UFR 2-12 Evaluation
Turbulent Flow Past Two-Body Configurations
Flows Around Bodies
Underlying Flow Regime 2-12
Evaluation
Comparison of CFD Calculations with Experiments
This section is organized as follows. First, results of some sensitivity studies are presented and briefly discussed. These include evaluation of such effects as span-size of the domain, compressibility, time sample used for computing the mean flow and turbulent statistics, and numerical dissipation of the method used. Then, a comparison with the experimental data is shown for the main body of simulations carried out within the ATAAC project with the use of the physical and computational problem setups outlined in the Test Case section.
RESULTS OF SENSITIVITY STUDIES
Effect of span size of domain
As mentioned in the Test Case Experiments section above, the aspect ratio of the CT configuration L_{z}/ D in the BART facility is equal to 12.4. Strictly speaking this demands carrying out simulations exactly at this value of L_{z}/ D and imposing no-slip boundary conditions on the floor and ceiling of the test section (see Figure 2). However such simulations would be very expensive. Considering this and, also, recommendations of the BANC-I Workshop based on simulations at different L_{z}/ D with periodic boundary conditions in the spanwise directions, most of the simulations in the ATAAC project were performed at L_{z}/ D = 3 assuming spanwise periodicity. In order to get an idea on how strong the effect of such a simplification could be, NTS conducted a series of simulations at different L_{z}/ D. Some results of these simulations are presented below ^{[1]}
Figure 4 compares flow visualisations from the SA DDES carried out in the "mandatory"
(L_{z}/ D = 3) and the widest of the considered domains (L_{z}/ D = 16)
in the form of instantaneous isosurface of the magnitude of the second eigenvalue of the velocity gradient tensor or
"swirl" quantity, λ_{2}.
The figure is reassuring in the sense that it visibly displays that the narrow-domain simulation resolves not only
fine-grained turbulent eddies but also large, nearly coherent, structures and exhibits all the complex flow features
observed in the visualization of the wide-domain simulation, except for the initial region of the free shear-layer
separated from the upstream cylinder, where a noticeable difference between the two flow-visualizations is observed.
Figure 4: Isosurface of λ_{2} = 4.0(U_{0} /D ) from incompressible SA DDES at L_{z} = 3D and 16D. |
As a result, sensitivity of predictions of the major characteristics of the flow in the wake of the downstream cylinder
to the value of L_{z}/D turns out to be marginal (see Figure 5
and Table 4).
At the same time, as seen in Figure 6, the flow features directly related to the details
of the flow past the upstream cylinder (its boundary layers separation and shear-layers roll-up) vary with L_{z}/D
variation rather significantly.
Other than that, Figures 5, 6 suggest that the effect of
L_{z}/D within different turbulence modelling approaches is different and is stronger pronounced for IDDES than for DDES.
These findings should be kept in mind when analyzing agreement with the experiment of the simulations carried out at
L_{z}/D = 3 with the use of different approaches to turbulence representation presented in the
comparison with experiment section.
Shedding frequency, Hz | |
---|---|
DDES, L_{z} = 3D | 188 |
DDES, L_{z} = 16D | 188 |
IIDDES, L_{z} = 3D | 192 |
IIDDES, L_{z} = 16D | 192 |
- ↑ The simulations at L_{z}/ D = 16 were conducted with the use of resources of the Argonne Leadership Computing Facility at Argonne National Laboratory, which is supported by the Office of Science of the U.S. Department of Energy under contract DE-AC02-06CH11357.
Compressibility effects
Considering that TUB simulations were carried out under assumption of incompressible flow and BTU and DLR performed compressible simulation at the experimental value of the Mach number (M = 0.128), it was important to find out how strongly this could affect the obtained results. In order to gain this knowledge NTS has carried out IDDES simulations both in the framework of incompressible and compressible problem statements. Results of these two simulations for the quantities which were found to be most sensitive to L_{z}/D (see Figure 6) are shown in Figure 7. They suggest that the role of the effects of compressibility in the considered flow is negligible.
Effect of time sample
This effect has been shown to be very strong for nominally 2D bodies with massive separation in many previous DES and LES studies. This is not surprising, since such flows typically have large scale coherent vortices in a vortex street pattern overlaid with finer random turbulent fluctuations at higher frequencies and random modulation and intermittency at frequencies lower than the vortex shedding one. This is true for the TC flow as well (see Figure 4), which dictates a need of rather long time samples for getting statistically representative mean flow characteristics and especially turbulence statistics. In order to exclude or at least minimize the effect of insufficient time sample when comparing results of different simulations, NTS has carried out a time-sample sensitivity study of the SA DDES of the TC flow. Its outcome is presented in Figure 8 and in Table 5. One can see that the time sample of about 150 convective time units (D / U_{0}) is sufficient to obtain a reliable statistics not only for the mean drag but also for rms of the pressure coefficient. Exactly this value was recommended as a minimum one within the ATAAC project.
Time, Convective time units (D/U_{0}) | C_{D} upstream cylinder | C_{D} downstream cylinder |
---|---|---|
100 | 0.501 | 0.410 |
200 | 0.510 | 0.403 |
300 | 0.505 | 0.404 |
Effect of numerical dissipation
In order to evaluate this effect, NTS has carried compressible SA IDDES of the flow at L_{z} = 3D on the mandatory grid with the use of different approximations of the inviscid fluxes, F_{inv}, available in the NTS code. All these approximations are based on the weighted upwind-biased (F_{upw} ) and central (F_{ctr} ) schemes
with the solution-dependent empiric weight-function of the upwind scheme, σ_{upw}, computed as
.
The function is designed so that σ_{upw} ∈ [σ_{min}, σ_{max} ] and is close to σ_{min} in the LES region of DES and close to σ_{max} in the RANS, irrotational, and departure regions [14]. The series of simulations performed included three simulations, all carried out for compressible flow in free air rather than in the wind tunnel. The first and the second ones had σ_{min} = 0 and combined the 4^{th} order central scheme with 5^{th} and 3^{rd} order upwind-biased schemes, respectively, whereas the third one had σ_{min} = 0.2 and combined 4^{th} order central scheme with 3^{rd} order upwind-biased scheme. Thus the first scheme has the minimum and the third scheme the maximum numerical dissipation with the second scheme somewhere in between ^{[1]}. Some results from this series are presented in Figures 9, 10.
They clearly show that increase of numerical dissipation causes a visible delay of the roll-up of the shear layer separated
from the upstream cylinder and general damping of resolved turbulent structures (Figure 9).
This, in turn, leads to a tangible variation not only of the unsteady pressure but also the mean flow parameters
(Figure 10), which turns out to be comparable with their variation caused by the variation of the
span size of the computational domain (see Figure 6 above).
Based on these results, it can be concluded that using as low dissipative scheme as possible is essential for
simulation of the considered and similar flows.
Also, the fact that even relatively mild increase of the upwinding results in a considerable variation of the mean flow predictions
suggests that the mandatory grid is not "fine-enough", which should be kept in mind when assessing agreement of results of
simulations with the use of different turbulence modelling approaches with experiment presented in
the comparison with experiment section below.
- ↑ Note that all the NTS results presented in the comparison with experiment section below are obtained with the use of the first, less dissipative, scheme.
COMPARISON WITH EXPERIMENT
In this section we present a comparison of predictions based on the simulations summarized in Table 3 above with experimental data ^{[1]}
Experiment | |||
Figure 11: Comparison of predicted and experimental instantaneous vorticity fields |
Figure 11 presents flow visualizations from the PIV and from all the simulations in the form of
instantaneous contours of the spanwise vorticity component.
One can see that all the simulations predict qualitatively similar and generally plausible (consistent with the experiment)
turbulent structures both in the gap between the cylinders and in the wake of the downstream cylinder.
This suggests that the modelling approaches used, in principle, are capable of representing the key physics of the flow
and that the numerical methods applied in all the codes possess essential features needed for turbulence- resolving simulations.
At the same time, the comparison reveals considerable difference between the simulations which is most pronounced
in the initial region of the free shear layers separated from the upstream cylinder, the peculiarities being associated with
both turbulence models and codes.
We now move to a quantitative comparison with the experiment of the computed mean flow characteristics, particularly,
distributions of mean pressure coefficient C_{p} over the surface of both cylinders and centreline
distributions of the mean streamwise velocity in the gap between the cylinders and in the wake of the downstream cylinder.
Figure 12: Mean pressure coefficient distributions on the upstream (left column) and downstream (right column) cylinders. |
As far as the pressure coefficient is concerned (see Figure 12), although the difference
of the resolved turbulent structures described above naturally results in some difference of its predictions by different
simulations, this effect turns out to be insignificant: all the computed distributions are, in general, reasonably close
to each other and fairly well agree with the data, thus supporting a capability of a reliable prediction of the mean surface
pressure by all the considered modelling approaches/codes.
The only simulation in which prediction of the mean pressure is somewhat away from the other ones is that of SST DDES BTU.
For the upstream cylinder it results in a bit too early separation and underestimation of the pressure peak but better than other
simulations predicts a level of the pressure on its leeward part, whereas for the downstream cylinder, this level, on the contrary,
turns out to be noticeably overestimated.
DLR, NTS and TUB results (both SA DDES and SA IDDES) are very close to each other and generally agree well with the data.
Figure 13: Centerline distributions of mean streamwise velocity in the gap between cylinders (left column) and in the wake of the downstream cylinder (right column) |
A comparison of centreline distributions of the mean streamwise velocity component, U /U_{0},
shown in Figure 13 suggests that this flow quantity, especially in the gap between the cylinders
(left column in the figure), turns out to be much more sensitive to both modelling approach and code, which is not surprising
considering the strong sensitivity of this quantity to the numerics discussed above
(see Figures 9, 10).
In particular, within the DDES group (upper row in Figure 13), the length of the
recirculation zone forming downstream of the upstream cylinder varies from about 1.65D (DLR and NTS SA DDES), which is very close
to the experimental value, up to about 1.95D (TUB SA DDES), thus showing a considerable code-dependence.
This is true also for the SA IDDES predictions of U /U_{0} in the NTS and TUB computations
(see lower row in Figure 13).
Both NTS and TUB observe the same model dependence between DDES and IDDES, namely a shortening of the recirculation length with IDDES.
The magnitude of the effect is also similarly predicted by NTS and TUB.
However, the degree of agreement with the benchmark data is predicted differently by these partners:
For TUB, IDDES gives good agreement with the experiment, whereas for NTS the DDES approach is superior.
This difference is most probably explained by the different level of numerical dissipation of numerics used in NTS and ELAN codes
in the LES region of DDES and IDDES (central differences of the 4^{th} and 2^{nd} order for the inviscid fluxes respectively).
For the near wake of the downstream cylinder, the scatter of the predictions of the centreline velocity is somewhat reduced,
and at x < 4.65D, where experimental data are available, they all are very close to the data.
A general conclusion regarding the mean flow prediction, which can be drawn based on the analysis of
Figures 12 and 13, is that the surface pressure can be predicted
by all the models and codes fairly well.
For the velocity field, especially in the gap between cylinders, because of the strong code-sensitivity of the results, the situation
is not that clear.
Particularly, two of three SA DDES computations (those of DLR and NTS) predict close velocity distributions both well agreeing
with the data.
However, SA DDES of TUB gets quite a bit away from them.
Other than that, for the same reason, according to NTS simulations, SA IDDES performs worse than SA DDES, whereas the SA IDDES
solution of TUB turns out to be much closer to the data than their SA DDES.
So, any absolute conclusions on the relative capabilities of DDES and IDDES, based on the analysis of U /U_{0}
distributions in the gap regions remain elusive.
Figure 14: Distributions of rms of pressure coefficient fluctuations on the upstream (left column) and downstream (right column) cylinders |
Similar conclusions can be drawn regarding the unsteady flow characteristics which are of major interest in terms of
aero-acoustic applications.
In particular, as seen in Figure 14, the difference between distributions of the root-mean
square (rms) of the surface pressure coefficient (C'_{p})_{rms} caused by both different turbulence
treatments and different numerics used in the simulations is rather large, especially for the upstream cylinder, where it reaches
about a factor 1.5.
In the DDES group (upper row in Figure 14), the best prediction of this quantity is that of the SA based DDES of NTS: SA DDES of TUB underestimates it over all ϑ, SA DDES of DLR predicts too low level of (C'_{p})_{rms} on the leeward part the cylinder, and SST DDES of BTU significantly overestimates (C'_{p})_{rms} over the whole surface. For the downstream cylinder, good agreement with the data are obtained in all the simulations, except for the SST DDES of BTU, which tangibly overestimates (C'_{p})_{rms} all over the cylinder. A possible explanation for the behaviour of the BTU simulation could be the earlier separation from the upstream cylinder, noted in the commentary to Fig. 12. This in turn, may be due to the underlying SST RANS model applied, however independent SST-based simulations with other codes would be required to confirm this. The earlier separation likely leads to a wider, more energetic wake, hence higher global levels of (C'_{p})_{rms}. Both SA IDDES computations predict higher levels of (C'_{p})_{rms} than their SA DDES counterparts (compare second and first rows in Figure 14), the trend being mostly pronounced for the upstream cylinder. This is consistent with the flow visualisations shown in Figure 11: IDDES predicts earlier roll-up of the shear layer separated from this cylinder than DDES. As a result, similar to what is observed for the centreline velocity distribution, SA IDDES of TUB gets very close to the data, whereas SA IDDES of NTS strongly overestimates (C'_{p})_{rms} on the upstream cylinder and somewhat overestimates it on the downstream cylinder.
Figure 15: PSD of the pressure on the upstream (left column) and downstream (right column) cylinders |
Figure 15 compares predicted and measured spectral characteristics of the surface pressure signals.
It shows plots of Power Spectral Density (PSD) of the pressure fluctuations at the polar angle of 135° for the upstream
(left column) and 45° for the downstream (right column) cylinders.
One can see that the simulations reproduce major characteristics of the shape of experimental spectra, except for the
plateau between 400Hz and 2000Hz observed in the experimental spectrum on the upstream cylinder, which is probably caused by the
tripping of the boundary layers in the experiment (it was not observed in un-tripped configurations [2, 3]).
Note also that SA DDES and SA IDDES spectra for the upstream cylinder of both NTS and TUB have high-frequency peaks (at about
1400Hz and 2000Hz with DDES and 2400Hz and 3000Hz with IDDES) which are not observed in the experimental spectra and are probably
spurious (perhaps associated with an inadequate representation of the initial stage of the shear layer roll-up).
A quantitative comparison of the spectra reveals a rather wide scatter of frequencies and amplitudes of the primary spectral peak
(see Table 6).
This is consistent with the scatter of predicted locations of the separation on the upstream cylinder: an upstream shift of the
separation should lead to slower shedding and lower frequencies.
The trend is clearly seen in the SST DDES of BTU. Other than that, the spectral peak predicted by this simulation is for unknown
reason more "smeared" compared with the other simulations and experiment.
Finally, predicted levels of the broadband part of the spectrum for the upstream cylinder also turn out to be model- and
code-dependent (the scatter of predictions reaches 10dB), whereas for the downstream cylinder these levels are close to each other
and fairly well agree with the data.
Primary shredding
frequency, Hz |
Tone amplitude,
Upstream cylinder, dB |
Tone amplitude,
Downstream cylinder, dB | |
---|---|---|---|
BART Exp. | 181 | 118.1 | 139.5 |
SA DDES, NTS | 188.0 | 117.1 | 141.2 |
SA DDES, TUB | 185.6 | 113.3 | 140.3 |
SST DDES, BTU | 163.8 | 116.6 | 139.3 |
SA IDDES, NTS | 192.7 | 124.3 | 142.7 |
SA IDDES, TUB | 185.6 | 121.0 | 142.5 |
The scatter of the spectra from different simulations for the downstream cylinder is much less compared with the upstream cylinder,
and all the predictions, except for those of the SST DDES of BTU, are in quite good agreement with the data (a tentative explanation for this
based on the separation prediction by the SST model has been offered above).
Considering that the input of the downstream cylinder in the noise generated by the tandem is dominant (the amplitude of the tone in the
PSD of the pressure on the downstream cylinder is about 20dB larger than that on the upstream cylinder), this suggests that most of the
simulations are capable of reliable prediction of the far-field noise of the tandem, which is a primary objective of turbulence-resolving
simulations of the considered UFR.
One more characteristic of turbulence in the considered flow available in the experimental database is the two-dimensional (including only
streamwise and lateral components of the velocity fluctuations) kinetic energy, 2D TKE.
A comparison of the predicted and measured centreline distributions and profiles of this quantity in two flow sections is shown in
Figures 16, 17 respectively.
One can see that the scatter of its predictions is rather wide, none of the models being capable of capturing its experimental behaviour
equally well in the whole flow.
Figure 16: Centerline distributions of resolved 2D TKE in the gap between cylinders (left column) and in the wake of the downstream cylinder (right column). |
Figure 17: Profiles of resolved 2D kinetic energy in the gap between cylinders at x = 1.5D (left column) and in the wake of the downstream cylinder at x = 4.5D (right column) |
- ↑ For NTS, results of the incompressible simulations are shown obtained at L_{z} = 3 with the use of hybrid, 5/4, scheme at σ_{min} = 0.
Contributed by: A. Garbaruk, M. Shur and M. Strelets — New Technologies and Services LLC (NTS) and St.-Petersburg State Polytechnic University
© copyright ERCOFTAC 2019