Turbulence decay towards the linearly-stable regime of Taylor-Couette flow
Taylor-Couette (TC) flow is used to probe the hydrodynamical stability of astrophysical accretion disks. Experimental data on the subcritical stability of TC are in conflict about the existence of turbulence (cf. Ji et al. Nature, 444, 343-346 (2006) and Paoletti et al., A&A, 547, A64 (2012)), with discrepancies attributed to end-plate effects. In this paper we numerically simulate TC flow with axially periodic boundary conditions to explore the existence of sub-critical transitions to turbulence when no end-plates are present. We start the simulations with a fully turbulent state in the unstable regime and enter the linearly stable regime by suddenly starting a (stabilizing) outer cylinder rotation. The shear Reynolds number of the turbulent initial state is up to and the radius ratio is . The stabilization causes the system to behave as a damped oscillator and correspondingly the turbulence decays. The evolution of the torque and turbulent kinetic energy is analysed and the periodicity and damping of the oscillations are quantified and explained as a function of shear Reynolds number. Though the initially turbulent flow state decays, surprisingly, the system is found to absorb energy during this decay.
Quasars are the most luminous objects in the Universe. They are thought to consist of supermassive black holes in the centres of galaxies, which accrete matter and emit radiation, thereby transforming mass into energy with an efficiency between 5-40% (1); (2). In order for orbiting material to fall into the so-called astrophysical accretion disk, it must lose its angular momentum. Molecular viscosity alone is not enough to account for this loss, so some sort of turbulent viscosity, causing the enhanced transport of angular momentum, has been conjectured (3), as otherwise gravitationally bound objects, like galaxies, stars or planets, would not exist. This implies that the flow of the material must be turbulent, but the origin of turbulence in accretion disks is currently unknown. Accretion disks can either be composed of “hot” matter, which is fully ionized and electrically conducting, or “cold” matter, i. e., dust with less than 1% ionized matter. Hot disks are found around quasars and active galactic nuclei, and thought to undergo a magneto-rotational instability (MRI) to become turbulent (4); (5). In contrast, cold disks are found in protoplanetary systems, and are thought to have “MRI-dead” regions, where turbulence due the MRI cannot exist (6); (2). The places where planets eventually form and reside coincide with these MRI-dead regions, so additional transport of angular momentum must take place. To account for this transport, another mechanism has been proposed: hydrodynamical (HD) non-linear instabilities, i.e. transport by turbulence.
Taylor-Couette flow (TC) is the flow between two coaxial cylinders which rotate independently. It is used as a model for probing the HD stability of accretion disks (1). Accretion disks have velocity profiles that are linearly stable, but just as in pipe and channel flows, the shear Reynolds numbers are so large that non-linear instabilities may play a role in the formation of turbulence. The question whether TC flow indeed does undergo a non-linear transition (7); (8) to turbulence at large shear Reynolds numbers has been probed experimentally by several authors with conflicting results(9); (10); (11); (12); (13); (14); (15); (16). The discrepancies between the different experiments have been attributed to the end-plates of the TC devices, i.e. the solid boundaries which axially confine TC flow. These cause secondary flows, known as Ekman circulation, which propagate into the flow and influence global stability. Avila (16), based on his numerical simulations with end-plates imitating the Ji et al. (11) and the Paoletti et al. (15) experiments, concluded that both of these experiments were not adequate for studying the non-linear transition due to the presence of end-plates. However, these simulations are at shear Reynolds numbers of the order , while Ji et al. (11) mention the counter-intuitive result that must exceed a certain threshold before the flow relaminarizes.
Indeed, confinement of the flow plays a very important role in this transition, but it is unavoidable in experiments. Direct numerical simulations (DNS) do not have these limitations, as they can be run with periodic boundary conditions to completely prevent end-plate effects. Following this idea, Lesur and Longaretti (17) simulated rotating plane Couette flow with perturbed initial conditions, going up to shear Reynolds numbers of order , but due to computational limitations, the quasi-Keplerian regime velocity (i.e., the regime where the two velocity boundary conditions are related by Kepler’s third law), was not reached.
In this letter, we adopt a similar approach, but now for Taylor-Couette flow and in particular reaching larger shear Reynolds numbers . We proceed as follows: We start from an already turbulent flow field and then add stabilizing outer cylinder rotation, wondering whether the turbulence is sustained. We find that it is not: the turbulence decays, and the torque decreases down to a value corresponding to purely azimuthal, laminar flow. This means that not only the TC system is linearly stable in this geometry, but an initially turbulent flow even decays towards the linearly stable regime.
The DNSs were performed using a second-order finite difference code with fractional time-stepping (18). This code was already validated and used extensively in the context of TC (19); (20). The turbulent initial conditions will be taken from previous work (20). The radius ratio is , where and are the inner and outer radius, respectively, and the aspect ratio is , where is the axial periodicity length, and the gap width . A rotational symmetry of order 6 was forced on the system to reduce computational costs while not affecting the results (21); (20).
The simulations are performed in a frame of reference co-rotating with the outer cylinder.
In the rotating frame, the inner cylinder has an
azimuthal velocity , with and
the inner and outer cylinder angular velocities respectively, while the outer cylinder is now stationary. The resulting shear drives the flow,
and can be expressed non-dimensionally as a shear Reynolds number
Six simulations were run: Three with fixed , but different strength of the Coriolis force, namely: a) , corresponding to a system on the Rayleigh-stability line, equivalent to , or in the lab frame of reference; b) , corresponding to or a system in the quasi-Keplerian regime, i.e. the regime in which the angular velocities at the two cylinders are related by Kepler’s third law ; and c) , an even stronger stabilization, equivalent to . The other three simulations were done by fixing and giving the values , , and . Grids of = were used for all simulations, except for , where a grid of = is required to guarantee sufficient resolution.
Simulating in a rotating frame adds a new perspective to the problem. In this frame the (non-dimensional) Navier-Stokes equations read:
Strong enough outer cylinder co-rotation in the lab-frame implies a large stabilizing Coriolis force in the rotating frame and turbulence is suppressed (19). This argument for stabilization (19) can be compared to that of Taylor-Proudman’s theorem (23); (24) which when applied to rotating Rayleigh-Bénard flow implies that the flow is stable even at large thermal driving, as long as the background rotation is large enough(25).
Fig. 1 shows three instantaneous snapshots of the angular velocity for , one for , and two for and , after the stabilizing Coriolis force corresponding to the quasi-Keplerian regime, , was added. The sequence of figures shows the reversal of the Taylor vortices, which happens with a period of . If the system is simulated for a large enough time, here , the Taylor vortices progressively fade away. The system behaves as a damped oscillator.
To quantify these reversals, we define the quasi-Nusselt number (26) as , where is the torque required to drive the system in the purely azimuthal and laminar case. represents the transport of angular velocity. For a purely azimuthal flow with no turbulence, , so represents the additional transport of angular velocity due to turbulence.
Figure 2a shows a time series of the axially averaged at the mid-radius , for and three values of the Coriolis force. can be seen to oscillate between large positive and large negative values, with an average , i.e. no net turbulent transport. The period of oscillation depends on . Fig. 2c shows long time series for . For large enough times, the oscillations damp out and the flow becomes purely azimuthal and laminar, . Fig. 2b shows for three values of and . Similar oscillations in can be seen, but in this case the period weakly depends on .
Figure 3 shows the axially averaged but now measured directly at the inner cylinder (probing the inner boundary layer (BL)), for different values of and . Unlike the previous mid gap case, no oscillations can be seen, reflecting that the oscillations only occur in the bulk of the flow, where the Taylor vortices are, but that the BLs are unaffected. Of course, the decay towards the purely azimuthal, laminar state is also observed in the BLs (Fig 3a,b), independent of and .
Finally, we quantify the decay of turbulence. To do so, we define the turbulent kinetic energy substitute of the flow as . Note that this is not the full turbulent energy, as for that also fluctuations in contribute, but, by definition, has the nice property to be zero in the purely azimuthal state. Fig. 4a shows the decay of for and three values of , while fig 4b shows the decay for and three values of . In the simulations, shows short time scale fluctuations, similar to that of in the mid-gap, so for clarity, only the peak of in every cycle is represented.
As expected from the previous results on , decays to zero when given enough time. The only mechanism for energy dissipation is viscosity, so it is not surprising that the decay time is proportional to the energy content, thus leading to an approximately exponential decay, where is the characteristic (dimensionless) decay time, and . Fits to the data in fig. 4b were performed to obtain estimates for the dependence , which is shown in fig. 5a. The absolute value of is large (around large eddy turnover times for and ) and in the range studied shows a power-law
This scaling can be understood from realizing that the decay of the turbulence is first dominated by the energy dissipation rate in the BLs, which scales as (27) . This immediately implies the scaling relation (2) for the typical decay time . Only for very large times or for very small Reynolds numbers from the very beginning, i.e., when the thickness of the BLs is comparable to the gap thickness and the Taylor rolls have died out or are absent, one has (cf. ref. (28)) and thus . This second regime can be seen in figs. 3b and 5b.
We highlight that even though decays, the total energy of the system increases, as it absorbs more energy through the boundaries than it dissipates viscidly. This can be seen in fig. 5b, displaying a time series of the non-dimensionalized energy input into the system , where is the torque applied at the inner (outer) cylinder, and are the fluid density and volume, respectively, and is the viscous dissipation in the purely azimuthal and laminar state, and a time series of the non-dimensionalized energy dissipation rate inside the system, . When transitioning from turbulence to the purely azimuthal -profile, the system absorbs energy, while at the same time the initial turbulence decays. The purely azimuthal -profile has more energy than its turbulent counterpart. Indeed, this is the reason for the Rayleigh instability, now supressed by the Coriolis force.
Again, two time scales for the decay can be seen in the inset of fig 5b. After the initial transient, turbulence in the bulk decays fast, due to the efficient angular momentum transport by the Taylor rolls. After about 200-300 large eddy turnover times this decay mechanism is exhausted as then the (turbulent) Taylor rolls in the bulk are so weak that they can no longer transport angular momentum. Then a second decay mechanism takes over, whose onset is marked by an arrow in the inset of fig 5b. In this regime, characterized by purely viscous dissipation in the whole gap, the profile returns to the azimuthal and laminar one and thus to . It is important to note that must return to , as in the statistically stationary state, has to be independent of .
In summary, consistent with what had been found in the experiments of Ji et al.(11), no turbulence, and therefore, no turbulent transport of angular momentum can be seen in the Rayleigh-stable regime for the control parameter range studied once the effect of axial boundaries is mitigated. An initially turbulent state is stabilized by the corotation of the outer cylinder and the transport of angular momentum in the bulk ceases; the turbulence decays in all our simulations, for up to .
We point out, however, that even though the system is stable, the decay times for turbulence are long,
ranging between hundreds and thousands of large eddy turnover times. If one extrapolates
In conclusion, in our TC simulations without end-plates, in the parameter range studied up to shear Reynolds numbers of , the flow was seen to not only remain laminar in the presence of small perturbations, but when starting from an initially turbulent state we can see that the turbulence decays and the system returns to its laminar state. All of this happens while the system absorbs energy. Therefore, we can attribute the turbulence and increased angular momentum transport found in some of the experiments (10); (14) and numerical simulations (16) which probe the linearly stable regime of TC, to effects of the end-plate confinement.
Acknowledgments: We would like to thank C. Sun for various stimulating discussions. We acknowledge an ERC Advanced Grant and the PRACE resource Curie, based in France at GENCI/CEA.
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