analysis of the interfacial area transport model for...
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The 15th
International Topical Meeting on Nuclear Reactor Thermal - Hydraulics, NURETH-15 NURETH15-067 Pisa, Italy, May 12-17, 2013
ANALYSIS OF THE INTERFACIAL AREA TRANSPORT MODEL FOR INDUSTRIAL
2-PHASE BOILING FLOW APPLICATIONS
K. Goodheart, N. Alleborn, A. Chatelain and T. Keheley AREVA - AREVA GmbH, Postbox 1109, 91001 Erlangen - Germany
ABSTRACT
One of the most important parameters when using a 2-fluid model to analyze the
critical heat flux (CHF) performance of a mixing grid is the interfacial area term.
This term is responsible for the rate of phase change and the amount of thermal
and mechanical interaction between phases. Accurate closure relations for this
term are not fully developed for flow conditions in a rod bundle that contain
spacers with mixing vanes and simple support grids. Using the OECD/NRC,
Nuclear Power Engineering Corporation (NUPEC) PWR Bundle Tests (PSBT)
5x5 rod bundle steady-state average void fractions are compared to numerical
simulations. Predicting the correct void fraction is one aspect in using numerical
simulation to predict CHF performance but attention must also be turned to the
temperature distribution along the rods, especially the impact of spacers. An
analysis is presented which shows the impact of the temperature distribution
along the rods for various interfacial area transport model parameters and closure
models. With this AREVA demonstrates that it is possible to predict average void
and correct temperature distributions with the use of computational fluid
dynamics (CFD).
1. INTRODUCTION
The modelling of multi-phase flow in rod bundles with spacers is an important aspect for nuclear
fuel design and operation. The use of simulation techniques from 1-D analysis to CFD is a well
established field in many industries. Especially in the field of nuclear applications single-phase
CFD is already an integral part of the thermal hydraulic method toolbox, see e.g. [1],[2]. Multi-
phase CFD is a subject of intense research, methods for nuclear applications are on-going [3],[4].
The purpose of this paper is to highlight the use of numerical simulations for multi-phase
applications which can be used for safety analysis, performance prediction and cost savings.
The paper will describe the models used for a 2-phase analysis and highlight areas of numerical
sensitivity to achieve stable/converged solutions. With the chosen set of models, the
experimental data from the OECD/NRC PSBT 5x5 rod bundle benchmark is used to highlight
the ability of the models to predict average void in a rod bundle configuration. Average void
prediction in the sub-channels is one important aspect of nuclear applications, but predicting the
correct rod temperature distribution close or at critical heat flux (CHF) will also be discussed.
2. PHYSICAL MODELS
The 2-phase simulations are based on the Eulerian multi-phase approach, where the conservation
of mass, momentum and energy are solved for each phase. The commercial software tool
provided by CD-adapco, STAR-CCM+ v7.04 is used for the standard 2-phase analysis with
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custom modelling for the interfacial area and wall boiling models. The conservative relations for
mass, momentum and energy used in STAR-CCM+ are given by [5]-[7].
2.1 Interfacial Area Transport Equation
The interfacial area term is very important in the interaction terms between phases for
momentum and mass/energy transfer. Ishii [8] summarizes the development of the interfacial
area term based on modelling and experimental benchmarks. Before going further it is important
to show the relationship between interfacial area and mean bubble diameter, for a spherical
bubble the relationship is
i
g
sa
dα6
= (1)
Where sd is the mean Sauter bubble diameter and ia is the interfacial area. The easiest method is
to assume a constant mean Sauter bubble diameter or a function of sub-cooling, but an advanced
method is to solve a transport equation for the interfacial area. Kocamustafaogullari and Ishii [9]
developed the Interfacial Area Transport Equation (IATE), based on the concept of a particle
number distribution, where this quantity of interfacial area is convected and its source/sink terms
are based on collision frequency, efficiency, compressibility and mass transfer. Many source
term variants have been developed to describe the break-up and coalescence, by Hibiki and Ishii
[10], Wu et al. [11] and Yao and Morel [12] to name a few. The volumetric form of the
interfacial area transport equation is given by Yao and Morel [8]
( ) ( ) NUC
nnuc
BK
n
CO
n
i
g
ig
g
i
ig
i daDt
Daau
t
aφπφφ
απρα
αρ2
2
,3
36
3
2)(++
+
−Γ=⋅∇+
∂
∂ r (2)
The 2 terms on the left hand side represent the unsteady and convective term of the interfacial
area. The 1st term on the right hand side represents the change due to condensation/evaporation,
but not nucleation at the wall, the 2nd
term is based on compressibility of the gas phase followed
by coalescence, breakup and nucleation.
If we multiply equation 2 by the density of the gas phase, assume steady-state and
incompressible gas phase, equation 2 can be rewritten as
( ) ( ) NUC
nnucgBKCOgig
i
ggg dSSa
u φπρρα
φρα 2
.3
2+++Γ=⋅∇
r (3)
where the
2
3
36
ia
απterm is incorporated into the BKCO SS , , source terms for coalescence/break-
up and φ is a passive scalar related to interfacial area by φα=ia . Equation 3 is the final form
implemented in STAR-CCM+ using passive scalar transport equation.
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2.1.1 IATE Break-up and Coalescence Source Terms
In equation 3 it is interesting to examine the two source terms for break-up and coalescence for
any potential numerical difficulties. There are many different models available for break-up and
coalescence, but for simplicity only 2 will be examined, Hibiki and Ishii [10] and Yao and Morel
[12].
The source terms for break-up and coalescence allow for singularities to occur, e.g. when the
void fraction α approaches αmax.
0 0.2 0.4 0.6 0.8 1-5.0x105
-3.0x105
-1.0x105
1.0x105
3.0x105
5.0x105
αg
∑(S
CO+
SB
K)
Hibiki&Ishii ε = 1 m2/s
3
Yao&Morel ε = 1 m2/s
3Yao&Morel ε = 1 m
2/s
3
Hibiki&Ishii ε = 1000 m2/s
3Hibiki&Ishii ε = 1000 m
2/s
3
Yao&Morel ε = 1000 m2/s
3Yao&Morel ε = 1000 m
2/s
3
0.0 0.2 0.4 0.6 0.8 1.0
-1.0x108
-5.0x107
0.0x100
5.0x107
1.0x108
αg
∑(S
CO
+S
BK)
Hibiki&Ishii ε = 1 m2/s
3
Yao&Morel ε = 1 m2/s
3Yao&Morel ε = 1 m
2/s
3
Hibiki&Ishii ε = 1000 m2/s
3Hibiki&Ishii ε = 1000 m
2/s
3
Yao&Morel ε = 1000 m2/s
3Yao&Morel ε = 1000 m
2/s
3
Mean Bubble Diameter 1mm Mean Bubble Diameter 0.1mm
Figure 1 - Comparison of the Hibiki and Ishii and Yao and Morel coalescence and break-up
source terms as a function of void fraction.
Using material properties at 135 bars for water/steam and assuming two different mean bubble
diameters (0.1 and 1mm) and two values for turbulent dissipation rate of water ε = 1 and 1000
m2/s
3 (typical sub-channel and near rod values), Figure 1 compares the sum of the break-up and
coalescence source term. For the Yao and Morel model for large bubbles, the source term shows
no singularity, because the term We/Wecrit (Wecrit =1.24) or the interaction time is dominant
compared to the free travelling time. As the bubble diameter gets smaller and volume fraction
increases a singularity is found in the Yao and Morel model, not because αα =max like in the
Hibiki and Ishii model but because the free travelling time and interaction term offset each other
resulting in a near zero value. The break-up and coalescence models were originally not devised
for flow parameters reaching values that lead to these unphysical singularities. However, during
the iterative numerical solutions of the governing equations such values might be reached during
intermediate solution steps. Therefore it is essential for a stable numerical implementation of
these terms, to provide stability measures, such as smoothing, suppressing the singularity or by
setting maxα to a number slightly greater than 1. These techniques have no physical meaning;
therefore it is necessary to evaluate the effect on the 2-phase results. A detailed discussion of the
numerical techniques and evaluation of these techniques is out of the scope of this paper.
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2.2 Wall Boiling
As the interfacial area is an important term for 2-phase modelling an equally important aspect is
the wall boiling models which generate the amount of void, but which is also a source term for
the IATE model (last term in equation 3).
In STAR-CCM+ the wall heat flux is composed of 4 components [3], liquid contribution based
on single-phase turbulent convection, portion responsible for producing bubbles ( "
evapq ), portion
of heat due to the influx of cooler liquid after a bubble as departed (quenching), and a vapour
contribution to heat flux, based on single-phase turbulent convection.
STAR-CCM+ has 2 different sub-models for wall boiling but there is also the ability to
implement user defined models, e.g. Model Set 3 in Table 1.
Wall Boiling Model Set 1 Model Set 2 Model Set 3
Nucleation site
number density Lemmert-Chawla Hibiki-Ishii
Kocamustafaogullari-
Ishii
Bubble departure
diameter
Tolubinsky-
Kostanchuk Kocamustafaogullari
Kocamustafaogullari-
Ishii
Bubble departure
frequency Cole Cole Cole
Table 1 - Summary of sub-models for wall boiling.
Before using these models in a CFD simulation it is important to examine "
evapq as a function of
wall superheat. Assuming the material properties at 135 bars and that the liquid temperature is
equal to the saturation temperature, sub-cooling is zero, the various model sets can be plotted as
a function of super heat. In Figure 2 the Model Sets 1 and 3 behave very similar: step increase in "
evapq and than levelling out as the super heat increases. Even though Model Sets 1 and 3 are
similar in terms of "
evapq , the bubble departure diameter is different by a factor of 100, where the
Kocamustafaogullari-Ishii model is driven mainly by the reference pressure, therefore being 100
times smaller than the Tolubinsky-Kostanchuk model, which is mainly driven by sub-cooling
and the reference diameter of 0.6mm.
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0 2 4 6 8 1010
-510
-410
-310
-210
-110
010
110
210
310
410
510
610
710
810
910
1010
1110
1210
1310
1410
1510
1610
1710
1810
1910
20
Tsuper [C]
qe
va
p [
W/m
2-s
]
Model Set 3
Model Set 2Model Set 2
Model Set 1Model Set 1
Figure 2 - Comparison of the different wall boiling model sets, see Table 1 for description of the
model sets.
2.3 Interfacial Momentum Closure Models
The interfacial momentum closure models used for the simulations are the drag model based on
Wang and turbulent dispersion. Additional closure models are examined in section 4.2.
3. RESULTS OECD/PSBT BENCHMARK
3.1 Geometry/Boundary Conditions
The boundary conditions and spacer location are given by [14]. It is based on the test assembly
B5, which is a 5x5 rod bundle, uniformly heated with 7 spacers with mixing vanes, 8 simple
support grids and 2 spacers with no mixing vanes. Five different test cases were examined,
which represent a range of operating pressure from 75-167 bars and a range of average void from
near zero to 56%. A summary of the cases used for the CFD simulations can be found in Table 2.
Test Case 5_1121 5_2442 5_5311 5_3321 5_3332
Pressure [bar] 164 147 73.5 122 122
Inlet Temperature
[°C] 316.9 263 193.8 271.8 277.3
Heat Flux (kW/m2) 1096 733 1285 1098 914
Mass Flux [kg/m2] 4156 1386 2242 3072 2219
Table 2 - Summary of PSBT operating conditions for CFD simulations.
The mesh consists of 121 million trimmed cells; Figure 3 shows the mesh resolution for the
spacer with mixing vanes and simple support grid.
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Figure 3 - Sections of the mesh used for the PSBT 5x5 full bundle CFD simulations.
3.2 Average Void prediction
The results for all simulations are based on models presented in section 2. For all runs, the
solution was considered converged when the percent error in mass imbalance
100,,
,,,,
+
+++
inling
outloutginling
mm
mmmm was less than 1% and the average void was no
longer changing at the 3 monitoring locations (2.216, 2.699, and 3.177m in the test section).
Figure 4 shows an example of the average void convergence history for the 5_2442 case (all
other cases show similar behaviours).
Figure 4 - Convergence for the average void at the 3 monitoring locations for case 5_2442.
One set of comparison with experimental data is to examine the average void in all sub-channels
and compare with chordal measurement, Figure 5. There is good agreement between the level of
the void at the 3 locations as well as the distribution, the edges having lower void compared to
the center. Figure 6 compares the predicted average void in the 4 central sub-channels with
experiment based on the 3 monitoring locations at 2.216, 2.699, and 3.177m in the test section.
Figure 6 shows for all 5 test cases the 2-phase models are able to predict average void within the
uncertainty of the experimental value.
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Figure 5 - Comparison of average void based on run 5_2442. Top: CFD results of average void
in each sub channel, Bottom: void distribution image in rod bundle by chordal measurement[15].
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9
1
0 0.2 0.4 0.6 0.8 1
Measured void fraction [-]
Calc
ula
ted
vo
id f
racti
on
[-]
CenterLine
+/- 2σ
5_1121
5_2442
5_3221
5_3332
5_5311
Figure 6 - Comparison of average void between CFD and experiments [16] for the 5 PSBT test
cases.
3.177m 2.699m 2.216m
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4. RESULTS OF 2X1 SUBCHANNEL WITH SPACER NEAR CHF
In section 3 the prediction of average void with CFD was shown to work within the uncertainty
of the experiment based on the OECD/PSBT benchmark. Another aspect of CHF prediction is
the rod temperature; therefore a 3-span, 2x1 sub-channels case was built using the OECD/PSBT
geometries. The interest of this study is to examine how the different closure models effect rod
temperature for a rod bundle with spacers and support grids. In the following section no
conclusion should be drawn on which is the best model or coefficients, but rather an examination
of the effect these models have on rod temperature near DNB conditions.
4.1 Geometry/Boundary Conditions
The boundary conditions are taken from test case 5_2442, which is shown in Table 2: the heat
flux is slightly increased by about 3% to get closer to DNB conditions, but the CFD inlet
condition remains sub-cooled. Figure 7 shows the geometry of the 3-span case and the periodic
matching that was used to study rod temperature; it consists of 2 spacers and 3 simple support
grids. Because the model is a 2x1 sub-channel with mixing vanes, it is necessary to introduce
periodic boundaries for the correct cross-flow field to be established, the 3 different periodic
matches (P1-P1, P2-P2, and P3-P3), can be seen in Figure 7.
Figure 7 - Geometry of the 3 spans, 2x1 sub-channel using the NUPEC spacer with vanes and
simple support grid. Lower Right: 3 Periodic boundary conditions and associated matching
4.2 Circumferential Averaged Rod Temperature
Based on experiments within AREVA it is well established that for uniform heating the highest
temperatures occur at the end of heated length (EOHL) and the simple support grid has a small
effect. Examining all the different closure models and model coefficients, a parametric study
could involve a huge matrix of comparisons, thus the purpose here is to highlight the differences
found from changing a few parameters and models. Using the lower center rod, every 5mm a
circumferential average temperature is made for the entire length of the 3 spans.
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Figure 8 - Comparison of circumferential average
temperature between sub boiling model sets 1 and 3
Figure 8 shows the effect of rod
temperature for 2 different wall
boiling models; Model Sets 1 and 3
(refer to Table 1 for a description). In
the region of the high temperatures,
the mean bubble diameter for Model
Set 1 is about 10 times higher,
evaporation rates are also higher and
a higher void content is found near
the wall compared with Model Set 3,
therefore the rod heat flux is going
into the vapour contribution of heat
flux, causing the temperature to be
higher. The position of the
temperature peaks is occurring after
the spacer, not at EOHL.
Figure 9 shows the
effect of changing the
coefficients in the
source term for the
IATE equation, break-
up and coalescence.
When changing the
break-up coefficients
there is very little
change in the rod
temperature, but when
increasing the
coalescence source term
coefficients there is a
distinct increase in
temperature. Increasing
the coalescence source
term has the effect of
Figure 9 - Comparison of circumferential average temperature by
changing the coefficients in the IATE break-up and coalescence
source terms eq.10-11.
decreasing the interfacial area, which corresponds to a slightly higher evaporation rate in cells
which are slightly superheated, thus there is an increase in the rod. This is the same reason why
Model Set 1 has higher temperatures; lower interfacial area due to the larger bubble departure
diameter. The reason why changing the break-up had a small effect is because the coalescence
term is the dominating factor in these cells near the wall.
Figure 10 shows the effect of changing different closure laws with respect to wall temperature.
The reference case is based on boiling Model Set 3 and increasing the coalescence source terms,
(Figure 9). The largest effect is seen by the lift model, which is showing the higher temperatures
near the end of span compared to after the spacer; this effect is in line with experimental results
for uniform heating. Adding the wall force models negates the benefit of the lift force and
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changing the drag law or adding particle induced turbulence has a small effect on the wall
temperature distribution.
Figure 10 - Comparison of circumferential average temperature between different closure models
(drag, particle induced turbulence, wall force, and lift).
Another interesting fact is that for all the different temperature profiles in Figure 10, the average
void at various cross-sections are all within 1% of each other, which is below the uncertainty in
void measurements, thus all models would provide the same average void prediction.
Figure 11 - Comparison of maximum void fraction along the wall,
between the lift and reference and lift model.
The main reason for the
change in the wall
temperature distribution by
using the lift model is
because it redistributes the
void along the wall. Figure
11 shows that for the
reference case there is a
peak in void after the
spacer, thus resulting in
high temperatures, for the
lift case the void is
maximum near the end of a
span, thus resulting in
higher temperatures in this
region.
5. CONCLUSION
The source terms for the IATE model for interfacial area were examined in this paper. It was
concluded that numerical techniques are needed to ensure stability of CFD runs for industrial
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applications. A comparison of 3 different boiling sub-models was examined, demonstrating that
Model Set 3 has an advantage in stability and realistic bubble departure diameters for PWR
conditions. The 2-phase Eulerian multi-phase model in STAR-CCM+ along with the IATE for
bubble distribution and the boiling Model Set 3 showed good agreement with predicting average
void within the uncertainty of the OECD/PSBT experiment.
Examining the circumferential average rod temperature for different models resulted in
interesting conclusions that can not be gained by looking at average void alone. The largest
impact for rod temperature is the boiling models chosen, but not necessary from the evaporation
heat flux but more from the bubble departure diameter that goes into the source term for
interfacial area. Changing the coalescence source term has a greater impact than the break-up
term in the considered flow regimes. The closure models for drag and particle induced turbulence
have a small effect on rod temperature, but the addition of a lift model brings the correct
temperature distribution. With this AREVA demonstrates that it is possible to predict average
void and correct temperature distributions with the use of computational fluid dynamics.
6. REFERENCES
[1] M. Leberig, N. Alleborn, M. Glück, J. Jones, Ch. Kappes, C. Lascar and G. Sieber,
“AREVA NP’s advanced Thermal Hydraulic Methods for Reactor Core and Fuel
Assembly Design”, Proceedings of Top Fuel 2009, Paper 2157, Paris, France, Sept. 6-10,
2009.
[2] C. Lascar, E. Jan, K. Goodheart, N. Alleborn, T. Keheley, M. Martin, A. Hatman, A.
Chatelain, E. Baglietto, “Example of application of the ASME V&V20 to predict
uncertainties in CFD calculations”, to be presented at NURETH-15, 2013.
[3] N. Alleborn, R. Reinders, S. Lo, A. Splawski, “Analysis of Two-Phase Flows in Pipes and
Subchannels under High Pressure”, Proceedings of ExHFT-7 2009, Paper FM-11,
Krakow, Poland, June 28-July 3, 2009.
[4] A. Chatelain, K. Goodheart, N. Alleborn, C. Baudry, J. Lavieville, T. Keheley, “Two-
Phase CFD Simulation of DNB and CHF Prediction Downstream Spacer Grids with
NEPTUNE_CFD and STAR-CCM+”, Proceedings of Top Fuel 2012, Manchester, UK,
Sept. 2-6, 2012.
[5] S. Lo and J. Osman, “CFD modelling of boiling flow in PSBT 5x5 bundle”, Science and
Technology of Nuclear Installations, Volume 2012, Article ID 795935, Hindawi
Publishing Corporation 2012.
[6] S. Lo, A. Splawski and B.J. Yun, “The importance of correct modelling of bubble size
and condensation in prediction of sub-cooled boiling flows”, The Journal of
Computational Multiphase Flows, Volume 4, Number 3, 2012, pp. 299-308.
[7] STAR-CCM+ v7.04 Manual, CD-adapco, 2012.
[8] M. Ishii, “Development of interfacial area transport equation modelling and experimental
benchmark”, Proceedings of the 14th International Topical Meeting on Nuclear Reactor
Thermal-Hydraulics (NURETH14), vol. 1, pp. 1–12, Toronto, Ontario, Canada,
September 2011.
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[9] G. Kocamustafaogullari and M. Ishii, “Foundation of the interfacial area transport
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