Turbulent thermal convection over rough plates with varying roughness geometries
Abstract
We present a systematic investigation of the effects of roughness geometry on turbulent RayleighBénard convection (RBC) over rough plates with pyramidshaped and periodically distributed roughness elements. Using a parameter defined as the height of a roughness element over its base width, the heat transport, the flow dynamics and local temperatures are measured for the Rayleigh number range , and the Prandtl number from 3.57 to 23.34 at four values of (0.5, 1.0, 1.9, and 4.0). It is found that the heat transport scaling, i.e. where is the Nusselt number, may be classified into three regimes in turbulent RBC over rough plates. In Regime I, the system is in a dynamically smooth state. The heat transport scaling is the same as that in a smooth cell. In Regimes II and III, the heat transport enhances. When is increased from 0.5 to 4.0, increases from 0.36 to 0.59 in Regime II, and it increases from 0.30 to 0.50 in Regime III. The experiment thus clearly demonstrates that the heat transport scaling in turbulent RBC can be manipulated using in the heat transport enhanced regime. Previous studies suggest that the transition to heat transport enhanced regime, i.e. from Regime I to Regime II, occurs when the thermal boundary layer (BL) thickness becomes smaller than the roughness height. Direct measurements of the viscous BL in the present study suggest that the transition from Regime II to Regime III is likely a result of the viscous BL thickness becoming smaller than the roughness height. The scaling exponent of the Reynolds number with respect to changes from 0.471 to 0.551 when is increased from 0.5 to 4.0, suggesting a change of the dynamics of the largescale circulation. Interestingly, the transition from Regime II to Regime III in terms of the heat transport scaling is not reflected in the scaling with . It is also found that increasing increases the clustering of thermal plumes which effectively increases the plumes lifetime. This leads to a great increase in the probability of observing large temperature fluctuations in the bulk flow, which corresponds to the formation of more coherent plumes or plume clusters that are ultimately responsible for the enhanced heat transport.
Key words:
1 Introduction
Turbulent thermal convection plays very important role in a range of phenomena in astrophysical and geophysical systems, where the underlying surfaces over which convective turbulence occurs are always rough. As an idealised model for the study of turbulent thermal convection in general, turbulent RayleighBénard convection (RBC), where a fluid layer confined between two horizontally parallel plates heated from below and cooled from above, has been studied extensively in the past two decades (for reviews, see e.g. Siggia 1994; Ahlers, Grossmann & Lohse 2009; Lohse & Xia 2010; Chillá & Schumacher 2012; Xia 2013). In terms of equations of motion, there are two control parameters in RBC, i.e. the Rayleigh number and the Prandtl number , where is the applied temperature difference across a fluid layer of height , is the gravitational acceleration constant and , and are respectively the thermal expansion coefficient, the thermal diffusivity and the kinematic viscosity of the working fluid. Any laboratory convection experiments are confined, thus the aspect ratio and the container shape come into the problem. One of the central issues in the study of turbulent RBC is to determine how the response parameters, i.e. the Nusselt number and the Reynolds number , depend on the control parameters, where is a measurement of the system’s heat transport efficiency and quantifies the turbulence intensity. The functional forms of and are usually expressed in terms of power laws:
(1.0) 
A comprehensive review on this issue can be found in Ahlers et al. (2009). It is now generally accepted that there are multiple scalings in the phase space where the bulk flow is in a turbulent state according to the Grossmann and Lohse model for turbulent thermal convection (Grossmann & Lohse 2000, 2001, 2002, 2004).
Besides its fundamental importance in geophysical and astrophysical problems, turbulent thermal convection over rough surfaces is found to be a more effective way to transport heat, which is also useful in practical applications. Heat transport enhancement is observed when the top and bottom plates are rough and the thermal boundary layer (BL) is thinner than the roughness height (Shen, Tong & Xia 1996). The enhancement is later found to be due to more thermal plumes being emitted from the tip of the roughness elements (Du, Tong & Xia 1998).
Although the heat transport is enhanced, the scaling relation between and is found to be insensitive to the plate morphology (Shen et al. 1996; Du et al. 1998). Several later experiments show that the scaling exponents also change in convection cells with rough plates (rough cells hereafter) when compared with observations in convection cells with smooth plates (smooth cells hereafter). Using glass spheres adhered to the bottom plate of the convection cell, the scaling exponent is found to depend on the distribution of the roughness height (Ciliberto & Laroche 1999). For , a scaling exponent of is reported when grooved roughness is distributed on both the plates and sidewall of the convection cell (Roche et al. 2001). A change of the scaling exponent from 0.28 in a smooth cell to 0.35 in a rough cell is observed (Qiu, Xia & Tong 2005). The rough cell used in the experiments of (Qiu et al. 2005) had similar design with the ones used in Shen et al. (1996) and Du et al. (1998).These authors have suggested that the discrepancy between their experiments and those of Shen et al. (1996) and Du et al. (1998) may be attributed to the different constructions and materials of the rough plates. In the earlier experiments, rough plates made of brass were attached on the surfaces the top and bottom smooth plates. While in the later experiment, the roughness elements were directly machined on a piece of copper. In addition to studying the global transport properties of the convection cell, the heat transport properties of individual plates with rough/smooth surfaces were also investigated (Wei et al. 2014). It is found that heat transport property of individual plate differs significantly and depends on the nature of the opposite plate of the same convection cell and the pertaining temperature boundary conditions. By determining the separately for the bottom rough plate and the top smooth plate, a scaling exponent of 1/2 for the rough plate and of 1/3 for the smooth plate are reported (Tisserand et al. 2011).
The effects of roughness elements on the local dynamics of turbulent RBC are also studied. Using flow visualization and nearwall temperature measurements, it is shown that the interaction of the largescale circulation (LSC) and the secondary flow in the grooved region of the rough plate enhances plume emission which leads to the enhancement of heat transport (Du & Tong 2000). The study of local temperature fluctuations suggest that the enhancement of heat transport is determined by the dynamics in the near plate region (Du & Tong 2001). The effects of rough plates on the velocity BL have been investigated very recently (Liot et al. 2016), where it is found that the flow field is very different before and after the heat transport enhancement transition.
Direct numerical simulations (DNSs) of turbulent RBC in rough cells also show that the scaling exponent increases (Stringano, Pascazio & Verzicco 2006; Shishkina & Wagner 2011; Wagner & Shishkina 2015; Toppaladoddi, Succi & Wettlaufer 2015, 2017). The scaling exponent increases to 0.37 in a rough cell with grooved walls at the top and bottom plates when compared with the smooth cell (Stringano et al. 2006). The scaling exponent was also found to depend on the geometry of the roughness elements or “obstacles” in a quasi2D DNS (Wagner & Shishkina 2015). But the number of roughness elements in this study is very limited (only 4 “obstacles” are used). In a 2D study, using sinusoidal rough elements, the scaling exponent is also found to depend on the wavelength of the roughness elements (Toppaladoddi et al. 2015, 2017). In a DNS study of turbulent TaylorCouette flow the scaling exponent is also found to increase with wallroughness (Zhu et al. 2016). These numerical studies imply the importance of roughness geometry on turbulent transport. However, the limited number of roughness element in a 3D or a (quasi) 2D computation domain makes the comparison between the DNS studies and experimental ones less straightforward.
Although there are quite a number of previous experiments studying the effect of roughness on turbulent RBC, to the best of our knowledge no experimental study has been made to systematically varying roughness geometry. This motivates the present study in which the effects of roughness geometry on turbulent RBC have been investigated by systematically varying the roughness geometry. A parameter which is defined as the height of a single roughness element over its base width is used to characterise the geometry of roughness elements. In addition to heat transport enhancement as found by previous studies, we find that the heat transport scaling in a rough cell with fixed roughness height may be classified into three regimes. The experiments further show that can be used as a tuning parameter to manipulate heat transport scaling in rough cells in the heat transport enhanced regime. The Reynolds number and local temperature fluctuation scalings with also change with , suggesting that the geometry of roughness elements not only alters the global heat transport of the system but also influences the bulk turbulence and the dynamics of the LSC.
The remainder of the paper is organised as follows: The experimental setup and measurement techniques are introduced in §2 which is divided into four subsections. The construction of the convection cell is described in §2.1. The properties of the working fluids used and the explored phase space are introduced in §2.2. The temperature measurement techniques are documented in §2.3, and §2.4 introduces the measurement of the viscous BL using particle image velocimetry (PIV). §3 presents the experimental findings. The heat transport measurements for different values of are reported in §3.1. The transitions between different heat transport regimes are discussed in §3.2. The Reynolds number and local temperature fluctuation measurements are presented in §3.3 and §3.4, respectively. A discussion of the proper parameter that characterises the system is reported in §3.5 before we summarise and conclude our findings in §4.
2 Experimental setup and measurement techniques
2.1 The convection cell
The experiments were carried out in four cylindrical convection cells. Each of the convection cells consisted of top and bottom plates and a Plexiglas sidewall. Except for the geometry of roughness elements on the top and bottom plates, the constructions of the convection cells were otherwise identical.
The sidewall was made of Plexiglas tube with a wallthickness of 4 mm. The convection cells had a diameter of 19.2 cm and a height of 20.3 cm measured from the base of the roughness elements. Thus the aspect ratios of the convection cells were approximately unity. The top and bottom plates were made of 12 mmthick copper except for the ones for rough cell with which were made of aluminium. The thermal conductivity of aluminium is 205 W/(mC) at temperature 25 C, which is roughly half that of copper. The differences in heat transport properties in convection cells with plates made of copper and aluminium, i.e. the effects of finite conductivity of plates (Verzicco 2004; Brown et al. 2005), have been shown to be minimal in the and range reported in the present studies (Wei, Ni & Xia 2012). The pyramidshaped roughness elements were directly machined on the top and bottom plates that were then plated with nickel to prevent oxidation. The roughness elements were arranged in a square lattice form (see figure 1), which was the same as those used previously (Wei et al. 2014; Xie et al. 2015). By keeping the height of roughness elements a constant at 8 mm and changing the base width of individual roughness elements from 16 mm to 2 mm, rough plates with roughness parameter , defined as the ratio of and , at 0.5, 1.0, 1.9 and 4.0 were used in the experiments. With the increase of , the number density (in unit of number of roughness element per cm) also increases, i.e. = 0.38 (), 1.5 (), 6.1 (), and 24.5 (). To clarify whether the number density or the is the key parameter that characterizes the system, another sets of rough plates with = 4.0 and a roughness height of 4 mm were used. The present study implies that is a more suitable parameter to characterise the geometry of the roughness elements and the response of the system, rather than the number density of the roughness elements.
The top plate was cooled by passing temperaturecontrolled water from a water bath (Poly Science, 9702) through a chamber fitted on its top. The cooling water entered the chamber through two inlets and left the chamber through two outlets. The arrangements of the inlets and outlets were such that the two inlets were along one diameter of the plate and the two outlets were along another diameter perpendicular to the inlets. Temperature stability of the cooling water was better than 0.01 C. A stirring blade driven by the inlet and outlet flows was installed inside the cooling chamber to ensure temperature uniformity across the top plate. The bottom plate was electrically heated by two rubber heaters connected in series and sandwiched in between the bottom plate and a copper plate with a thickness of 10 mm (see, e.g. figure 1). The heaters were connected to a DC power supply with a long term voltage stability of 99.99% (Sorensen, XFR3004). To ensure good thermal contact, a thin layer of thermally conductive paste was used between the heaters and the plates. The largest temperature difference within the same plate was about . It should be noted that under this arrangement, the temperature boundary condition for the top plate was constant temperature and that for the bottom plate was constant heat flux.
To prevent heat leakage and to minimise the influence of the environmental temperature fluctuation, the convection cells were wrapped with Styrofoam with a thickness of 6 cm. A temperature regulated copper basin was placed beneath the convection cell to prevent heat leakage from the bottom plate of the convection cell by maintaining the same temperature at the top and bottom of the basin. The whole set up was put into a thermostat where the temperature was regulated to match the mean temperature of the top and bottom plate. The temperature stability of the thermostat was better than 0.1 C.
2.2 The working fluids
Only about one and a half decades of can be achieved in a single experimental setup using classical working fluid like water. To extend the range, two kinds of working fluids, namely deionized water and Flourinert FC770 (FC770 hereafter, 3M Inc.) were used. Water has been widely used in the study of turbulent convection, we will mention here only the properties of FC770. The data listed below are given by the manufacturer (3M Inc.) and are all obtained at the temperature C. The FC770 has = 0.063 W/(mC), = 0.00148/C, m/s, the specific heat 1038 J/(kgC), and the density = 1793 kg/m.
The working fluid was filled into the convection cell through a hole attached with a stainless steel tube ( 8 mm in diameter) located at the centre of the top plate. The working fluids were degassed in the following way to ensure there was no bubble forming during a single run of the experiment, which typically lasts for three weeks. Deionized water was boiled for a hour and then cooled down to room temperature before filling into the convection cell. For FC770, it was first filled into the convection cell and degassed by keeping the temperature of the top and bottom plate, and thus the whole convection cell, at C for 24 hours. Then the temperature of the convection cell was lowed to C which was the for all the experiments using FC770, and the bubbles formed were totally removed.
The explored and phase space at different values of is shown in figure 2. Except for which was investigated for a single (23.34) in the present studies, all the other values of were studied for the four values of , i.e. = 3.67 (water, C), = 4.34 (water, C), = 6.14 (water, C), and = 23.34 (FC770, C). The experiments covered . The temperature difference applied across the convection cell using water as the working fluid for different values of were: 0.98 C to 26.99 C (); 0.47 C to 20.16 C () and 0.89 C to 24.75 C (). The temperature difference applied using FC770 as working fluid at different values of were: 1.40 C to 22.14 C (); 0.99 C to 17.25 C (); 1.11 C to 27.63 C () and 0.96 C to 29.66 C ().
2.3 The temperature measurements
Temperature of the top plate was measured using four thermistors (Omega, Model 44031) embedded at a distance of from the centre of the plate and uniformly in the azimuthal direction. Four thermistors at the mirror location of the top plate embedded in the bottom plate with one additional thermistor at the centre were used to measure its temperature. The thermistors were calibrated individually and separately in a temperature controlled water bath. The temperature range of calibration was from 5 C to 70 C with a temperature accuracy better than 0.01 C. The resistances of the thermistors were measured using a digital multimeter (Keithley, 2700) and were converted to temperature using the calibration curve. The sampling rate of the temperature measurement was 0.7 Hz.
Local temperatures at the cell centre and 1 cm away from the sidewall were measured using two small thermistors with a bead diameter of mm and a time constant of 30 ms in liquid (Measurement Specialities, Model: G22K7MCD419). These small thermistors had a temperature accuracy of 0.01 C. They were guided into the convection cell using a stainless steel tube with an outer diameter of 1.1 mm and wall thickness of 0.2 mm (Goodfellow, Stainless Steel  AISI 304 Tube). Each of the small thermistors had an independent temperature measurement system specially designed to measure the temperature fluctuation. Detailed design of the measurement system can be found in Zhou & Xia (2001). Briefly, the thermistor acted as one arm of a AC Wheatstone electrical bridge. The resistance fluctuations of the thermistor induced by the temperature fluctuations in the convection cell were converted to the voltage fluctuations of the electrical bridge which were magnified using a lockin amplifier (Stanford Research System, SR830). The output signal from the lockin amplifier was then digitised and stored by a dynamic signal analyser (HP, 35670A). The measured voltage was converted to resistance and then to temperature using the calibration curve of the thermistors. The sampling rate of the local temperature varied from 16 Hz to 128 Hz depending on and to ensure that the small scale temporal temperature fluctuations were fully resolved.
From the temperature measurements, the heat transport across the convection cell, i.e. the Nusselt number , local temperatures, and the Reynolds number were measured as a function of , and , where was the input heating power at the bottom plate, was the thermal conductivity of the working fluid and was the characteristic velocity of the LSC. Each measurement lasted at least 12 hours after the system had reached a stable state to ensure that the system had explored all flow states.
2.4 The viscous boundary layer measurements
The dynamics of viscous boundary layer in the rough cell with was measured using a commercial particle image velocimetry (PIV) system that had been documented elsewhere (Xia, Sun & Zhou 2003). The flow was seeded with particles with a diameter of 2 m and density matched with water. A 2D flow region with a size of 20 mm 28 mm was measured within the LSC’s circulation plane with denoting the direction along the circulation path of the LSC and denoting the direction pointing upwards at the centre of bottom plate (see, e.g. figure 7). The origin of the coordinate system was located at the centre of the plate. To minimise optical distortion of the particle images induced by the curved surface of the cell, a jacket filled with water with flat window was adhered to the convection cell. The optical arrangement was such that the measurement plane was within one groove of the rough plate and the images were acquired perpendicular to it. A mask with the shape exactly matching that of the plate geometry when viewing from the front was applied to the measured images to exclude the parts blocked by the roughness elements in the captured images.
The velocity field was obtained by crosscorrelating two consecutive images taken with a time separation that matches the velocity of the flow at different . The velocity map consisted of 63 79 vectors in the and directions respectively. Totally 26136 vector maps were acquired at a sampling rate of 2.2 Hz, which lasts for hours. The velocity fluctuation map was obtained by subtracting the mean velocity map from each of the instantaneous velocity map. The measurements were done at and . To lock the direction of the LSC, the convection cell was tilted with respect to the vertical direction by .
3 Results and discussion
3.1 Heat transport measurements
We show in this section that the heat transport in turbulent RBC over rough plates may be classified into three regimes based on the scaling law of vs. . In addition, the heat transport scaling in the enhanced regime (Regimes II and III) can be manipulated by changing the roughness geometry. The transition from Regime I to Regime II in a rough cell with = 4 mm and is discussed in section §3.1.1. The heat transport measurement with changing the geometry of roughness elements, i.e. for different values of , is presented in §3.1.2 together with the observation of Regime II and Regime III.
3.1.1 Transition from Regime I to Regime II
Previously, Shen et al. (1996) find that the heat transport cannot be altered in a rough cell if thermal BL thickness is larger than the height of the roughness elements. We call this Regime I of convective turbulence in a rough cell. As decreases with increasing , it will eventually become smaller than the roughness height, i.e. . When this happens turbulent convection enters a new, heat transport enhanced regime, termed Regime II here. This regime has been observed by a number of previous experiments (Shen et al. 1996; Du et al. 1998; Qiu et al. 2005; Tisserand et al. 2011; Wei et al. 2014).
We plot in figure 3() as a function of in a rough cells with mm and . For comparison, the data from Funfschilling et al. (2005) in a smooth cell with , from Wei et al. (2014) in a smooth cell with and from Sun et al. (2005) in a smooth cell with are plotted respectively as downpointingtriangles, hexagons and stars. Figure 3() plots the corresponding data in a compensated form. It is seen that in the rough cells first overlaps nicely with those from the smooth cells for . With increasing , there is a gradual transition, where the heat transport enhances. Within the transitional range , there is no well defined scaling law between and . For , the data shows a powerlaw relation, i.e. . These data clearly demonstrate the transition from Regime I to Regime II. Such a transition is also observed by Wei et al. (2014) in a rough cell with mm. Using the relation (which was valid only for the platewise averaged thermal BL thickness and for a smooth cell), we had mm at , which might be considered to be close to the roughness height of 4 mm in an order of magnitude sense and broadly consistent with the proposed interpretation by Shen et al. (1996).
3.1.2 Effects of roughness geometry on the heat transport enhanced regime
We present measurements of as a function of in convection cells with a roughness height of 8 mm and different roughness geometries in this subsection. The roughness height was much larger than for the explored range of . Therefore, Regime I behaviour was not observed here. Instead, we focus on Regime II and Regime III (a new regime to be defined below).
Figures 4() show as a function of and in rough cells with and 0.5, respectively. The solid lines in the figure are power law fit to each data set for larger and smaller than a critical Rayleigh number . The same data from smooth cells as shown in figure 3 are shown in these figures. The general conclusion that one can draw from these figures is that the heat transport is enhanced in rough cells.
We first discuss the case with (figure 4()). Within the precision of the experiments, data at different values of but the same collapse onto each other, suggesting that the dependence in the rough cell with is very weak in the present parameter range, which is consistent with observation in a smooth cell (Xia, Lam & Zhou 2002). Detailed examination of the data shows that there is a transition of the scaling at . Below and above , the data can be fitted by different scaling laws, i.e. and . The different scaling laws suggest that the heat transport enhancement regime in a rough cell can be further classified into two regimes for the range covered in the present experiments. We term the two regimes before and after as Regime II and Regime III. The data are compensated by the scaling exponents in Regimes II and III and shown in figure 4(). A gradual transition around is clearly seen.
Data at and 0.5 are plotted in figure 4 (). One interesting feature revealed in figure 4() and () is that the at is larger than that at when is the same. We note that this enhancement for FC770 (), as compared to water (), only occurs for the large cases. In fact, for the smallest value of () there is a slight decrease in . This is quite surprising and unexpected, as in the case of a smooth cells, is peaked around (Xia et al. 2002). It is not clear why the heat transport enhancement in rough cells has this peculiar dependence, and furthermore this behaviour has a strong dependence, i.e. its 150% for , 134% for , 4% for , and 8% for . One possible reason leading to such a abnormality is that the lifetime of the thermal plumes at larger is larger compared to the small case. Assuming that the thermal plumes have typical length scale comparable to the thermal BL thickness, the estimated thermal diffusion time scale, i.e. , for FC770 is 14.5 sec and that for water is 2.6 sec at . When normalised by the LSC turnover time, the dimensionless plume lifetime for FC770 is 0.25 and that for water is 0.11 for . Another likely reason is the stronger plume clustering effect in rough cells with larger as shown by the shadowgraph images in figure 16, which also has the effect of increasing plume lifetime or slowing the decay of plumes. While it is difficult to quantify the combined effect of these two factors, it appears that larger values of together with a larger result in a more efficient enhancement in the heat transport. For small and/or small , thermal plumes lose more heat to the surrounding fluid and therefore won’t be enhanced as much.
To determine more accurately the scaling law of vs. , the data at in figure 4() and () are shifted downwards by a constant, i.e. 1.50 in () and 1.34 in (), to collapse data at different but the same . The transition of the heat transport scaling around is observed for all studied. The power law fits of in Regimes II and III for different values of are summarised in table 1. It should be noted that the shifted high data were included in the fitting. Since obtained using water as working fluid at and that using FC770 as working fluid at had an overlapping range of less than a half decade, i.e. from to , a determination of the dependence in Regime III was not possible in the present experiments. It is seen that the heat transport law is distinctively different in Regime II and Regime III. This can be seem more clearly from the compensated plot in the right panel next to figure 4(.
The experimentally determined scaling exponent , i.e. , in both Regime II and Regime III increases significantly with . In Regime II, the increases from 0.36 to 0.59 when is increased from 0.5 to 4.0; and in Regime III, it increases from 0.30 to 0.50. These data are plotted in figure 5. If a power law fit is attempted to these data within the limited range of , we obtain and which are shown as solid lines in the figure. Within the error bar, the dependences of and are the same except that the prefactor of is larger than . The results suggest that the scaling law of the heat transport in turbulent RBC over rough plates can be manipulated using . In this sense, the present experiments demonstrate clearly the importance of roughness geometry on turbulent heat transport. Any realistic model for turbulent thermal convection in nature should take into account the effects of wall roughness.
Very recently, it is found that there is an upper bound for the heat transport in turbulent convection over rough plates, i.e. cannot grow faster than in the limit of (Goluskin & Doering 2016). With increasing , Regime II is just a transient, and Regime III is the dominated one. Our experiments showed that at the scaling exponent already reached 0.50, which was consistent with the upper bound derived (Goluskin & Doering 2016). One interesting question is whether the scaling exponent will saturate to 0.50 with further increasing which is very challenging to achieve experimentally due to technical difficulties in machining the plates. DNS studies may provide helpful insights into this aspect of the problem.




4.0 

1.9  
1.0  
0.5 
We next study the dependence of the heat transport enhancement behaviour in Regime II and Regime III. Figure 6 shows the heat transport enhancement in rough cells compared with that in a smooth cell. It is seen that the heat transport enhancement in Regime II (open symbols in figure 6) first increases and then decreases with increasing . The situation is very different in Regime III (solid symbols in figure 6) where it is found that the heat transport enhancement increases monotonically with increasing . A maximum heat transport enhancement of 637% is observed at .
We note that in a DNS study, Wagner & Shishkina (2015) show that the heat transport is enhanced more for slender roughness elements, i.e. larger , using only four roughness elements with a roughness height of 0.125H (“obstales” in Wagner & Shishkina (2015)) in a quasi2D convection cell. The observation in Wagner & Shishkina (2015) is qualitatively in agreement with what we find here, e.g. heat transport enhancement generally increases with (see e.g. figure 6).
3.2 Transition from Regime II to Regime III: The viscous boundary layer crossover
To understand what may have happened at , i.e. the transition from Regime II to Regime III, we recall that there are two BLs in turbulent RBC, i.e. the thermal BL and the viscous BL. The viscous BL is thicker than the thermal BL for . According to the GrossmannLohse model for turbulent RBC, BLs play crucial role in determine the global heat transport (Grossmann & Lohse 2000). The transition seen in figure 4 may be understood in terms of the viscous BL crossover, i.e. the roughness elements not only strongly perturb the thermal BL, but also alter the viscous BL in Regime III. To verify this, we directly measured the dynamics of the viscous boundary layer in a rough cell with .
An example of the instantaneous velocity map measured at and is shown in figure 7(). The triangles outline the space occupied by the roughness elements schematically. The velocity magnitude is coded by both the colour and the length of the vectors. The instant velocity field shows that the mean flow is going from the right to the left and there are intermittent bursts of the flow velocity. Figure 7() depicts the time averaged velocity field with the velocity magnitude coded also in both colour and the length of the vectors. One may notice that the timeaveraged maximum velocity magnitude is significantly reduced when compared with the instantaneous one as revealed by the scale bars. After averaging over time one sees that the mean velocity is uniform with respect to except very close to the plate, e.g. in between the roughness elements. A tiny counterrotating vortex may be identified in the region 8 mm 5 mm and 0 mm 4 mm. The mean velocity field varied weakly with (figure 7()). We thus averaged the mean velocity field along direction to obtain the mean velocity and the rootmeansquare (rms) velocity profiles.
Figure 8() shows an example of the horizontal mean velocity profile and the profile of the rms velocity measured at and . A remarkable feature shown in figure 8() is that the rms velocity is comparable to the mean velocity very close to the plate, and it’s even larger than the mean velocity within the viscous BL. The origin of the enhanced velocity fluctuation is not clear but speculatively this should largely correlate with the intermittent bursts of thermal plumes. In contrast, the maximum rms velocity in a smooth cell is only about 30% of the maximum mean velocity and it is always smaller than the mean velocity within the boundary layer region (Sun, Cheung & Xia 2008; Wei & Xia 2013).
The viscous boundary layer thickness was determined using the socalled slope method: The intersection between the extrapolation of the linear part of the velocity profile very close to the plate and the maximum mean horizontal velocity was defined as the thickness of the viscous boundary layer (indicated by the vertical dashed line in figure 8()) (Xin et al. 1996; Xin & Xia 1997; Qiu & Xia 1998; Sun et al. 2008; Wei & Xia 2013). The dependence of the viscous BL thickness normalised by the height of the convection cell is plotted in figure 8(). With increasing , becomes thinner and thinner. At , approximately equals to . This roughly corresponds to seen in the measured (. This observation indicates that the transition of the heat transport law between Regimes II and III may be caused by the viscous BL becoming smaller than the height of the roughness elements. After this viscous BL crossover, the roughness elements strongly perturb both the thermal and the viscous BLs. The thermal plumes emitted from the tip of pyramids can then be directly ejected into the bulk. For , the estimated viscous BL thickness at the smallest explored in the experiments () was 0.04H (Lam et al. 2002), which was very close to the height of roughness element, implying that the measurements with were all in Regime III.
In the asymptotically large limit, the thickness of the BLs is so small such that the roughness elements perturb both the thermal and the viscous BLs. The system is in Regime III in this case wherein is very sensitive to the LSC, or equivalently to the Reynolds number associated with the LSC (to be defined in section 3.3). We plot in figure 9 as a function of for () = 23.34, () = 6.14, () = 4.34, and () = 3.57. On one hand, figure 9 () shows that increases with for all measured at , which are in the Regime III. On the other hand, at other where mostly within the Regime II shows weak dependence on . This is another evidence supporting that the viscous BL crossover may also play important role in turbulent thermal convection with the presence of roughness elements.
3.3 Reynolds number measurements
The selforganised largescale circulation (LSC, or “wind of turbulence”) is one of the fascinating features of turbulent RBC. The flow dynamics of the LSC is characterised by the associated Reynolds number . We study in this section how the roughness geometry alters the dynamics of the LSC by examining the dependence on both and . It has been wellknown that there exits a welldefined lowfrequency oscillation in turbulent RBC. The time scale of this oscillation is interpreted as the turnover time of the LSC (see, e.g. Xie, Wei & Xia (2013) and references therein). By choosing a typical length scale of the LSC, e.g. 4H, the Reynolds number is calculated as:
(3.0) 
Timeresolved temperature signals measured cm away from the sidewall were used to determine and thus the as a function of and when changing the roughness geometry, i.e. at different values of . The turnover time of the LSC was determined by locating the time position of the first peak of the temperature autocorrelation function , which is defined as:
(3.0) 
where denoted timeaveraging and is the rms temperature. An example of the autocorrelation function measured in convection cell with at and is depicted in figure 10. Clear oscillations can be seen from . Fitting the data points nearby the first peak of with a six order polynomial, the time location of the first peak was determined and denoted as . The uncertainty of was from s to s with increasing .
Figure 11 displays as a function of and in rough cells with (), (), () and . Let’s first discuss the case for . The as a function of for and are plotted in figure 11() on a loglog scale. The exhibits power law dependence on at different , i.e. . To determine more precisely , data at = 3.57, 4.34 and 6.14 were multiplied by a dependent constant to collapse them with data at onto a single line. The shifted data are shown in the main plot of figure 11(). A power law fits to the data over almost three decades of yielded: . The dependence of was then divided out by compensating the data in figure 11() with the sodetermined power law, e.g. the inset of figure 11(). Within a relatively limited range of , the data was also described by a power law, i.e. . The sodetermined was:
(3.0) 
Applying the same procedure to data obtained in rough cells with (figure 11()), (figure 11()), and (figure 11()), we determined the and dependence of for each values of , respectively. The scaling laws of for different values of are summarised in table 1.
On one hand, with increasing from 0.5 to 4.0 the scaling exponent , i.e. , increases from 0.472 to 0.551, which is plotted as a function of in figure 5. The data may be described by an empirical power law within very limited range of , i.e. . On the other hand, the scaling exponent , i.e. , remains at the same value around within experimental uncertainty except for . Whether there is a change of the dependence of in the rough cell with requires future investigation with a wider range of . The change of with suggests a change of the LSC dynamics when the geometry of the roughness elements is changed. It is thus interesting to study torsional and sloshing oscillations of the LSC dynamics in rough cells with different values of as those done in a smooth cell (Funfschilling & Ahlers 2004; Xi et al. 2009; Xie et al. 2013). This is beyond the scope of the present studies and will be investigated in the future. Interestingly, the transition of the heat transport scaling law from Regime II to Regime III is not observed in the Reynolds number measurement.
It is found very recently that is insensitive to the plate morphology for a given input heat flux for and 0.5 (Wei et al. 2014), i.e. when is plotted against the flux Rayleigh number , data at different values of collapse. We plot as a function of for different values of and in figure 12. The data at the same but different indeed overlap onto each other which is in agreement with the observation in Wei et al. (2014), but now for a wider range of and . In addition, data at the same can be fitted by a power law, i.e. , , , and . The scaling exponents of these power laws fits are the same within experimental uncertainty but the magnitudes decrease with .
3.4 Local temperature fluctuations
Since Regime II is a transitional state, we focus on temperature fluctuations measured in Regime III only. To simplify the analysis, we don’t take into account the effects of and limit the analysis to measurements done in FC770 only (=23.34). The results may shed light upon the mechanism leading to the change of the heat transport scaling in rough cells with different roughness geometries in Regime III.
The probability density function (PDF) of the standardised temperature measured at at four different values of at the cell centre and sidewall are displayed in figure 13 () and () respectively, where is the rms temperature that is shown as a function of in figure 13 () and () at the cell centre and sidewall. It is seen that the PDFs at different overlap onto each other very nicely at the cell centre, suggesting that the bulk turbulence shares the similar dynamics at different values of . A notable feature seen in figure 13 () is that the PDFs are significantly skewed toward the negative side, i.e. more cold plumes are detected in the cell centre than hot ones. This feature hasn’t been observed either by us or reported by others in smooth cells with the same boundary conditions, i.e. constant temperature at the top boundary and constant heat flux at the bottom boundary. Thus, the reason for this phenomenon remains unknown to us at present. At sidewall, the shapes of the PDFs remain approximately invariant with except the case with . For measurements with the thermistor was sopositioned such that the upwelling hot plumes of the LSC were detected, while for the other cases the downwelling cold plumes of the LSC were detected. The positive tails of the PDFs overlap well onto each other while the negative tails, especially those larger than , change with . The rms temperature at the cell centre increases considerably with as can be seen from figure 13(), and that at the sidewall first remains almost the same for =0.5 and 1.0 and then increases with as well. As the large temperature fluctuations are caused by thermal plumes, this observation suggests a change of the plume dynamics with increasing .
The Rayleigh number dependence of normalised rms temperatures for different values of measured at the cell centre and near the sidewall are shown in figure 14() and (), respectively. With increasing , enhances considerably. The changes lie not only in the magnitudes but also the scaling exponents with . The scaling exponents of the power law fits, e.g. , are displayed nearby each data set in figure 14() and () and the scaling laws of each data set are summarised in table 1. The scaling exponent increases from 0.16 to 0.09 with increased from 0.5 to 4.0 in the cell centre. For comparison, Wei & Ahlers (2016) obtained an exponent of 0.17 in the centre of a smooth cell for a comparable ( = 12.3). With a possible dependence of the temperature fluctuation unknown at the present, the experimental results suggest that the dependence of the temperature fluctuation at the cell centre becomes stronger with increasing . Near the sidewall, the scaling exponent increases from 0.23 to 0.08 in the range covered in the experiments, suggesting a weakened dependence of temperature fluctuation on at the sidewall. To the best of our knowledge, there has been no report on the smoothcell value for this exponent in the similar range near sidewall.
To gain further insight into the dynamics of temperature fluctuations with increasing , we examine the PDFs of the normalised temperature deviation from the mean for different values of at at the cell centre and the sidewall respectively, as displayed in figure 15() and (). The figure reveals that large events are becoming more probable with increasing at the same , i.e. hotter and colder plumes, suggesting that the effects of changing roughness geometry are to modify the dynamics of thermal plumes and make them more coherent and energetic (therefore decay slower). This is also supported by the shadowgraph visualisation of the flow field, such as those presented in figure 16. These images are taken at and 23.34. It is seen that, with increasing , both the density and the morphology of the thermal plumes change drastically. In the smooth cell there is a welldefined LSC with few thermal plumes passing through the cell centre (figure 16()). In the rough cell with , more thermal plumes are passing through the cell centre (figure 16()). In the rough cell with , thermal plumes occupy almost all the space in the convection cell (figure 16()). Furthermore, the plumes are now packed (or clustered) much more densely. This will result in their slower decay through thermal diffusion, which explains why it is now much more probable to find large temperature excursions in the cell centre (figure 15()).
To quantitatively understand the change of the dynamics of thermal plume, we extract time series of thermal plume amplitude and width using the timeresolved temperature data measured near sidewall. The detailed plume extraction method can be found in Zhou et al. (2016). The normalised timeaveraged plume amplitude and normalised timeaveraged plume width are shown in figure 17() and () respectively. Figure 17() reveals that with the increase of , the plume amplitude increases. The solid lines are power law fits to the data at different values of with the scaling exponents listed nearby each data set. The scaling exponent of plume amplitude increases from 0.386 to 0.266 with increasing from 0.5 to 4.0. In contrast, the dependence of the plume width remains almost the same with a scaling exponent around 0.25 for smaller than 4.0. It should be noted that the scaling exponent of plume width for increases considerably (0.341) when compared with other values of , which may be correlated with the drastically changed plume dynamics and morphology in rough cell with . As the thermal plumes are main heat carriers in turbulent RBC, the experiments suggest that the change of plume dynamics may lead to the change of the scaling law of heat transport for different values of .
3.5 A proper parameter characterising the system: vs number density of roughness elements
When varying the number density of roughness elements also varies, i.e. . In fact, the two parameters have onetoone correspondence provided that the ratio of the roughness element height to the cell height and are fixed, which is the case for the present study. To figure out whether is the most relevant parameter that characterises the system, we carried out another experiment, in which was kept constant at 4.0 and the height of the roughness elements was halved. Thus the number density of the roughness elements is increased by a factor of 4.
We show in figure 18() as a function of for measurements in = 4.0 rough cells with mm and mm together with the same smooth cell data which have be shown in figure 3 and figure 4. The estimated viscous boundary layer thickness at the highest reached in the experiment is 4.8 mm. Thus, the measurements at and mm are in Regime II. A scaling exponent = 0.60 is observed in rough cell with mm in Regime II, which is consistent with 0.59 observed in Regime II of rough cell with 8 mm, which is indicated by the two parallel lines in figure 18. The similar dependence of in Regime II in rough cells with = 4 mm and 8 mm can be seen more clearly from the compensated plot in figure 18(). These observations suggest that is not only a suitable parameter describing the geometry of the pyramidshaped roughness elements, but also a suitable parameter to characterise the response of turbulent RBC over rough plates with different roughness geometries.
A noticeable feature from figure 18() is that the measured in the rough cell with 8 mm is larger than that in the rough cell with 4 mm in Regime II despite the fact that they have similar dependence. This may be explained by the measured Reynolds number based on the circulation time of the LSC as plotted in figure 19. It is seen that in the rough cell with mm is larger than that in the rough cell with 4 mm, which is true for both 4.34 and 23.34. The result suggests that a faster LSC can transport heat more efficiently cross the convection cell.
4 Conclusion and outlook
We studied systematically in this paper the effects of roughness geometry on the global heat transport, the flow dynamics and the local temperature fluctuations in turbulent RayleighBénard convection over rough plates. The experiments were carried out in rough cells with pyramidshaped roughness elements directly machined on the top and bottom plates. We defined a parameter (the height of the roughness element over its base width) to characterise the geometry of the roughness element and to analyse the observed scaling behaviour of and , where and are respectively the Rayleigh number and Prandtl number, and are respectively the Nusselt number and Reynolds number. We varied from 0.5 to 4.0 by keeping the roughness height at a constant of 8 mm and changing the base width from 16 mm to 2 mm. In addition, a rough cell with 4 mm was used. The experiments covered Rayleigh number and from 3.57 to 23.34.
It is found that the heat transport is enhanced significantly by roughness elements, and the enhancement depends strongly on the roughness geometry. It is also found that the heat transport scaling, i.e. , may be classified in to three regimes in turbulent RBC over rough plates. In Regime I, the system is in a dynamically smooth state. The heat transport scaling in a rough cell is the same as that in a smooth cell in this regime. In Regimes II and III heat transport enhances. The scaling exponents of vs. increase from 0.36 to 0.59 with increased from 0.5 to 4.0 in regime II. It increases from 0.30 to 0.50 in Regime III with increased from 0.5 to 4.0. The experiment thus clearly demonstrated that the heat transport scaling in turbulent RBC could be manipulated using in Regimes II and III. The transition from Regime I to Regime II may be understood in terms of the thermal boundary layer thickness becoming smaller than the roughness height with increasing as suggested by a number of previous studies (Shen et al. 1996; Du et al. 1998; Ciliberto & Laroche 1999; Roche et al. 2001; Tisserand et al. 2011). The transition from Regime II to Regime III may be understood in terms of viscous boundary layer crossing, i.e. the viscous BL thickness becomes thinner than the height of the roughness elements, as shown by direct measurement of the viscous boundary layer profiles in the present study. When this happens, the thermal plumes emitted from the tip of the roughness can be directly ejected into the bulk flow. An unexpected effect in turbulent RBC over rough plates was also observed: Larger heat transport enhancement was observed for larger values of and larger . This may be correlated with the strong clustering of thermal plumes as clearly seen from the shadowgraph visualization of the flow field (figure 16).
The Reynolds number is measured based on the turnover time of the largescale circulation evaluated near the sidewall of the cells. Both the and dependence of were studied for different roughness geometries, i.e. . The scaling exponent increased from 0.472 to 0.551 with increasing from 0.5 to 4.0. and remained at the same value around except for the case of (). With a limited range of , a truly increased for was not for assertion. Consistent with the observation in Wei et al. (2014), it is found that is insensitive to the plate morphology for a fixed flux Rayleigh number, i.e , but now with a wider range of and as compared with the experiment of Wei et al. (2014).
Timeresolved local temperatures at the cell centre and sidewall were measured using two small thermistors. The probability density functions (PDFs) of the standardised temperature ( in the cell centre remain almost invariant with respect to . The measured local temperature fluctuations at both the cell centre and sidewall increase considerably with . The scaling exponent of the normalised rms temperature (/) with increases from to at the cell centre and from to at the sidewall with increased from 0.5 to 4.0. By extracting thermal plume amplitude and width using a method described in Zhou et al. (2016), it is found that both the plume amplitude and width increase with . The scaling exponent of plume amplitude increases from 0.386 to 0.266 with increasing from 0.5 to 4.0. The scaling exponent for the plume width remains at the same value around 0.25 except for the case of which is 0.34. As thermal plumes are the main heat carriers in turbulent RBC, the experiments suggested that that the change of thermal plume dynamics might be a possible reason leading to the change of the scaling laws between and in Regime III.
The experiments demonstrated that the heat transport behaviour in turbulent thermal convection can be manipulated using a roughness parameter that characterises the geometry of the roughness elements. It further showed that the flow dynamics and local temperature fluctuations are also altered by roughness geometry. There are several open questions: What is the effects of on the dynamics of the largescale circulation, e.g. twisting/sloshing oscillation, flow cessation/reversal? How will the vertical mean and variance temperature profiles change with ?
Finally, we remark that the 0.5 scaling exponent observed for = 4.0 in Regime III reminds one of the Kraichnan ultimate regime of turbulent convection (Kraichnan 1962). Whether Regime III for 4.0 really corresponds to the Kraichnan regime needs further investigations. The place to look would be the boundary layer, i.e. a truly turbulent boundary layer should be the ultimate test for the Kraichnan regime. A very recent DNS study suggests roughness may be used as a route to trigger the transition to the ultimate state of turbulent convection (Toppaladoddi et al. 2017). If this is indeed the case, then the dynamics of turbulent convection in the Kraichnan regime may be studied in a Rayleigh number range that is accessible using classical fluids like water in a table top experiment.
Acknowledgments
We thank YuHao He for help with the experiment. This work is supported by the Hong Kong Research Grants Council under grant Nos. CUHK1430115 and CUHK404513.
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