friction factor of annular poiseuille flow in a transitional regime

Special Issue Article Friction factor of annular Poiseuille flow in a transitional regime Advances in Mechanical Engineering 2017, Vol 9(1) 1–10 Ó The Author(s) 2017 DOI: 10.1177/1687814016683358 journals.sagepub.com/home/ade Takahiro Ishida and Takahiro Tsukahara Abstract Annular Poiseuille flows in a transitional regime were investigated by direct numerical simulations with an emphasis on turbulent statistics including the friction factor that are affected by the presence of large-scale transitional structures Five different radius ratios in the range of 0.1–0.8 and several friction Reynolds numbers in the range of 48–150 were analyzed to consider various flow states accompanied by characteristic transitional structures Three characteristic structures, namely, turbulent–laminar coexistence referred to as ‘‘(straight) puff,’’‘‘helical puff,’’ and ‘‘helical turbulence’’ were observed The selection of the structures depends on both the radius ratio and the Reynolds number The findings indicated that despite the transitional state with a turbulent–laminar coexistence, the helical turbulence resulted in a friction factor that was as high as the fully turbulent value In contrast, with respect to the occurrence of streamwise-finite transitional structures, such as straight/helical puffs, the friction factor decreased in a stepwise manner toward a laminar level The turbulent statistics revealed asymmetric distributions with respect to the wall-normal direction wherein the profiles and magnitudes were significantly influenced by the occurrence of transitional structures Keywords Annular Poiseuille flow, direct numerical simulation, helical turbulence, subcritical transition, turbulent statistics Date received: September 2016; accepted: 17 November 2016 Academic Editor: Bo Yu Introduction Turbulent transition in most wall-bounded shear flows is characterized by subcritical scenarios.1,2 There exists a significant hysteresis between critical Reynolds numbers for global (Reg ) and linear instabilities (Rel ) For instance, the cylindrical Poiseuille flow (cPf) and plane Couette flow (pCf) are widely known to be linearly stable for any Reynolds number However, experimental studies demonstrated that both cPf and pCf cannot maintain these laminar states at high Reynolds numbers, no matter how ideal experiment is conducted,3 because unpreventable finite-amplitude disturbance triggers a subcritical bypass transition for Re (\Rel ) The lower bound of this subcritical transitional regime may be defined as Reg This corresponds to the lowest Reynolds number to sustain turbulence even under a spatiotemporal intermittent state, and this value is important practically and scientifically In the plane Poiseuille flow (pPf), Rel is known as 5772,4 which is based on the channel half width (d) and the channel centerline velocity of laminar flow, and Reg is lower than Rel in a manner similar to cPf and pCf The determination of Reg value generally demands massive flow channel (in experiments) or computational resources (in simulations) because of the presence and large-scale patterning of localized turbulence The flow transition to turbulence undergoes an intermittent turbulent regime around Reg in the subcritical scenario As is widely known, a streamwise Department of Mechanical Engineering, Tokyo University of Science, Noda, Japan Corresponding author: Takahiro Tsukahara, Department of Mechanical Engineering, Tokyo University of Science, 2641 Yamazaki, Noda, Chiba 278-8510, Japan Email: tsuka@rs.tus.ac.jp Creative Commons CC-BY: This article is distributed under the terms of the Creative Commons Attribution 3.0 License (http://www.creativecommons.org/licenses/by/3.0/) which permits any use, reproduction and distribution of the work without further permission provided the original work is attributed as specified on the SAGE and Open Access pages (https://us.sagepub.com/en-us/nam/ open-access-at-sage) 2 localized turbulence that is referred to as a puff is typically observed in cPf.5 Recent studies considered the thermodynamic limits of puff decaying and splitting time scales to determine the value of Reg for cPf.6 However, this is not true for both pPf and pCf, as they reveal a more complex transition scenario given the existence of an additional free dimension in the spanwise direction This contrasts to cPf, which is closed in the azimuthal, or spanwise, direction The transitional structure observed in pPf and pCf around Reg often forms a two-dimensional (2D) pattern, referred to as ‘‘turbulent stripe.’’7,8 The turbulent stripe is very large in both the streamwise and the spanwise directions This stripe pattern is inclined with a certain degree against the streamwise direction However, the inclination angle of pattern has not been unresolved, because it is influenced by both the computational/experimental horizontal domain sizes and the Reynolds number In addition, the decaying and splitting processes of turbulent stripe that are very important phenomena for determined Reg as in cPf are still an open issue to date This study focuses on the subcritical transition of pressure-driven flows between two concentric cylinders This is termed as annular Poiseuille flow (aPf) In addition to its merit of a closed system in the spanwise (azimuthal) direction, the aPf may be an ideal flow system to understand canonical wall-bounded shear flows in a comprehensive manner based on the radius ratio, denoted by h = ri =ro (where ri and ro are the inner and outer radii, respectively) The limiting conditions of h ! and represent the flow geometries of a cylinder and a channel between two parallel plates, respectively, despite the existence of a thin inner cylinder for h ! Actually, a linear stability analysis by Heaton9 demonstrated that aPf should connect two important canonical flows, namely, pPf as h ! and cPf as h ! Hysteresis is also present between Rel and Reg In terms of the transitional structure, our previous study10 revealed smooth alternations, with dependence on h, of the localized turbulent patterns: helical turbulence, helical puff, and straight puff Robust helical turbulence corresponding to the turbulent stripe in pPf has been identified for high h ! 0:5 With decreasing h, the pitch angle of helical turbulence decreases and the flow relaminarizes partly at marginally low Reynolds number for h = 0:3 Finally, a new form of streamwise localized helical turbulence, named helical puff, emerges For much smaller h 0:1, the organized structure becomes axisymmetric, and finite-length streamwise localized structures similar to equilibrium puffs in cPf emerges They reveal that the helical turbulence for high h and the straight puff for low h are linked by the helical puff for intermediate h Detailed expressions of each structure will be shown later with a discussion of the Reynolds number dependency Advances in Mechanical Engineering Ishida et al.10 focused only on transitional structures, and statistical properties in aPf were not examined Hence, this article would describe statistical results including the friction factor This work uses direct numerical simulation (DNS) of a quenching study from fully developed turbulence to a laminar regime in order to investigate how the transitional structure would affect turbulent statistics We discuss rather low-dimensional statistical properties in transitional and fully developed turbulent regimes Patel and Head11 measured the skin friction to scrutinize the transition regime and how turbulence can be sustained in cPf and pPf, both of which are the limiting cases of aPf They found that Reg occurred at for cPf and at Rem jcPf = um D=n ’ 2000 Rem jpPf = 2um d=n ’ 1350 for pPf (where um denotes the bulk mean velocity and D is the pipe diameter) Recently, Samanta et al.12 considered the dependence of the friction factor on initial conditions in cPf focusing on localized structures of puff and spot Their data provided a well-defined connection between the laminar and turbulent laws and predicted well the upper bound of transitional regime Since the aPf is widely used in engineering applications, such as heat exchanger, several previous studies examined the friction factor as typified by Rothfus and colleagues.13–15 Those studies suggested the critical Reynolds numbers of the onset and end of the transitional regime,14 which were defined by a slight progressive departure from the theoretical analysis and the empirical equation of cPf (applied for aPf using the hydraulic diameter), respectively The obtained onset Reynolds numbers of transition for h = and almost agree with those obtained by the recent studies for the global instability of cPf and pPf.11 These studies imply that both laminar and turbulent flow patterns exist in the transitional region Hanks and Bonner16 employed a theoretical analysis to suggest that the first transition occurs near the inner cylinder and the second transition occurring near the outer cylinder follows the first one A smaller radius ratio h led to larger differences in the value of the critical Reynolds number between the first and second transitions Moreover, due to the existence of singularity (inner cylinder), the first critical Reynolds number indicated that the flow was always unstable for any Reynolds number as h approached zero In contrast, there was no difference between the first and second critical Reynolds numbers at h = Their result also suggested that the dual-flow regime consisting of laminar and turbulent flows near the outer and inner cylinders, respectively, separated at the radial position of maximum velocity, and this typically occurred between the first and the second critical Reynolds numbers The second critical Reynolds number (on the outer-cylinder side) obtained experimentally14 and theoretically16 was a similar to that for the pPf, although they did not Ishida and Tsukahara exactly correspond The second critical Reynolds number for aPf was indicated to connect between cPf and pPf with the variance of h Hanks and Peterson17 also performed an experimental study to verify the theoretical analysis, measured the flow rate by the oscilloscope traces at a low radius ratio (h = 0:0416), and observed the first and the second transitions Despite the occurrence of the first transition, no oscillation was observed in the dual-flow regime where oscillations were expected to exist, while disturbed oscillations were detected for the second transition Based on these results of existing studies, this study on aPf investigates its subcritical transition scenario from the developed turbulent state to the laminar flow and scrutinizes the presence of the transitional structure in detail to illuminate the manner in which transitional structures affect flow statistics including the friction factor Numerical methods In this study, DNS of pressure-driven flows was performed in two concentric cylinders A cylindrical coordinate system (x, r, u) was adopted as shown in Figure Additionally, we define y = r À ri , which corresponds to the wall-normal distance from the inner wall, and z = 2pru, which corresponds to the azimuthal length The aPf was driven by a constant uniform pressure gradient (equation 1) in the axial direction x dp t o + ht i =À dx d 1+h ð1Þ Here, to and t i correspond to the mean wall shear stresses at the outer and inner walls, respectively, and d = ro À ri is the gap width between the inner and outer cylinders A periodic boundary condition was imposed in the x and u directions A non-slip condition was applied on the walls The fully developed states of flows were considered The working fluid is an incompressible Newtonian fluid The friction velocities on the inner and outer cylinder, respectively, are defined as follows rffiffiffiffi rffiffiffiffiffi ti to uti = and uto = r r Figure Configuration of the annular Poiseuille flow (aPf) The averaged friction velocity is defined by the following expression sffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi to + ht i ut = rð1 + hÞ ð3Þ The fundamental equations for the velocity u = (ux , ur , uu ) and the pressure p are given by the equation of continuity (equation (4)) and the Navier–Stokes equation (equation (5)) r Á u+ = À Á r2 u+ ∂t u+ + u+ Á r u+ = À rp+ + Ret ð4Þ ð5Þ The superscript + indicates the quantities normalized by the wall unit (i.e the friction velocity ut and/or the kinematic viscosity n) The finite difference method was adopted for the spatial discretization The fourth-order central scheme was employed in both x and u with uniform grids, and the second-order central scheme was in r with nonuniform grids The non-uniform spacing with fine grids near the walls was given as done by Moin and Kim.18 Further information with respect to the numerical methods we employed can be found in the previous reports.10,19 We analyzed several values of Ret = ut d=2n = 48 to 150 and selected five different values of h = 0.1, 0.2, 0.3, 0.5, and 0.8 Table summarizes the simulation parameters In this study, long streamwise domains of Lx = 51.2d–166.0d were set to capture intermittent structures with long streamwise extents As the Reynolds number decreased, the computational domain size was elongated in x so that its length would be almost constant in terms of the wall units As for the azimuthal direction, the present simulation covered the complete domain of u = 2p Its normalized azimuthal length Lz =d = rLu =d should depend on h and r Results and discussions Flow regimes and transitional structures ð2Þ The alternations of dominant transitional structures depending on h and Ret are discussed in this subsection First, we introduce the turbulent fraction to demonstrate the laminar–turbulent coexistence Then, we would show rather simpler transition processes for high and low h, where observed structures are reminiscent of well-known transition scenarios in pPf and cPf Finally, we describe the transition process for intermediate h = 0.3, which seems to combine the features of transitional structures for lower and higher h, as an anomalous case of aPf 4 Advances in Mechanical Engineering Table Computational conditions for DNS: Rem = (um d=n), the bulk Reynolds number; Lx and Lz denote the streamwise and azimuthal lengths (Lzi = 2pri and Lzo = 2pro ); Nx , Ny , and Nz denote the corresponding grid numbers (y = r À ri , z = ru) h Ret Rem Lx =d Lzi (h)=d, Lzo (h)=d Nx Ny Nz 0.8 562150 1590–4630 51.2–74.0 25.1, 31.4 2048 128 1024 0.5 52–150 1460–4640 51.2–80.0 6.28, 12.6 2048 128 512 0.3 50–150 1590–4650 51.2–166.0 2.69, 8.98 2048 or 4096 128 512 0.2 50–150 1660–4630 102.4–166.0 1.57, 7.85 4096 128 256 0.1 46–150 1515–4630 51.2–180.0 0.70, 6.98 2048 or 4096 128 256 DNS: direct numerical simulation Figure Turbulent fraction as a function of the bulk Reynolds number Error bar denotes the magnitude of time variance Figure shows turbulent fraction Ft , modified from Ishida et al.,10 that is employed to specify the transition process in aPf The turbulent fraction illustrates the content rate of turbulence in the flow field When Ft = 1, the flow regime corresponds to featureless turbulence without any laminar patch The zero Ft corresponds to a laminar flow Therefore, intermediate values of Ft indicate the occurrence of turbulent– laminar coexistence Fully developed or featureless turbulence was observed in the high Reynolds number regime With decreasing Rem , Ft decreased gradually for all values of h Once the flow undergoes a transitional Reynolds number regime, the laminar region intermittently occurred in the turbulent region, and Ft decreased toward zero As typical flow regimes describing transitional structures, Figures 3–5 show the 2D contours of wallnormal velocity fluctuations in the xÀz plane for different values of h First, let us focus on the case of a rather high h of 0.5 As visualized in Figure 3(a), featureless turbulence was observed at Ret ! 80 despite the occasional appearance of small laminar patches with wispy obliqueness at Ret = 80 Helical turbulence represented by robust oblique laminar–turbulent patterns emerged at Ret = 64 and 56 This helical turbulence corresponded to a stripe pattern observed in the plane channel flows (pCf and pPf) The laminar region expanded with a decrease in Ret , and the helical turbulence was marginally modulated and collapsed at Ret = 52, as shown in Figure 3(d) Therefore, several helical puffs (with finite streamwise lengths) and Figure Two-dimensional xz-plane contours of wall-normal velocity fluctuations u0r at Ret = (a) 80, (b) 64, (c) 56, and (d) 52 for h = 0:5 The mean flow direction is from left to right and (e) three-dimensional visualization of wall-normal velocity fluctuations at Ret = 56 (u0r ! 0:75, red; u0r < À 0:75, blue) turbulent spots were observed for a very low and narrow Reynolds number range near Reg Whereas the previous study10 suggested that the helical puff occurred only for h = 0.3, we newly observed the helical puff even for high h = 0:5 Xiong et al.20 also reported similar observations in the pPf at very low Reynolds numbers, demonstrating the occurrence of a localized oblique pattern around Reg even for pPf (h ! 1) In Figure 3(e), a three-dimensional (3D) visualization of the helical turbulence in aPf was presented to aid in easy understanding In contrast to the stripe pattern observed in pPf, the helical turbulence coils around the inner cylinder because the flow system of aPf is closed in the azimuthal direction The transition process for h = 0.8 was similar to that for h = 0:5 Ishida and Tsukahara Figure Two-dimensional xz-plane contours of wall-normal velocity fluctuations u0r at Ret = (a) 80, (b) 64, (c) 60 (d) 56, (e) 54, (f) 52, (g) 50, and (h) 48 for h = 0:1 The color range is the same as that in Figure Therefore, clear helical turbulence can be observed for h ! 0:5 A small radius ratio must be expected to reveal transitional states similar to those in cPf Figure shows the flow fields at h = 0:1 The featureless turbulence without any laminar patch was confirmed at Ret = 150 and 80 Even at Ret = 64, almost the whole field is dominated by the turbulent region and sometimes small laminar patches occur, as given in Figure 4(b), although helical turbulence emerges for high h A streamwise localized laminar–turbulent pattern corresponding to the puff in cPf was found below Ret = 60 Even for small h of 0.1, oblique interfaces between turbulent and laminar region were rarely observed at slightly high values of Ret = 60 and 56 As Ret decreased from 60 to 48, the number of puffs or streamwise length of the puff was decreased The puff in aPf exhibited splitting, decaying, and combining processes, which were similar to those of the puff in cPf.21,22 At low Ret , the combining process could not be detected and the probability of splitting decayed analogous to the previous study.22 Although the puffs split, one of the separated puffs immediately decayed in aPf at Ret = 52 and 50 At Ret = 48, any puff splitting was not observed, the streamwise size of the puff changed slightly and increased/decreased with time The flow relaminarized at Ret = 46, and Figure 4(h) shows an instant field before the relaminarization completed As well as the other cases shown above, the intermediate h of 0.3 resulted in the flow state of featureless turbulence at Ret ! 80 (see Figure 5(a)) At Ret = 64, the helical turbulence similar to that observed for h ! 0:5 occurred, as shown in Figure 5(b) There was a Figure Two-dimensional xz-plane contours of wall-normal velocity fluctuations u0r at Ret = (a) 80, (b) 64, (c) 56, (d) 54, and (e) 52 for h = 0:3 The color range is the same as that in Figure breaking-off point of helical turbulence, and streamwise localized helical turbulence (called helical puff) was observed at Ret = 60 Figure 5(c) shows the flow field at Ret = 56, where mixed helical and straight puffs can be observed The obliqueness of the helical puff decayed, the straight puff infrequently occurred at lower Ret , and the probability of occurrence of a straight puff was increased compared to that of the helical puff, with decreasing Ret At Ret = 50, the transitional structure immediately decays and the flow becomes laminar This complex transition process was also found for h = 0:2 The occurrence ratio of straight puff increases more compared to h = 0:3 Additionally, helical turbulence could not be recognized for h = 0:2 even at high values of Ret A future study will discuss the separation of these complex transition processes based on both h and Ret Friction factor The friction factor, denoted by Cf , is defined by following equation as shown in Figure Cf = 2tw u2m ð6Þ The Blasius empirical friction law in the turbulent regime is also shown for a comparison The laminar solution depends on h In the laminar solution of Cf = 8Ch =Rem , the definition of Ch is as follows Ch = À 2h + h2 + h2 + 1Àh2 lnh ð7Þ Advances in Mechanical Engineering Figure (a) Friction factor Cf , (b) product of Rem Cf , and (c) extended figure of Rem Cf around the transitional regime With respect to cPf and pPf as the limiting cases of aPf, Ch values are 1.0 and 1.5, respectively In order to facilitate an easy understanding of the transition process, the product Rem Cf as a function of Rem is also plotted in Figure 6(b) and (c) The friction factor at high Reynolds numbers are in agreement with the empirical function Furthermore, Cf maintained high value even at lower Reynolds numbers in the transitional regime, when the flow is accompanied by the helical turbulence (for h = 0:5 and 0:8) However, given the localization of helical turbulence in the x direction and the emergence of a helical puff, Cf deviated from the empirical function toward a laminar solution, as seen at Ret = 52 (Rem = 1460) for h = 0.5 With respect to intermediate h of 0.2–0.3, Cf maintained a high value similar to that for high h This must be also because of the presence of helical turbulence or helical puff A further decrease in Ret induces a sudden drop of Cf , retaining the same values of Rem and gradually approaches a laminar solution It should be noted again that the present flow system is driven by a fixed-mean pressure gradient and Rem depends on the flow state Under such a condition, once a relaminarization occurs, the bulk Reynolds number Rem should increase significantly with a fixed Ret and lowered Cf In this sense, there exists an overlapping region around Reg for h = 0:2 and 0:3 This must be caused by the alternations of transitional structures from helical turbulence to puffs through helical puff, due to decrease in Ret for moderate h With respect to h = 0:1, Cf gradually decreased with the Reynolds number after the occurrence of the straight puff There is no overlapping region, unlike that observed for intermediate h (h = 0:2 and 0:3) because the transitional structure does not change from straight puff at any Reynolds number for h = 0.1 As described above, Cf in the transitional regime considerably depends on the form of transitional structure Similar aspects can be confirmed from the turbulent fraction that is given in Figure Both Cf and Ft would maintain magnitudes as high as those of featureless turbulence, if the transitional structures forms helical pattern Such an enhancement of turbulence contributions is weakened in the following order: helical turbulence ! helical puff ! straight puff Figure shows the local friction velocities at the inner and outer cylinders (denoted by uti and uto , respectively) and the ratio of the friction Reynolds number on the inner and outer cylinders (denoted by Reti and Reto , respectively) The difference between uti and uto increases at low Ret and small h when compared to the difference at high Ret and large h Specifically, the difference enlarges noticeably when Ret = 80 ! 64, which corresponds to a shift of the regime from the featureless turbulence to a transitional state of helical/straight puff On the outer-cylinder side, uto does not depend much on both h and Ret , and it is approximate to the global friction velocity ut defined by equation (3) In contrast, uti is significantly different from ut and depends on h and Ret The distribution of Ishida and Tsukahara Figure Mean streamwise velocity profiles The line types indicate different values of h, and the colors correspond to different values of Ret The inner-cylinder wall corresponds to y=d = 0, while the outer one is at y=d = Figure (a) Friction velocity on the inner and outer cylinders (uti and uto ) as a function of Rem (b) Comparison of the friction Reynolds number based on the inner friction velocity versus the friction Reynolds number based on the outer friction velocity If h = 1, it should be Reti = Reto the ratios of the friction Reynolds number for all values of h was almost a linear distribution, as shown in Figure 7(b) This implies a less dependency of the ratio Reti =Reto on the global Reynolds number (Ret ) Here, let us briefly describe a background mechanism of the high friction velocity, that is, the large velocity gradient, on the inner-cylinder wall, which can be seen in Figures 7(a) and In aPf, the inner cylinder should be associated with a large number of intensive sweep and ejection events that can be attributed to the transverse curvature effect.23 In addition, elongated streaky structures near the inner wall are more active than those along the outer wall The turbulent motions on the outer wall are similar to those near the flat wall of cPf and pPf These phenomena have also been studied by Satake and Kawamura.24 They discovered that a high-speed fluid impinging against and across the inner rod would form a wake-like region behind the rod and a large-scale wall-normal motion in the large lowpressure region This distinctive turbulent event increases the friction Reynolds number on the inner cylinder, and this phenomenon leads an asymmetric profile especially for low h The asymmetric properties are discussed also in the following sections Mean flow statistics The mean velocity profiles are presented in Figure In the figure, the profiles of ux are slightly tilted toward the inner cylinder (y/d = 0) showing asymmetric distributions with respect to the gap center For large values of h, the distributions are rather symmetric at any Ret and similar to the mean velocity profile in pPf The peak position shifts to the inner-cylinder side, in particular, for low h As for the Reynolds number effect, the peak of ux does not move so much when Ret decreases from 56 to 52, but both the peak value and the bulk velocity (normalized by ut ) increase noticeably This is because those flows are already in the intermittent state and a decrease in the Reynolds number would expand laminar regions In terms of transitional structures among the helical turbulence and the helical/straight puffs, any significant difference cannot be observed in the ux profiles However, with respect to the decreasing Ret from 80 to 56, the peak position of ux moved toward the gap center (y/d = 0.5) and the asymmetric property is suppressed particularly for low h = 0:1 This implies that the asymmetric property of the core region would be moderated in the transitional regime accompanied by large-scale intermittent structures, while featureless turbulence at a high Reynolds number reveals an asymmetric ux profile due to the aPf geometry Because of this, the ux profile in the transitional aPf even for h = 0:1 is more dissimilar to cPf, in which ux has a peak at y=d = and decreases monotonically with y=d ! However, both flows exhibit straight puffs, as shown in Figure 4(f)–(h) It is interesting to note that the flow statistics including the mean velocity profile in the subcritical regime were dissimilar to cPf, although the flow structure is analogous in both flows For reference, Table assembles the types of dominant transitional structures that are found in each case we focus in this section As seen in the table, Ret = 80 gives rise to the featureless turbulence at any h ( 0:5) Below this Reynolds number, the transitional structure is formed and depends on h At h = 0:1, only the straight puff can be formed, as discussed with Figure However, we have observed the helical shape of structures at h = 0:5 in Figure For (Ret , h) = (56, 0:3), Advances in Mechanical Engineering Table Transitional structure observed in the selected cases The value sets of the parameters (Ret , h) are corresponding to those shown in Figures 8–11 Ret = 80 Ret = 56 Ret = 52 h = 0:5 h = 0:3 h = 0:1 Featureless Turbulence Helical Turbulence Helical Puff Featureless Turbulence (Helical) Puff Straight Puff Featureless Turbulence Straight Puff Straight Puff Figure Root-mean-square values of: (a) streamwise, (b) wall-normal, and (c) azimuthal velocity fluctuations the helical puff seems unstable and might cycle through breakup and reshaping Figure shows the root mean square value of each fluctuating velocity component In Figure 9(a), the streamwise turbulent intensity u0xrms shows asymmetric distributions with two clear peaks near the inner and outer cylinders The difference between the two peaks increases with smaller values of h, and the peak near the inner cylinder is larger than that near the outer cylinder It should be noted that, if scaled with each friction velocity (either uti or uto ), the inner peak of u0xrms =uti is much lower than the outer one of u0xrms =uto (figure not shown here) In a manner dissimilar to the ux , the asymmetricity in a profile is increased at low values of Ret as well as h The two near-wall peaks for the high Ret of 80 exhibit the almost same magnitude At this Reynolds number, the fully turbulent state might reduce the intensity gap between both sides and, as a result, three curves with different h are roughly matched This aspect can be similarly seen in the other components An interesting distribution of u0xrms is observed at Ret = 52 for h = 0.1 and 0.3, and a third peak is observed around the gap center This centerline peak must be attributed to localized (straight) puffs with very large laminar regions, as shown in Figures 4(f) and 5(e) In Figure 9(b) and (c), u0rrms and u0urms indicate skewed profiles with higher peaks near the outer cylinder at a high value of Ret = 80 Given decrease in Ret , the difference between the peaks near the inner and outer cylinder of u0rrms decreases and an almost plateau region is observed around the gap center With respect to this plateau region, we found that the cases in the presence of helical turbulence always provide large u0rrms and u0urms compared to the cases of puff For instance, u0urms for h = 0:5 is 10%–20% larger than that for h 0:3, as given in Figure 9(c) These results suggesting an enhanced turbulent intensity in the helical turbulence are in consistency with the above-mentioned high Cf in the transitional regime A high-value distribution of u0urms near the inner cylinder is the same trend with that of u0xrms for low h Ishida and Tsukahara state Hanks and Bonner16 proposed a picture of the dual flow, that is, the first transition from the innercylinder side, in aPf In contrast, our DNSs have demonstrated no dual flow and shown a less active turbulence near the outer-cylinder wall For h = 0:1, the streamwise localized puff with a large laminar regime led to high fluctuations around the gap center, as discussed in the distribution of ux Conclusion Figure 10 Reynolds shear stress Figure 11 Turbulent energy Figure 10 shows the Reynolds shear stress ( À u0 x u0 r ) The radial position of the zero Reynolds shear stress moves slightly toward the inner cylinder for low values of h, while the zero value for pPf should be located at the center of the gap The zero position shifted to the channel center with a decrease in the value of Ret from 80 to 56, as does the peak position of ux (Figure 8) The zero position approaches the center of the gap even for low values of h with decrease in Ret With respect to the magnitude of Reynolds shear stress, we may detect tendencies similar to those in the turbulent intensity: the larger peak near the inner cylinder for low h, the weakening due to decay from featureless turbulence, and the enhancement by the presence of helical turbulence Figure 11 shows the turbulent energy, denoted by k = (u0 x u0 x + u0 r u0 r + u0 u u0 u )=(2u2t ) As widely known, turbulent motion is vigorous near the wall With respect to the aPf, the turbulence is more activated near the inner cylinder than near the outer cylinder In contrast, the peak of k near the outer cylinder is slightly higher only at the high value of Ret = 80 Therefore, this enhanced turbulent fluctuation near the inner cylinder was prominent when the transitional structure occurred Note again that in terms of normalization by each wall units, the magnitude of k becomes lower on the inner-cylinder side than on the outer side It may imply that the near-wall coherent structure common to plane-wall turbulence may tend to be absent near the inner cylinder, in particular, under the transitional This study on aPfs has investigated the Reynolds number (Ret ) and radius ratio (h) dependencies of the subcritical transition process, friction factor, and turbulent statistics, by means of DNSs The results indicated that the transition process of aPf depended on both Ret and h Clear helical turbulence was observed for high h (h ! 0:5) Even for such a high h, helical puffs emerged in a very narrow range of Reynolds number around Reg In contrast, with respect to low h (h = 0:1), straight puffs similar to those in cPf occurred in low Ret ranges With respect to intermediate values of h (h = 0.2 and 0.3), given decrease in Ret , the transitional structure varied and included helical turbulence, helical puff, and straight puff The occurrence of the transition structures considerably influenced the friction factor Cf and turbulent fraction Ft When the flow regime corresponding to helical turbulence, the friction factor and turbulent fraction maintained a high value that was similar to that for fully turbulent regime However, the friction factor immediately decreased, once the transitional structure was localized in the streamwise direction and formed the helical/straight puff For low h 0:1, only the straight puff was organized independently of Ret , and Cf decreased toward laminar solution monotonically In contrast of this monotonic trend, an overlapping region existed around Reg for intermediate h = 0:2 and 0:3 This non-monotonic trends of Cf and Ft must be caused by the alternations of transitional structures As mentioned above, the shape of transitional structure depended not only on h but also on Ret For h = 0.3, helical turbulence was sustained only in a small range of high Ret , where the intermittent regime occurred With decrease in Ret , the helical turbulence changed into the straight puff through the helical puff Attributed to these alternations of transitional structures for a fixed intermediate h, both Cf and Ft followed two different paths of the helical turbulence and the straight puff The turbulent statistics in aPf corresponded to an asymmetric distributions with respect to the gap center With respect to the streamwise mean velocity ux profile, the asymmetricity was strong when Ret was high and h was small Even for low values of h (h = 0:1), the 10 distributions became symmetric once the transition from featureless to intermittent turbulence occurred The transitional structure for low h was a puff (similar to that in the cPf but different from the oblique pattern in pPf) Hence, in the subcritical regime, it was interesting to note that ux exhibited dissimilarity with the cPf, although the flow structure was analogous for both flows In contrast, the distributions and magnitude of turbulent intensities exhibited complex behaviors The turbulent intensities displayed strong peaks near the inner cylinder with decrease in Ret , whereas the peak near the outer cylinder was higher at high Ret This is due to the difference in the local friction velocity between the outer and inner cylinder, which becomes large significantly after a shift from featureless turbulence to the transitional regime With respect to the transitional regime, the turbulent intensities were enhanced, in particular, when the helical turbulence occurred The third peak appeared around the gap center, when there existed the straight puffs among which large laminar regions emerged Acknowledgements The present simulations were performed on NEC-SX supercomputers at the Cyberscience Centre of Tohoku University and at the Cybermedia Centre of Osaka University Declaration of conflicting interests The author(s) declared no potential conflicts of interest with respect to the research, authorship, and/or publication of this article Funding The author(s) disclosed receipt of the following financial support for the research, authorship, and/or publication of this article: T.I was supported by a Grant-in-Aid from Japan Society for the Promotion of Science (JSPS) Fellowship #267477 This work was partially supported by Grant-in-Aid for Young Scientists (A) #16H06066 from JSPS References Manneville P On the transition to turbulence of wallbounded flows in general, and plane Couette flow in particular Eur J Mech B 2015; 49: 345–362 Manneville P Transition to turbulence in wall-bounded flows: where we stand? 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Heaton CJ Linear instability of annular Poiseuille flow J Fluid Mech 2008; 610: 391–406 10 Ishida T, Duguet Y and Tsukahara T Transitional structure in annular Poiseuille flow depending on radius... (normalized by ut ) increase noticeably This is because those flows are already in the intermittent state and a decrease in the Reynolds number would expand laminar regions In terms of transitional