Conductive and convective heat transfer in fluid flows between differentially heated and rotating cylinders

Conductive and convective heat transfer in fluid flows between differentially heated and rotating cylinders

Abstract

The flow of fluid confined between a heated rotating cylinder and a cooled stationary cylinder is a canonical experiment for the study of heat transfer in engineering. The theoretical treatment of this system is greatly simplified if the cylinders are assumed to be of infinite length or periodic in the axial direction. In these cases heat transfer in the laminar regime occurs only through conduction as in a solid. We here investigate numerically heat transfer and the onset of turbulence in such flows by using both periodic and no-slip boundary conditions in the axial direction. The influence of the geometric parameters is comprehensively studied by varying the radius ratio () and the length-to-gap aspect ratio (). Similarly, a wide range of Prandtl, Rayleigh, and Reynolds numbers is explored (, , and , respectively). We obtain a simple criterion, , which determines whether the infinite-cylinder assumption can be employed. The coefficient is well approximated by a cubic fit over the whole -range. Noteworthy the criterion is independent of the Prandtl number and appears robust with respect to Reynolds number even beyond the laminar regime.

keywords:
Taylor–Couette, radial heating, end walls, heat transfer
1

1 Introduction

Instabilities driven by the combination of rotation and thermal gradients determine the dynamics of complex geophysical, astrophysical and industrial flows. Simple models of such flows can be tested in laboratory experiments of a laterally heated differentially rotating annulus, for which extensive information about the physical mechanisms and flow regimes can be found in the literature (see La12 () for a review on this topic). The case of rotating heated inner cylinder and stationary cooled outer cylinder (RHISCO) is a model for the cooling of rotating machinery, the solidification of pure metals, techniques of chemical vapor deposition, rotating-tube heat exchangers and nuclear reactor fuel rods (kreith1968, ; Singer1984, ; vives1988, ; SelOz14, ). The geometry of such an experimental apparatus is fully specified by the length-to-gap aspect ratio , and the radius-ratio , where and are the radii of the inner and outer cylinders, and is their height.

Depending on the geometry, RHISCO experiments used in the literature can be classified in two groups. The first group of experiments (SK64, ; SoCo79, ; LeGoPriMu08, ) is characterized by long cylinders and narrow gap . Ali and Weidman AlWe90 () performed a detailed linear stability analysis of such flows using axial periodicity and reported on the influence of the Prandtl number () and on the stability boundaries. Their results showed a good agreement with SK64 () and, to a lesser extent with SoCo79 (). Ali and Weidman attributed the discrepancies to the limitations of linear stability theory and the infinite-cylinder idealisation to capture the experimental details. A similar linear stability analysis (YoNaMu13, ) reported good agreement between numerical and related experimental results (LeGoPriMu08, ). Nonlinear simulations for small temperature gradients were provided by Kedia et alKeHuCo98 () who quantified the heat transfer across the system. A second group of experiments embraces apparatuses with moderate aspect ratio and wide gap. Ball and Farouk BaFa87 (); BaFa88 (); BaFa89 () reported heat transfer measurements as well as the sequence of flow transitions using an experimental setup with and . Subsequent numerical simulations (KuBa97, ) for and provided insight on the bifurcations structure of the system. However, the results showed significant discrepancies with experiments suggesting strong effects of the axial boundaries.

An accurate numerical simulation of the axial (Ekman) boundary layers in flows between long cylinders entails a substantial computational cost, especially for rapid rotation and large temperature gradients. The assumption of axial periodicity reduces the computational effort because the Ekman layers are not present and only a short central fraction of the apparatus needs to be simulated to estimate transport properties. Moreover, under this assumption variables can be expanded as a Fourier series in the axial direction, which greatly simplifies the numerical approach and enables the use of more efficient solvers.

In this paper we determine under what conditions periodic boundary conditions can be employed to describe the dynamics of RHISCO experiments. In particular, we provide criteria to distinguish flow features that arise from the interplay between differential rotation and temperature, from those which are mainly determined by the axial boundaries or end walls. We compare the flow dynamics by using both physical (no-slip) and axially periodic boundary conditions in our numerical simulations. We show that axial periodicity renders a good approximation of laboratory flows as long as the Rayleigh number is small. We provide a simple criterion that determines whether heat transfer in the laminar flow is conductive or convective. In particular, conductive profiles, which enable the use of axially periodic boundary conditions, are obtained as long as . In addition, the coefficient may be neglected for .

2 Specification of the system and numerical methods

We consider the motion of an incompressible fluid of kinematic viscosity and thermal diffusivity confined in the annular gap between two rigid and concentric rotating cylinders of radii and . The inner cylinder rotates at constant angular velocity , whereas the outer cylinder is kept at rest. A radial thermal gradient is considered by setting the inner and outer cylinder temperature to and , respectively. Here is the mean temperature of the fluid. The axis of the cylinders is vertical, i. e. parallel to the gravitational acceleration . We study flows with stationary end walls and with axially periodic boundary conditions (Figures 1 and respectively). The latter model the case of infinitely long cylinders, whereas the former reproduce experimental boundary conditions (no-slip for the velocity and thermally insulating end walls for the temperature).

Figure 1: (color online) Sketches of geometry and boundary conditions for the two cases considered in this paper. Stationary insulating endwalls (no-slip boundary condition for the velocity and zero flux for the temperature) and axially periodic boundary conditions. The temperature profile is superimposed on the right hand side of each figure.

2.1 Governing equations

We consider the Boussinesq approximation including centrifugal buoyancy in an inertial reference frame as described in LoMaAv13 (). The dimensionless governing equations are

(1a)
(1b)
(1c)

where denotes the velocity field vector and is the deviation of the temperature with respect to . The length, time, temperature and pressure scales chosen to make the set of equations dimensionless are the gap width , the viscous time , the temperature difference between the cylinders and respectively. There are six independent dimensionless numbers (see table 1). The term accounts for centrifugal buoyancy, including secondary effects stemming from differential rotation or strong internal vorticity LoMaAv13 (). The equations are solved in cylindrical coordinates

Name Symbol Formula Operation range
Grashof number
Relative density variation
Prandtl number
Aspect ratio
Radius ratio
Reynolds number Re

Table 1: Dimensionless parameters. Here and are respectively the thermal diffusivity and the coefficient of volume expansion of the fluid, is the density variation associated with a temperature change of . Last column indicates the range of values covered by the simulations shown in this paper.

2.2 Numerical methods

In the axially periodic case the onset of instabilities was determined via linear stability analysis of the basic flow as in LoMaAv13 (). Fully nonlinear simulations were performed using the Boussinesq-approximation LoMaAv13 (), which was added with the heat equation to the finite-difference-Fourier–Galerkin (hybrid MPI-OpenMP) code of Shi et al.LiRaHoAv14 (). A time-step viscous time units was used in all computations.

For rigid end walls the governing equations were solved using a second-order time-splitting method. A pseudo-spectral formulation is used for the spatial discretisation, with the Fourier–Galerkin method in the azimuthal coordinate and Chebyshev collocation in and . The code is based on a previous hydrodynamic code AGLM08 (), which has been extended with the Boussinesq-approximation of LoMaAv13 () and parallelised as in LiRaHoAv14 (). Details can be found in J. M. Lopez’s PhD thesis Lop15 (). The numerical resolution has been chosen to ensure that the infinite norm of the spectral coefficients decays at least four orders in magnitude. Time steps as small as viscous time units have been required for numerical stability and accuracy of the second-order temporal scheme.

3 Conductive and convective basic flows

The assumption of axial periodicity allows to considerably simplify the calculation of the basic flow. The radial velocity is zero and the rest of variables only depend on the radial component. Under these conditions an analytical solution can be found by imposing a zero axial mass flux. This reads

(2a)
(2b)
(2c)

The azimuthal velocity is the classical Couette flow, corresponds to the temperature in a conductive regime and is the axial velocity profile induced by gravitational buoyancy. The parameters , and are

(3)
(4)

and the non-dimensional radii are , .

Note that the conductive temperature (2c) only depends on the radial geometry. Figure 2 illustrates the variation of the axial velocity and temperature with .

Figure 2: Radial profiles of axial velocity (computed for ) and temperature as a function of the radius ratio .

3.1 End walls effect: influence of fluid properties and geometry.

The presence of end walls in the system leads to non-zero radial velocities close to the end walls, commonly referred to as Ekman layers, and enables convective heat transfer across the gap even for the basic flow (Gre68, ; HiMa75, ). This switches on the contribution of terms of the heat equation, which were zero under the axial periodicity assumption. The temperature equation (1b) reads

(5a)

In the infinite case the steady basic flow has no radial velocity () and the temperature () depends only on , so all terms in the left hand side are zero. Consequently, the basic flow is unaffected by changes in the fluid properties. In contrast, the influence of may be expected to play a significant role in bounded systems. It modifies the basic flow with respect to the idealised periodic situation and may become an important source of discrepancies between both systems.

(a)
(b)
(c)
(d)
Figure 3: (color online) Colormaps of the temperature for , , , and different values of . They are plotted in a meridional section with the inner cylinder on the left hand side. Note that the aspect-ratio has been scaled in these plots to enhance the visualization of the contours. (b)–(c) Temperature profiles at mid-height and mid-gap, respectively.(d) Variation of with for several values of . The case of has a purely conductive temperature profile as in the axially periodic system.

Figure 3() shows colormaps of the temperature in a meridional section for , , , , and . It clearly illustrates how changes in alter the temperature of the basic flow in a finite system. Radial and axial temperature profiles are shown respectively in figures at mid-height and () at mid-gap as a function of . For (gases or liquid metals), and sufficiently far from the end walls, the temperature profiles are nearly independent of and thus deviations from the conductive regime () are negligible. The axial dependence becomes stronger with increasing , resulting in radial temperature profiles that differ substantially from a conductive profile even at mid-height. This temperature regime is usually referred to as convective ThValD70 (); AlMcF05 (), and is characterised by sharp thermal boundary layers and enhanced heat transfer.

The heat transfer across the gap is here characterised by the Nusselt of the inner cylinder

(6)

where indicates time average and denotes the dimensionless heat flux of the laminar (conductive) flow in the periodic case. To simplify the notation the subindex is omitted henceforth. Note that the Nusselt number of the outer cylinder is . The effect of the transition between the conductive and convective regime on heat transfer is shown in figure 3(). Large and short promote convective profiles and thus efficient heat transfer.

3.2 Transition from conductive to convective: the Rayleigh effect

We quantify the departure of the radial temperature profiles from the conductive regime with the parameter

(7)

where is the radial temperature profile at mid-height and denotes the conductive profile (2c) of the infinite-cylinder case.

Figure 4 shows the transition between the conductive and convective regimes as a function of the Rayleigh number () and . The critical Rayleigh numbers have been computed by fixing (using different values) and , and increasing until was reached. For low values of there are significant differences between calculated with different . However, for the transition takes place at nearly the same regardless of . This interesting behaviour can be explained by analysing equation (2c). The laminar state is steady and axisymmetric, so departures from the conductive regime are due to either or . The first term is only affected by changes in and plays a significant role in setups with a relatively short aspect-ratio, as the radial velocities arising near the end walls are more vigorous. Consequently, variations of with are observed in short setups.

In contrast, the second term depends on both and , but only through their product: the Rayleigh number . This becomes progressively dominant as increases and the transition to the conductive regime becomes dependent on only. Interestingly, varies linearly with according to

(8)

This linear behaviour was also observed for fixed by Thomas and De Vhal Davis ThValD70 (), who studied the transition between both temperature regimes for natural convection.

Figure 4: (color online) Transition from conductive to convective temperature regime () as a function of the aspect-ratio and Rayleigh number for and . Variation of the slope in the linear equation (8) marking the transition between the conductive and the convective regimes.

The linear relationship (8) separates the regions of parameter space in which the temperature regime is conductive and conductive. It provides a criterion to determine a priori whether simulations using axially periodic boundary conditions render a good approximation of laboratory flows. Note however that since the temperature profile of the laminar conductive state (2c) depends on , criterion (8) is valid only for . In order to investigate the effect of curvature in the transition from conductive to convective heat transfer, we performed simulations as those shown in figure 4 for different values of . We found that for all investigated curvatures a linear relationship of the form

(9)

is always satisfied, but the slope depends significantly on (see figure 4 ). The curve is well approximated by the cubic function

(10)

The offset of the linear equation satisfies for the whole -range and so can be neglected in comparison with for .

4 Primary instability

Figure 5: (color online) Critical stability boundaries ( vs Re). The numbers that appear on top of the critical curves are the azimuthal modes associated to the critical perturbations. (Blue) Solid line and squares are used in the case of finite-length cylinders, whereas (green) dashed line and circles stand for the marginal stability in the case of infinite long cylinders. The working fluid is air () and the geometric parameters are and (in the finite case). Detail of the marginal curve for low G in the infinite cylinders case.

4.1 Axially periodic disturbances

The dashed line in figure 5 shows the stability curve of the conductive laminar flow to axially periodic disturbances for and . Three regions with qualitatively different behaviour can be distinguished. For slow or no rotation the laminar flow is destabilised as increases. Buoyancy is the indirect force driving the instability, which occurs because the axial velocity profile (2b) has an inflection point. At low viscosity can stabilise the laminar flow, but as increases the magnitude of the axial velocity grows proportionally to until the flow becomes unstable at . The instability pattern consists of axisymmetric convection rolls that travel axially in the upward direction VaTh69 (). This axial drift of the rolls is caused by curvature, which makes the axial velocity profile of the conductive basic flow radially asymmetric (see Fig. 2). In the limit of vanishing curvature (vertical plates) the roll-pattern is steady because the system is left-right symmetric about the mid-gap elder1965laminar ().

As the inner-cylinder rotation speed increases the centrifugal force starts to compete with buoyancy and the laminar flow becomes first unstable to nonaxisymmetric spiral modes. Although centrifugal instabilities are typically axisymmetric (i.e Taylor vortices), it is well known that in the presence of a sufficiently large axial velocity nonaxisymmetric spiral modes are dominant. This was first shown by Snyder snyder1962experiments () in Taylor–Couette flow with a superimposed axial pressure gradient. In our system, as increases the critical Rayleigh number for the onset of these spiral modes and their wavenumber () progressively decrease. At the critical curve for the spiral modes intersects the curve corresponding to the pure centrifugal instability (i.e Taylor vortices with ). Figure 5 shows a close up to the vicinity of this point.

4.2 Axially bounded cylinders

Following Kuo and Ball KuBa97 () we chose . The computed stability curve is shown as a solid line in figure 5 and also features an intersection point around which spiral modes and axisymmetric Taylor vortices compete. In comparison to the periodic case, this intersection point is displaced to because of the finite aspect-ratio. Here, as in the periodic case, and long aspect-ratio experiments of Snyder and Karlson SK64 (), who used , there is a region in which spiral modes appear at lower values of Re than Taylor vortices. However, this region is limited by a turning point and when is further increased instabilities are suppressed. The Ekman layers cause a slow transition to the convective basic state and enhance heat transfer without the need for instabilities. Overall the stability curves for the finite and periodic system are in qualitative agreement up to . This is in line with criterion (8), which predicts the transition between conductive and convective states at .

5 Heat transfer for increasing rotation speed

The stability analysis of the previous section cannot predict the dynamics and heat transfer properties of the flow. For these purposes we performed direct numerical simulations of the Navier–Stokes equations. We first investigated , so that the temperature for is conductive. In the periodic case we choose a cylinder length of , which allows some freedom in the selection of the wavenumber of the vortex-pairs.

Figure 6 shows the sequence of emerging patterns in the periodic (upper row) and finite (lower row) cases as the Reynolds number is increased. For the periodic system the primary instability occurs at , leading to spiral flow with azimuthal wavenumber (figure 6 ). By further increasing Re the axial flow generated by buoyancy loses importance in comparison to the centrifugal force. This results in secondary transitions towards spiral flows with decreasing azimuthal mode . The transition from to takes place at , whereas the transition to occurs at . The flow patterns with and are shown in figure 6 and , respectively. At the spiral flow is modulated by a low frequency and the flow becomes quasi-periodic. The resulting state preserves the spiral structure with and is characterised by the appearance of spatio-temporal defects (figure 6 ). Finally, for the centrifugal force completely dominates and spiral flow is superseded by Taylor vortices (figure 6 ). These results are consistent with the physical mechanisms discussed in the linear stability analysis of §4.1.



Figure 6: Evolution of an isosurface of the axial velocity in the periodic (upper row) and finite (lower row) systems as Re is varied and , , , (finite case) and (infinite case).

The same sequence of flow states was found in the finite case, but with slightly different Reynolds number for the transitions. The basic flow loses stability to spiral flow with for (figure 6 ), whereas the transitions to and occur at and respectively (figure 6 )). The transition between spiral flow and Taylor vortices is also characterised by the presence of defects, which are much more pronounced than in the infinite cylinders case (figure 6 ). The onset of Taylor vortices (figure 6 ) takes place at .

In figure 7 we show the heat transfer rate, normalised by the conductive rate as in equation (6), as a function of increasing Re. As the basic flow is conductive for periodic and finite boundary conditions, is in both cases independent of Re before the onset of instabilities (). In the infinite case heat transfer is purely conductive (), whereas in the finite case, is slightly higher () due to the heat transfer at the Ekman boundary layers. The onset of instability enhances the convective heat transfer significantly and the Nusselt number follows a power-law scaling , with for the finite case and for the periodic case.

Figure 7: Variation of with Re for , and in the finite () and infinite () cases.

6 Heat transfer for increasing temperature difference

We here investigate the dynamics and heat transfer for and increasing . The upper row of figure 8 illustrates the bifurcation scenario for axially periodic boundary conditions. Colormaps of the temperature in longitudinal sections at are depicted. The onset of instability occurs at resulting in a spiral flow pattern with azimuthal mode number . This is stable only in the vicinity of the critical point. A small increase in leads to a new spiral state with (figure 8 ), which remains stable for . Complex spatio-temporal dynamics emerges as is further increased (). The sequence is as follows. First, spiral states turn into wavy spiral flow patterns shown in figures 8 and , corresponding to and respectively. Note that the dominant spiral mode changes back from to as is increased. These flow patterns are similar to those reported in both experimental LeGoPriMu08 () and numerical studies ViPo14 () for large and . Subsequently increasing above the wavy spiral flow regime the flow becomes chaotic (figure 8 ).

Figure 8: (color online) Evolution of the temperature in the periodic (upper row) and finite (lower row) systems as changes and , , , (finite case) and (infinite case). Colormaps are plotted in longitudinal sections at , with the exception of the axisymmetric states and , which are plotted in a meridional section . Note that these plots have been resized and do not correspond to the aspect-ratio of the investigated system.

The sequence of flow states obtained in the finite case (lower row of figure 8) is qualitatively similar to the periodic case up to the transition to the convective basic state, which is found to occur at , in qualitative agreement with criterion (8). Nevertheless, there are quantitative differences. Here the conductive basic flow (figure 8 ) remains stable up to , where spiral flow with develops (figure 8 ). As the radial heating increases the dominant spiral mode changes to at (figure 8 ). This increase in with is driven by the stronger axial flow acting on the fluid because of thermal buoyancy KuBa97 (). Further increasing leads to the thinning of the thermal boundary layers at the sidewalls and the flow transitions gradually to the convective laminar flow (figure 8 ). A similar transition from spiral flow to the convective state as is increased was experimentally observed by BaFa89 () using an apparatus with . We refer the reader to Ref. KuBa97 () for a detailed description of these instabilities.

The evolution of the normalised with clearly illustrates the different dynamical behaviours in the finite (figure 9 ) and infinite (figure 9 ) systems. The largest differences occur for weak rotation (). In the infinite case , remains constant up to , indicating that heat transport is exclusively conductive up to reach the onset of instability. In contrast, in the finite case, the Ekman layers provide an efficient mechanism to transfer heat, which results in an almost linear increase of with . Such growth is also observed for spiral flow, and . When exceeds the value corresponding to the upper part of the marginal curve in figure 5 the flow becomes again axisymmetric and solely depends on . As a result, curves corresponding to different values of Re collapse. In the infinite case, the behaviour of within the region of spiral flow, and , reflects the transitions described above. The spiral flow () resulting from the primary transition provides efficient heat transfer, leading to a rapid linear growth of as is increased. In this flow regime the values of in the infinite case are slightly larger than those in the finite case. The transition towards wavy spiral flow results in a sudden decrease of the convective heat transport, consistently with the results of KeHuCo98 (). After this initial drop, further increasing towards fully developed turbulent flow is accompanied by a progressive growth in , which is however significantly lower than the linear growth from the spiral flow regime.

Figure 9: Variation of with as a function of Re for and in the finite () and infinite () systems.

7 Discussion

Heat transfer in laminar flows between two concentric vertical cylinders can be of conductive or convective nature. Regardless of the curvature of the cylinders, parametrised here by the radius ratio , the transition between these regimes is governed by the Rayleigh number and the length-to-gap aspect ratio . In particular, for a given there is a critical above which the laminar state is convective. We here determined numerically a linear criterion (9), which applies to all geometries and is independent of the Prandtl number as long as . For smaller the transition to the convective state is influenced by because of the stronger effect of the Ekman layers. Although the criterion was obtained for a fixed Reynolds number , we provided evidence that it appears valid as increases. This was done by comparing results obtained with axially periodic boundary conditions, for which the laminar flow is always conductive, to results obtained with physical (no-slip) boundary conditions.

If the laminar flow is conductive and is increased while is kept fixed, our direct numerical simulations show that the transition to chaotic flow is very similar in the periodic and finite cases. This was shown by using , , and in the finite case, following Kuo and Ball KuBa97 (). All their reported transitions were reproduced here, however, we found a notable difference in the onset of spiral flow, which occurs for lower Re in our simulations and corresponds to a critical spiral mode instead of . This can be explained because Kuo and Ball KuBa97 () neglected the correction of the velocity field in their simulations, so their velocity field was not mass conserving. Omitting the correction in our simulations we reproduced their results and found that its relevance diminishes as Re increases, so that the secondary transitions reported here coincide with those in KuBa97 ().

We further repeated these simulations by using periodic boundary conditions in a domain of length . We found that the onset of instability occurs at slightly lower Re than in the finite case, where the Ekman layers act as frictional layers, slowing down the internal flow and thus delaying the primary and secondary instabilities. In contrast, as the Re is further increased the remaining instabilities, culminating in Taylor-vortex flow, are favoured by the presence of axial end walls. In this case the Ekman circulations at the end wall enhance the Taylor vortices, as happens in the isothermal case.

The heat transfer, quantified by the convective Nusselt number (6), follows a simple power law ( and in the finite and infinite cases respectively). The exponents are in good agreement with the analytical correlation provided by Dorfman dorfman1963 (). A similar exponent () has also been found by Viazzo and Poncet ViPo14 () who numerically explored a region of parameter space similar to that in figure 7, but using an apparatus with and . The small discrepancies between the correlations obtained in the finite and infinite cases occurs because of the Ekman layers, whose importance grows as is reduced.

If is kept fixed while increases, the transition to chaotic flow and heat transfer of the periodic and the finite system remain similar as long as criterion (9) is approximately satisfied. In the finite system, further increases in result in a transition to the laminar convective state, whereas the periodic system becomes gradually more turbulent. Thus there are two counter-acting mechanisms as increases. Instabilities and turbulence are stimulated because of thermal driving. However, thermal driving results in a thinning of the thermal boundary layers because of end-wall effects. This quenches turbulence and causes the transition to the laminar convective state. Noteworthy, at a fixed the laminar convective state is much more efficient in transferring heat than the turbulent flow of the periodic system.

8 Conclusions

The role of axial boundaries in laterally heated and rotating flows was investigated with linear stability analyses and direct numerical simulations. Both periodic and no-slip boundary conditions were considered in the axial direction. The main results can be summarised as follows:

  • Criterion (9) determines whether laminar heat transfer in an axially bounded system is of conductive or convective nature. It is independent of Prandtl number and robust with Reynolds number as long as .

  • If the laminar state is conductive axially periodic boundary conditions correctly describe the dynamics and heat transfer in laboratory setups. If the laminar state is convective the infinite-cylinder approximation may be used but the basic flow must be modified to include axial stratification AlMcF05 ().

  • A variety of flow patterns was observed. The underlying flow instabilities are driven by the interaction of two physical mechanisms: thermal buoyancy generates an inflectional axial velocity profile, whereas the inner-cylinder rotation promotes centrifugal instability.

Acknowledgement

This work was supported by the Spanish Government grant FIS2013-40880-P and BES-2010-041542. Part of this work was done during the visit of J.M. Lopez to the Institute of Science and Research (IST) in Klosterneuburg (Austria) whose kind hospitality is warmly appreciated. We thank Red Española de Supercomputación (RES) for the computational resources provided.

References

Footnotes

  1. journal: International Journal of Heat and Mass Transfer

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