively.

Length [m]

Diameter [m]

1

0.01

Analysis type and Domain

In this study the focus was on two turbulence models: the k−ϵ

$k-\u03f5$

model and the k−ωSST

$k-\omega \text{}SST$

. These models fall under the category of Reynolds Averaged Navier-Stokes (RANS) method of turbulence modeling.

A typical property to assess the mesh quality in regards to the near-wall modeling in turbulent simulations is the y+

${y}^{+}$

(“y-plus”) value, which is defined as the non-dimensional distance to the wall; it is given by y+=u∗yν

${y}^{+}=\frac{{u}^{\ast}y}{\nu}$

. A y+

${y}^{+}$

value of 1 would correspond to the upper limit of the laminar sub-layer.

There are two ways of modeling the physics of near-wall flow in RANS models:

“Full resolution” of the near-wall region: This approach explicitly models the boundary layer all the way down to the laminar sub-layer. It requires the first cell center to be placed at most at the top of the laminar sub-layer, where y+≈1 ${y}^{+}\approx 1$

. This procedure demands computational grid resolution in to be very fine. Boundary conditions for this approach are given in Table 2.

Use of wall-functions to resolve the near-wall region: This approach allows for the center of the first cell next to the wall boundary to be placed in the range: 30⩽y+⩽300 $30\u2a7d{y}^{+}\u2a7d300$

. Boundary conditions for this approach are given in Table 1.

In this validation project both approaches are investigated – wall functions for both k−ωSST

$k-\omega \text{}SST$

and k−ϵ

$k-\u03f5$

turbulence models; and full boundary layer resolution for k−ωSST

$k-\omega \text{}SST$

model.

Uniformly-spaced hexahedral meshes were generated on the SimScale platform, using the hex-dominant parametric meshing operation (see Fig.2.). For the “wall function” approach, the aimed first cell layer thickness was around 1mm

$1\text{}mm$

, with the intention of y+

${y}^{+}$

being ≈30

$\approx 30$

. For the “Full resolution” case, the aimed first cell layer thickness was 0.041mm

$0.041\text{}mm$

, with the intention of achieving y+≈1

${y}^{+}\approx 1$

.

Tool Type : OPENFOAM®

Analysis Type : Incompressible Steady-state (Turbulent)

Turbulence Models : k−ϵ

$k-\u03f5$

/ k−ωSST

$k-\omega \text{}SST$

Mesh and Element types :

Mesh type

Cells in x

Cells in y

Cells in z

Total number of cells

Refinements

hex-dominant parametric

19

500

19

179092

Inflate boundary layer

hex-dominant parametric

20

1000

20

451360

Inflate boundary layer

Fig.2. Meshes used for the Turbulent Pipe Flow validation: left is used for wall function (y+≈30

Boundary conditions are given in the Tables 1. and 2. below:

Table 1. Boundary Conditions for the “Wall function approach”:

Type

u[m/s]$u[m/s]$

p[m2s−2]$p[{m}^{2}{s}^{-2}]$

k[m2s−2]$k[{m}^{2}{s}^{-2}]$

epsilon[m2s−3]$epsilon[{m}^{2}{s}^{-3}]$

omega[s−1]$omega[{s}^{-1}]$

Inlet

1$1$

Zero Gradient

3.84×10−3$3.84\times {10}^{-3}$

0.03059×10−3$0.03059\times {10}^{-3}$

88.525$88.525$

Wall

0$0$

Zero Gradient

Wall Function

Wall Function

Wall Function

Outlet

Zero Gradient

0$0$

Zero Gradient

Zero Gradient

Zero Gradient

Table 2. Boundary Conditions for the “Full resolution approach”:

Type

u[m/s]$u[m/s]$

p[m2s−2]$p[{m}^{2}{s}^{-2}]$

k[m2s−2]$k[{m}^{2}{s}^{-2}]$

omega[s−1]$omega[{s}^{-1}]$

Inlet

1$1$

Zero Gradient

3.84×10−3$3.84\times {10}^{-3}$

88.525$88.525$

Wall

0$0$

Zero Gradient

0

Wall Function

Outlet

Zero Gradient

0$0$

Zero Gradient

Zero Gradient

where k

$k$

represents the turbulence kinetic energy. It is calculated as:

k=32(uavgI)2

$$k=\frac{3}{2}({u}_{avg}I{)}^{2}$$

where uavg

${u}_{avg}$

is the average velocity in the pipe cross-section and I

$I$

is the turbulence intensity, which can be calculated for fully developed pipe flow as:

I=0.16Re−18

$$I=0.16R{e}^{\frac{-1}{8}}$$

Having calculated k

$k$

, the turbulent dissipation rate ϵ

$\u03f5$

is calculated as:

ϵ=Cμk32l

$$\u03f5={C}_{\mu}\frac{{k}^{\frac{3}{2}}}{l}$$

where Cμ=0.09

${C}_{\mu}=0.09$

is an empirical constant specified in the turbulence model.

Specific turbulent dissipation rate ω

$\omega $

is calculated as:

ω=k−−√l

$$\omega =\frac{\sqrt{k}}{l}$$

In both expressions above l=0.07dh

$l=0.07{d}_{h}$

is the turbulent length scale, where dh

${d}_{h}$

is the hydraulic diameter, which for circular pipes is equal to the diameter d

$d$

.

Table 2. lists boundary conditions prescribed for full boundary layer resolution case with y+

${y}^{+}$

being around 1 and using k−ωSST

$k-\omega \text{}SST$

turbulence model. It shows that at the pipe surface, k

$k$

was set to be 0

$0$

, while for ω

$\omega $

a wall function is prescribed. This it the recommended setting for meshes with y+≈1

${y}^{+}\approx 1$

for the version of OPENFOAM® turbulence models currently running on SimScale platform. The validity of such choice will be demonstrated in the result section below.

Results

The velocity profile for turbulent pipe flow is approximated by an empirically derived relation [1]:

is a measure of the curvature of the profile. For this case, it is calculated to be 6.189

$6.189$

.

The pressure drop for turbulent flow in pipes is obtained by the Darcy friction factor f

$f$

calculated by the solution of the Colebrook equation. The solution of the Colebrook equation is plotted in the form of the Moody diagram (See Fig.3.) and for this case, the value of f

$f$

is 0.0309

$0.0309$

. This value is then used to calculate the pressure drop using the Darcy-Weisbach equation:

ΔP=fρu2l2d

$$\mathrm{\Delta}P=f\frac{\rho {u}^{2}l}{2d}$$

The comparison of simulation results using wall function approach with the result of analytical calculation is given in Fig.3A and 3B. Pressure drop along the pipe length can be observed in Fig.3A, while Fig.3B shows the developed radial velocity profile, located 60cm

$60\text{}cm$

from the inlet.

The first cell center for “wall function approach” is on average at y+=32.7

${y}^{+}=32.7$

for k−ωSST

$k-\omega \text{}SST$

and y+=33.45

${y}^{+}=33.45$

for k−ϵ

$k-\u03f5$

. For “full resolution”, average wall distance of first cell center is at y+=1.24

${y}^{+}=1.24$

. These values were calculated from simulation results.

Besides good agreement with the analytical model, results show that k−ωSST

$k-\omega \text{}SST$

and k−ϵ

$k-\u03f5$

are equally successful in predicting the pressure drop along pipe length using “wall function” approach, for the given mesh.

Fig.3. Pressure drop along the pipe length (A) and radial velocity profile (B) – for simulations with wall function approach

The k−ωSST

$k-\omega \text{}SST$

is chosen for full boundary layer resolution case since it takes advantage of accuracy of k−ω

$k-\omega $

model in proximity of no-slip boundaries, while in the free-stream flow it uses k−ϵ

$k-\u03f5$

formulation, thus avoiding the tendency of k−ω

$k-\omega $

of being too sensitive to inlet turbulence quantities. Switching between the two formulations is done seamlessly by blending functions. Moreover, use of k−ω

$k-\omega $

formulation close to the wall makes the k−ωSST

$k-\omega \text{}SST$

directly applicable for full resolution case, since it does not need extra damping functions to ensure correct behavior close to walls.

The comparison of simulation results using full resolution approach with the analytical calculations is given in Fig.4C and 4D. Pressure drop along the pipe length can be observed in Fig.4C, while Fig.4D shows the developed radial velocity profile, located 60cm

$60\text{}cm$

from the inlet.

Fig.4. Pressure drop along the pipe length (C) and radial velocity profile (D) – for simulations with full boundary layer resolution.

Average pressure difference between inlet and outlet is better predicted by k−ωSST

$k-\omega \text{}SST$

and full resolution modeling, while pressure distribution along wide range of L

$L$

values is equally well predicted with wall function as well as the full resolutionmodeling.

Velocity profiles from simulations using full resolution approach show better prediction of maximum velocity at the pipe centerline, as well as better agreement with analytical model in areas of high velocity gradient, i.e. close to the wall. The reason for the latter lies in the mesh used for “wall function” modeling. Precisely in its coarseness in the near-wall region, which was deliberately introduced in order to place the first cell center in the y+>30

${y}^{+}>30$

region. Flow velocity is relatively low in the present case, which reflects in boundary layer thickness, and ultimately in the height of first cell next to the boundary. This kind of situations is sometimes faced in modeling, meaning that a certain modeling approach can be more or less favorable for a specific application.

Taking all results in consideration, it can be observed that a generally good correspondence exists between analytical results and SimScale simulations.

References

[1]

(1, 2, 3) A Course in Fluid Mechanics with Vector Field Theory – Dennis C. Prieve

Disclaimer

This offering is not approved or endorsed by OpenCFD Limited, producer and distributor of the OpenFOAM software and owner of the OPENFOAM® and OpenCFD® trade marks. OPENFOAM® is a registered trade mark of OpenCFD Limited, producer and distributor of the OpenFOAM software.

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