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Nuclear Engineering and Design 241 (2011) 47044713
Contents lists available at ScienceDirect
Nuclear Engineering and Design
j o u r n a l h o m e p a g e : w w w . e l s e v i e r . c o m / l o c a t e / n u c e n g d e s
Numerical research on oscillation of two-phase flow in multichannels under
rolling motion
Youjia Zhang a,, Guanghui Su a, Suizheng Qiu a, Wenxi Tian a, Hua Li a, Libo Qian a, Yong Li b,Xiao Yan b, Yanping Huang b
a State Key laboratory of Multiphase Flow in Power Engineering, Department of Nuclear Science and Technology, Xian Jiaotong University, Xianning West Road 28,
Xian City 710049, Chinab Key Laboratory of Bubble Physics and Natural Circulation, Nuclear Power Institute of China, 610041 Chendu, China
a r t i c l e i n f o
Article history:
Received 19 January 2011
Received in revised form 16 April 2011
Accepted 16 April 2011
a b s t r a c t
Two-phase flow instability and dynamics of a parallel multichannels system has been theoretically
studied under periodic excitationinduced by rolling motion in the present research. Basedon thehomo-
geneous flow model considering the rolling motion, the parallel multichannelsmodel and system control
equations are established by using the control volume integrating method. Gear method is used to solve
the system control equations. The influences of the inlet, upward sections, heating power and rolling
amplitudeson theflow instability under rolling motion havebeen analyzed.The marginalstability bound-
ary (MSB) under the rolling motion condition is obtained. The unstable regions occur in both low and
high equilibrium quality and inlet subcooling regions. The multiplied period phenomenon occurs in the
high equilibrium quality region and the chaos phenomenon appears on the right of MSB. The concept of
stability space is presented.
2011 Elsevier B.V. All rights reserved.
1. Introduction
The phenomenon of two-phase flow instability occurred widely
in manyindustrial systems and equipments, such as nuclear reactor
steam generators, reboilers, and cooling plants etc. It is undesir-
able since the oscillation caused by two-phase flow instability can
affect the operation and safety features of the systems. Therefore,
analysis of two-phase flow instability is very important for the
safety of nuclear reactors and other two-phase flow equipments.
Su et al. (1998, 2001, 2002) conducted both theoretical and exper-
imental studies on density wave oscillation of two-phase natural
circulation. The MSB of density wave oscillation was obtained. A
criterion of two-phase natural circulation, which predicts the sta-
bility thresholds, was developed by lumped parameter method.
Yun et al. (2005) performed a theoretical study on two-phase
instability in natural circulation loops of China advanced researchreactor (CARR). The phase-space trajectory of the boiling boundary
and the mass flow rate were discussed. Because of the inherent
defect of frequency-domain analysis method, many researchers
(Clausse and Lahey, 1990; Zhou, 1994; Chang and Lahey, 1997; Lin
and Pan, 1994; Lin et al., 1998; Lee and Pan, 1999, 2005a,b; Durga
Prasad and Pandey, 2008a; Durga Prasad et al., 2008b) adopted the
time-domain analysis method to investigate the characteristics of
Corresponding author.
E-mail address: [email protected] (Y. Zhang).
two-phase flow instability. In addition, there are several extensive
reviews of instabilities in two-phase flow system in recent years,
notably by Tadrist (2007), Durga Prasad et al.(2007) and Kakac and
Bon (2008).
Recently, the two-phase flow instability among parallel mul-
tichannels has received extensive attention. In multichannels
system, the instability of natural circulation is very complicated
because of the interaction among channels. Satoh et al. (1998)
conducted a numerical investigation on the effects of multiple
loops on the natural circulation instability. They considered that
the instability of natural circulation in multiple loops system is
more complicated than that of a single loop system because of
the interaction among the loops. Lee and Pan (1999) investigated
the nonlinear dynamics of multiple parallel boiling channels with
forced flows by using the Galerkin nodal approximation method.
They found thesystem becomes unstabledue to channel to channelinteraction with the increase of the channel number. The oscilla-
tions in the pressure drop and in the mass flux to the channels
have been investigatedwhen outof phase oscillations occur. Durga
Prasad et al. (2008b) investigated the oscillation modes under dif-
ferent operating conditions and channel to channel interaction
during power fluctuations and on-power refueling in a double
channels natural circulation boiling system. The system is mod-
eled usinga lumped parametermathematicalmodel. At high power
levels, disturbances in one channel significantly affect the stability
of the other channel. Yun et al. (2008a) conducted a theoretical
research on the behavior of two-phase flow instability in multi-
0029-5493/$ see front matter 2011 Elsevier B.V. All rights reserved.
doi:10.1016/j.nucengdes.2011.04.037
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Y. Zhang et al. / Nuclear Engineering and Design 241 (2011) 47044713 4705
Nomenclature
A cross-sectional area of the control volume (m2) or
amplitude (m)
A+ nondimensional cross-sectional area of the channel
Eu Euler number, Eu = Ps/fu2s
f frictional coefficient
f+ nondimensional frequency, f+ =f/(us/LH)
Fr Froude number, Fr = u2s /gLHh enthalpy (J/kg)
h+ nondimensional enthalpy, h+ = (h hf)/[Q0/(fAxsus)]
k loss coefficient
L length of the control volume (m)
L+ nondimensional channel length, L+ = L/LHM+ nondimensional channel mass, M+ = M/fLHAHNpch phase change number, Npch = (Q/W)(vfg/(hfgvf))
Nsub subcooling number, Nsub = ((hf hi)/hfg)(vfg/vf)
Ns node number in single-phase region
P pressure (Pa)
PH heater perimeter (m)
P pressure drop (Pa)
P+ nondimensional pressure drop, P+ = P/fu2sP+
fnondimensional frictional pressure drop
P+a nondimensional acceleration pressure dropP+g nondimensional gravitational pressure dropP+
Inondimensional inertial pressure drop
P+add
nondimensional additional pressure drop
Q heating power (kW)
q power density (W/m2)
t time (s)
t+ nondimensional time, t+ = t/(LH/us)
u velocity (m/s)
u+ nondimensional velocity, u+ = u/usus characteristic velocity, us = ui,nvf specific volume of saturated liquid (m
3/kg)
z axial coordinate (m)z+ nondimensional length, z+ =z/LH
Subscripts
E entrance of the channel
f fluid or frictional pressure drop
H heated section
i channel inlet
j jth channel
n nth node in single-phase region
o stable state
R upward section
s standard value (characteristic value)
tot total
1 single phase2 two-phase
Greek symbols
+ nondimensional boiling boundary, + = /LH+ nondimensional coefficient of viscosity density (kg/m3)
f the density of fluid (kg/m3)
+ nondimensional density, + = /f
channels system. A physics model that includes the inlet, heated,
and upward sections was built. The instability boundaries of the
multichannels system were obtained in the parameter plane of
subcooling and phase change numbers. The instability space or
instability reef had been found. The present work in this paper is
an extension of the work conducted by Lee and Pan(1999) and Yun
et al. (2008a,b).
The marine reactor plant is influenced thermal-hydraulically by
variousshipmotions(Ishida andTomiai,1992). Therefore,the influ-
ence of ocean motions (such as rolling, pitching, heaving, swaying,
yawing and surging) on the two-phase flow instability among par-
allel multichannels must be taken into account. Rolling motion can
alter the relative positions of the equipments, which have an effect
on the natural circulation and heat transfer. All the ocean motions
can influence thebubble distribution andpressuredifference. These
motions can affect the flow instability of parallel multichannels
system. Thus, it is necessary to have some research in this field
for actual engineering application and the safety of nuclear reac-
tors. There were many papers on the two-phase flow instability
among parallel multichannels system under rolling motion con-
dition such as by Pang et al. (1995), Kim et al. (2001), Ishida and
Yortisune (2002), Murata et al. (2002). In China, many researchers
and scholars (Gao et al., 1997, 1999; Yang et al., 2002) conducted
many theoretical investigations on the characteristics of coolant
system under ocean conditions. Tan and Pang (2005a) and Tan
et al. (2005b, 2006, 2007, 2009) carried out a series of theoretical
and experimental researches on the characteristics of natural cir-
culation under rolling motion condition. Yun et al. (2007, 2008b)
investigated the two-phase flow instability of parallel multichan-
nels system under ocean conditions. The MSB of 9-channel system
was obtained.
The present study extends Lee and Pans method (1999), com-
binedwith Gaos model(1997) for pressure drop in a multichannels
system under the ocean conditions. In Lee and Pans model, there
is only a heated section, and the subcooled boiling is not con-
sidered. The present model is developed by Yun et al. (2008a),
including the inlet and upward sections besides the heated sec-
tion. The subcooled boiling is also considered. On this basis, the
ocean conditions were added into this model (Yun et al., 2008b).
Therefore, the present model can be used to estimate the stability
of parallel multichannels system under ocean conditions.
The influence of rolling motion on the two-phase flow insta-bility among parallel multichannels is analyzed. The MSBs of
multichannels (i.e. 4, 9-channel) systems are obtained under
different pressures. The accurate stability spaces under rolling
motion are presented.
2. System and physical model
2.1. Parallel multichannels model
The parallel multichannels model which is made up of two
plenums and many parallel channels (as shown in Fig. 1) is based
on the model of Lee and Pan (1999). The channel is divided into
three parts from bottom to top: inlet, heated and upward sec-
tions, respectively. The heated section is composed of two parts,
which are single-phase and two-phase sections, separately. In themodel of Lee and Pan (1999) there was only heated section. And
in the present study, the models of inlet and upward sections are
also included. This is based on the previous work of Clausse and
Lahey (1990). In our study, the manifestation of flow instability is
intertube pulse. It belongs to the dynamic instability.
The nondimensional system conservation equations can be
written as follows:
Mass conservation equation:
+
t++
z+(+u+) = 0 (1)
Energy conservation equation:
t+
(+h+) +
z+
(+h+u+) = 1 (2)
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Upper Plenum
Lower Plenum
heating section
upward section
inlet sectionthrottle valve
LR
LH
LE
single phase zone
two-phase zone
subcooling boiling
saturated boiling
Fig. 1. Schematic of parallel multichannels system.
Momentum conservation equation:
t+(+h+) +
z+(+u+
2) = +u+
2
Ni=1
ki(z+
z+i
)++
2
2
1
Fr+ Eu
P+
z+(3)
where = (1 + Npchh+)1, h+ > 0; + = 1, h+ 0; = 1 , in single-
phase region, frictional factor; = 2 , in two-phase region,
frictional factor.
The present theoretical model is basedon the following assump-
tions:
1. Uniform heat flux in the axial direction.
2. The fluid is in subcooled state at the channel inlet.
3. The homogeneous flow model for two-phase flow.
4. Constant properties at a given system pressure.
5. The two phases are in thermodynamic equilibrium.
6. The flow is one-dimensional flow.
Based on the conservation equations and assumptions above,the system equations are as follows:
dL+n,j
dt+= 2ui,j
+ 2Ns
Npch,jNsub,j
(L+n,j
L+n1,j
) dL+
n1,j
dt+
dM+H,j
dt+= u+
i,j +
e,ju+
e,j
d+e,j
dt+=
1 +
+e,j
ln(+e,j
)
1 +e,j
d+
j
dt++ +
e,ju+
e,j u+
i,j
(1 +e,j
)2
(1 +j
)[1 +e,j
+ ln(+e,j
)]
dM+R
dt+=
ARAH
u+e (+
e +
R )
du+edt+
=du+
i
dt+
d+
dt+
du+i,jdt+
=Ajdu+i,1dt+
+ Bj, j = 2, 3, . . . , M
du+i,1
dt+=
(dW+tot/dt+)
Mj=2
A+H,j
Bj
1 +M
j=2A+
H,jAj
(4)
where = (qpHvfg)/(AHhfg), calculating coefficient of the flowvelocity change at the inlet; Aj and Bj, calculating coefficient of
velocity, dependent on the pressure drop and mass of the two-
phase flow in the channel; vfg, difference in specific volume ofsaturated liquid and vapor (m3/kg); hfg, latent heat of evaporation
(J/kg).
Detailed contents about the system equations were presented
in the previous study ofYun et al. (2008a) and Zhang et al. (2009).
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Y. Zhang et al. / Nuclear Engineering and Design 241 (2011) 47044713 4707
2.2. Rolling motion model
The pressure drop of channels can be written as follows:
P+j
= P+f,j
+ P+a,j
+ P+g,j
+ P+I,j
+ P+add,j
(5)
where P+add
is the additional pressure drop, which is caused by
rolling motion and its specific expression can be obtained by inte-
grating along thelengthof channel. We consider the rolling motion
means solving the additional force caused by the additional pres-sure drop. In the progress of system calculation, considering the
rolling motion means putting the additional pressure drop reckon
in the momentum equation.
When the ship is under the rolling motion condition, the influ-
ence of inclination must be taken into account at the same time
since the channels are tilted too. Noticeably, when the ship is in
periodic fluctuation or translation of varying speed all the channels
have the same P+add,j
. Therefore, such motions have no influence
on the local multichannels system. However, these motions will
affect the pressure drop of the whole loop. If the ship is in periodi-
calfluctuation, the gravity pressure drop of thewhole flow channel
will be changed, and then the total mass flow will be changed too.
Hence, periodical total mass flow changing was used to simulate
the two motions. Thereby, dW+tot/dt+ is used to analyze the effectof these motions (periodical fluctuation or translation of varying
speed).
W+tot = W+
tot,0(1 +A sin(2f+t+)) (6)
where W+tot,0 =
Wtot,0/fAHusThen,
dW+totdt+
= 2f+AW+tot,0
cos(2f+t+) (7)
3. Mathematical solving method
Based on the all facts mentioned above, Eqs. (4), (5) and (7) are
combined to solve the rolling motion. Thus, the thermodynamiccharacteristics of the multichannels system under a given ocean
condition can be obtained by solving the set of non-linear ordi-
nary differential equations. The set of equations can be written as
follows:
dy
dt=
f(t, y, y, x) (8)
y(t0) = y0 (9)
where y is the state vector, [L+, M+H, M+
R , +e , u
+
i,j, W+
total, u+e ]
T. and
x is the input vector.
The input vector consists of the heat input power, inlet loss
coefficient, inlet subcooling, mass flow rate and ocean conditions
etc. We adopted the Gear multi-value method (Gear, 1974), whichdesigned especially for stiff equation system to solve the set of
equations. In the calculation the nodes of single-phase are 3 and
the upward section is looked as one control volume. The set of
equations includes 70 equations. The original step length is 10 3,
the precision of solution is 104 and the relative error is 5 105
that provided the best trade-off between calculation accuracy and
computation time.
4. Results and discussion
As shown in Fig. 2, 9-channel system is arranged symmetrically.
Four channels (channel 1, 2, 6 and 7) are located at the rolling axis
(x-axis). The other four channels (channel 3, 4, 8 and 9) are located
at the radial position (y-axis). Channel 5(CH 5) is located at the
x
z
y
13
6
8
5 2
4
7
9 channel
Fig. 2. Schematic of 9-channel system.
Table 1
The effect of inlet section length on the system stability.
Heating powerQ(kW)
Inlet sectionlength (m)
Upward sectionlength (m)
Stability
120 0.3 0 Stable
120 0.4 0 Stable
120 0.5 0 Stable
120 0.6 0 Unstable
120 0.7 0 Stable
120 0.8 0 Unstable
120 0.9 0 Unstable
origin of coordinate axis. The lengths of channel, inlet and upward
sections are 1, 00.9 and 00.3m, respectively.
In general, there are four kinds of flow oscillations in the
multichannels system, including damped oscillation, limit cycle
oscillation, chaotic oscillation and divergent oscillation. When thedamped oscillation occurs, the system is stable. However, when
the chaotic oscillation or divergent oscillation occurs, the system
becomes unstable. In the previous study, if the amplitude of limit
cycle oscillation is not great than 510%, the system is considered
to be stable. In the present study, we define the system is stable if
the amplitude of limit cycle oscillation is less than or equal to 8%,
otherwise the system is unstable.
4.1. The influence of inlet and upward sections on the system
stability
When the inlet resistance coefficient kin is 0, inlet temperature
Tin is 270C, system pressure P is 15 MPa, inlet flow rate uin is
2.75m/s, swing angular velocity Rv is 0.1 rad/s, rolling amplitude
Ra is 20, the effect of inlet and upward sections on the stability of
8-channel system had been analyzed. Specific calculation results
are shown in Tables 1 and 2.
There are seven operating conditions to analyze theinfluence of
inlet section length on the system stability in Table 1. The heating
Table 2
The effect of upward section length on the system stability.
Heating power
Q(kW)
Inlet section
length (m)
Upward section
length (m)
Stability
100 0.2 0 Stable
100 0.2 0.1 Stable
100 0.2 0.2 Unstable
100 0.2 0.3 Unstable
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4708 Y. Zhang et al. / Nuclear Engineering and Design 241 (2011) 47044713
Fig. 3. Inlet velocity oscillation curves of 9-channel system under rolling motion condition. (a) Q= 65kW, (b) Q=100 kW, (c) Q= 140kW, and (d) Q=145kW.
power Q is 120 kW, the upward section length is 0 m. The length
of inlet section increases gradually from 0.3 to 0.9 m. In Table 1, it
reveals that the influence of inlet section length on the system sta-
bilityis variable.On theone hand, theinherentstability of systemis
intensified with the increase of the single-phase section length. On
the other hand, the quotient of additional pressure drop has been
enhanced under the rolling motion condition with the increase of
the single-phase section length. The differences of additional pres-
sure drop on each channel are more obvious. Because the position
of each channel is different, which results in the flow oscillation
increasedand thesystembecome unstable.So, theinfluenceof inlet
section lengthon thesystem stabilityis variable.The data in Table 2
shows that increasing thelength of upwardsection will weakenthesystem stability.
4.2. The influence of heating power on the system instability
Fig. 3(a)(d) is the inlet velocity oscillation curves of 9-channel
system when the inlettemperature Tin is 260C (P= 13MPa) chang-
ing the heating power under the rolling motion condition. Fig. 3(a)
shows that the system is unstable when the heating power is low.
With the increase of the heating power (Fig. 3(b) and (c)), the
system becomes stable. While continuing to increase the heating
power, the system is in the unstable state of divergent oscillation
developedfrom thestable state of intertubepulse. Hence,the influ-
ence of heating power on the system instability is also variable.
The increase of heating power strengthens the system stability in
low equilibrium quality region, whereas it weakens the system
stabilityin high equilibriumquality region. Interestingly, the diver-
gent oscillation has a counterflow phenomenon when the heating
power Q is 145kW as shown is Fig. 3(d). This is attributed to the
Fig. 4. Inlet velocity oscillation curves of CH 1 under rolling motion condition (4-
channel system, P=15MPa, Tin =270
C).
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Y. Zhang et al. / Nuclear Engineering and Design 241 (2011) 47044713 4709
Fig. 5. Inlet velocity oscillation curves (a) and phase space trajectory (b) under rolling motion.
large amplitude of the oscillation, some flow oscillation back to theprevious channel.
4.3. Multiplied period phenomenon
In high equilibrium quality region, the inlet velocity oscillation
curves of CH 1 with different oscillation periods are shown in Fig. 4.
The black, red, blue and dark cyan lines are inlet velocity oscil-
lations curves of CH 1 when the heating power are 70, 90, 110
and 140 kW, respectively. (For interpretation of the references to
color in this sentence, the reader is referred to the web version of
the article.) In Fig. 4, the multiplied period phenomenon appeared
with the increase of heating power gradually. This is caused by the
nonlinear characteristics of system. Because Eqs. (4) are nonlinear
equations, there may has a periodic solution. Owing to the rollingmotion, which is a periodic effort added into the system, the multi-
pliedperiodphenomenon occurs. The blackline (Q=70kW)isaunit
flow oscillation curves. It is merely caused by the rolling motion.
The characteristic of intertube pulse of parallel multichannels sys-
temitself occurs with the increase of heating power, and these two
aspects superimpose together. The blue line is the double periodic
flowoscillation curvesandthe dark cyan line is thefourfold periodic
flow oscillation curves.
The multiplied period phenomenon usually occurs at the right
side of the MSB in high equilibrium quality region, namely, the
unstable zone. The emergence of multiplied period enhances the
flow fluctuation among channels. Thus, the interaction among
channels is strengthened resulting in the anomalistic oscillation
appears. So, that is the chaos phenomenon exactly.
4.4. Chaos phenomenon
Chaos is a non-linear phenomenon. It is impossible to use the
traditional approach (such as solving the nonlinear differential
equation) to analyze the chaos. The feasible method is analyzing
the geometry image in the space. Nearby the marginal stability
boundary (MSB) where the equilibrium quality is high, it is easy to
discover the chaos phenomenon. As shown in Fig.5 (9-channel sys-
tem, Tin =280C, Q=130kW, P= 13MPa),the flowoscillationcurves
(Fig. 5(a)) are interlaced. There are at least two chaos attractors
emerged in the phase-space trajectory (Fig. 5(b)). Usually, judging
a system whether it is chaotic or not can be based upon the chaos
attractors in the phase plane trajectory. If there are many chaos
attractors appear in the phase space trajectory, this work conditionis the chaos operating condition.
4.5. The marginal stability boundary under rolling motion
condition
The MSB of 9-channel system is shown in Fig. 6 (P=11MPa,
Rv = 0.1rad/s, Ra = 20). The system is stable inside the MSB. The
systembecomes unstable outside the MSB at the two phase region.
In the low equilibrium quality region, the instability is caused by
the inlet section. While in the high equilibrium quality region,
the instability results from the inherent characteristic of the sys-
tem, which means the true intertube pulse led to the instability.
Moreover, even without rolling condition the intertube pulse will
also come into being. But under this circumstance, the flow oscil-lation results from both the intertube pulse of the system and
the flow fluctuation, which is caused by rolling motion at the
same time. In the low subcooling region, the subcooling has great
affects on the system instability and it is not single-value. On the
one hand, the length of single-phase region is increased at the
inlet section with the increase of inlet subcooling number. The
Fig. 6. The MSB of 9-channel system (P= 11MPa).
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4710 Y. Zhang et al. / Nuclear Engineering and Design 241 (2011) 47044713
Fig. 7. The MSBs of 4-channel system under rolling motion condition.
single-phase liquid has a well stability, which increased the inletresistance. Thereby, the system stability is enhanced. On the other
hand, the increasing of inlet subcooling number decreases the quo-
tient of equilibrium quality at the inlet section. It increases the
growth circulate period of bubble. Therefore, the time of evap-
orating grows is prolonged. This induces intertube pulse occurs
and weakens the system stability. The influence of low subcool-
ing on the system instability is multi-valued because the two sides
mentioned above are added together. In the low inlet subcooling
region, because the inlet temperature is close to the saturation
temperature of water under 11 MPa, therefore the length of two-
phase section is increased and the unstable probability of system
is high.
In the high inlet subcooling region, the influence of subcooling
on the system stability is also multi-valued. When the subcool-ing is constant, there is a critical value either. At this region,
the extremely high subcooling makes the equilibrium quality
decrease sharply, the growth circulate period of bubble has been
prolonged. Therefore, the unstable probability of system is also
high.
4.6. The MSB of multichannels system under rolling condition
As shown in Fig. 7, the shape of MSBs for 4-channel system
(under 7, 9, 11, 13 and 15 MPa) is a polygon. They seem similar
and the area of each MSB is nearly identical. The MSBs shift to left
with the increase of pressure. It means the system can get into
the stable region more quickly from the unstable region when the
pressure is increased. But we cannot conclude that the system ismore stable when the pressure is increased. This is different from
the non-rolling condition. Usually, the system will become more
stable when the pressure is increased under the non-rolling condi-
tion. However, due to the influence of rolling motion, the effect of
pressure on the system stability is weakened. When the pressures
are 13 and 15 MPa, respectively, some operating condition points
on the MSBs cross the equilibrium quality line (Xe = 0). It means
because of the rolling motion, even at the single-phase region, the
system may be unstable.
The MSBs of 9-channel system (under 7, 9, 11, 13 and 15 MPa)
are shown in Fig. 8. It is evident that the shape of MSBs for 9-
channel system is a quadrilateral. It is notably that there are some
differences between the MSBs for 4-channel system and 9-channel
system. Firstly, in the high equilibrium quality region when the
Fig. 8. The MSBs of 9-channel system under rolling motion condition.
inlet subcooling number is about 1.5, the MSB of 4-channel system
has a salient compared with that of 9-channel system. We sup-
pose that the flow rate (amplitude) for 9-channel can be averaged
into other more channels compared with 4-channel system. So, the
influence of rolling motion is weakened. Therefore, the MSBs of
9-channel system are much slippier than that of 4-channel sys-
tem. Secondly, the area of MSB for 4-channel system is larger than
that of 9-channel system (as shown in Fig. 9). Because the influ-
ence of rolling motion on the system stability can be replaced by
the influence of pressure drop of channels on the system stabil-
ity. Fig. 2 shows 9-channel system has more channels (CH 5-9)
compared with 4-channel system. Thus, the total pressure drop of
9-channelsystem is largerthan that of 4-channelsystem. Theinflu-
ence of rolling motion on the system stabilityfor 9-channel systemis greater than that of 4-channel system. So, the 4-channel system
is more stable than 9-channel system under this condition. Some
researchers said the system with more channels is more stable.
Nevertheless, this rule is notapplies to thesystem under therolling
condition.
Fig. 9. The MSBs of 4 and 9-channel system (P=9 MPa).
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Y. Zhang et al. / Nuclear Engineering and Design 241 (2011) 47044713 4711
Fig. 10. The stability space of 4-channel system.
4.7. Three-dimensional stability space
In almost all the investigations of flow instability under rolling
motion condition, the MSB is only a simple curve at two-
dimensional coordinate. A concept of stability space (the stability
island) is presentedin thepresent work. Thesystem stabilitycan be
described in the three-dimensional space. The three-dimensional
stability space is made up of phase change number (Npch), subcool-
ing number (Nsub) and nondimensional pressure (P+). We defined
the nondimensionalpressureP+=P/(10Patm) forconvenience, where
Patm is atmospheric pressure.
The stability spaces for 4 and 9-channel system are shown inFigs. 10 and 11, respectively. The stability space is made up of the
MSBs under different system pressures (such as 7, 9, 11, 13 and
15 MPa).
Fig. 11. The stability space of 9-channel system.
Fig. 12. The MSBs of 4-channel system with different rolling amplitudes
(P= 13MPa).
4.8. The Influence of rolling amplitudes
Fig. 12 is the MSBs of 4-channel system with different rolling
amplitudes (P= 13 MPa). The system is stable when the operating
condition point is inside the MSB. When the operating condition
point is outside the MSB at the two-phase region, the system is
unstable. This figure illustrates that the increase of rolling ampli-
tudes will destabilize the system stability. Since the area of the
MSBs are decreased with the increase of rolling amplitudes.
4.9. The influence of rolling condition on the system stability
The inlet velocity oscillation curves of rolling and non-rolling
conditions are shown in Fig. 13(a) and (b), respectively. These
two instances are under the same operating condition (P=11MPa,
Tin =220 C). The inlet velocity oscillation curve of 4-channel sys-tem under rolling motion condition is shown in Fig. 13(a). In this
figure the flow oscillation curves are moved up compared with the
equilibrium position. Based on the datum line (ui+ = 1), the flow
oscillation amplitudes of upper part are greater than that of lower
part. So, the system is unstable. The inlet velocity oscillation curve
of non-rolling motion condition is shown in Fig. 13(b). It is obvious
that thesystemcomesbackto itsequilibrium positionafterbe given
a sudden disturbance at the 50th second. Therefore, the system
is stable. For these two operating conditions, the system is sta-
ble when the heating power below 170 kW under the non-rolling
motion condition. While, the system stable region is between 105
and 150 kW for the rolling motion condition. So, we can conclude
the rolling motion causes the system instability occurs in advance,
which results in the system become more unstable.
4.10. The influence of channel number on the system stability
The homogeneous flow model is adopted to deal with the two-
phaseflow of the multichannels system underthe rolling condition.
The previous studies (such as Yun et al., 2008b) and the results in
this work indicated that the homogeneous flow model can accu-
rately predict the MSB and the major characteristics of limit cycle
oscillations under the middle andhigh systempressure conditions.
The effect of interaction among parallel channels on the system
stability can be analyzed to extrapolate the model in parallel mul-
tichannels system with different channel numbers. The MSBs of
different channel number systems can also be obtained. Never-
theless, the homogeneous flow model neglects the slip, which
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Fig. 13. Inlet velocity oscillation curves of rolling condition (a) and non-rolling condition (b).
may strengthen the system stability (Lahey and Podowski, 1989),between two phases. Therefore, the homogeneous flow model is
conservativein terms of predicting theMSB. Moreover,the increas-
ing channel number strengthens the interaction among channels.
It will interfere in the analysis on the system instability.
5. Conclusions
The present research in this paper extended the models of Lee
and Pan (1999) to analyze the multichannels system considering
the inlet and upward sections (Clausse and Lahey, 1990) under
the rolling motion. In the present model, the homogeneous flow
assumption is adopted for two-phase flow. Generally speaking, the
homogeneousflowmodelcandescribethetwo-phaseflowinstabil-ity of parallel multichannels system under middle or high pressure
condition. But the drawback of this model is neglect the possi-
ble thermodynamic and hydraulic disequilibrium between phases.
Because of the slip effect between the two phases is not consid-
ered in this model, and the slip effect can stabilize the system
stability. Therefore, the predicted results of the characteristics of
two-phase flow will leans conservative. Especially at the condi-
tion of low pressure, high equilibrium quality and heat transfer
rate or fast transient process, the forecast error is obvious. More-
over, the interaction among channels will be enhanced with the
increase of channel number. Thus, the model predicted results will
be influenced, andthe credibility of systemstability which is calcu-
lated by this model will be reduced. The two-phase flow instability
in the parallel multichannels system under rolling motion con-
dition had been investigated. Some conclusions obtained are as
follows:
(1) The parallel multichannels system has four unstable regions,
namely low andhigh equilibrium quality regions and inlet sub-
cooling regions under the rolling motion condition. Increasing
the length of upward section can weaken the system stability.
(2) The influence of heating power on thesystem instability is vari-
able. In the low equilibrium quality region, the system stability
is intensified with the increase of heating power. While in the
high equilibrium quality region, increasing the heating power
can weaken the system stability.
(3) The multiplied period phenomenon appears with the increase
of heating power. Nearby the MSB of high equilibrium quality
region, the chaos phenomenon emerges under some operatingconditions.
(4) Because of the rolling motion, the effect of pressure on the sys-
tem stability is not obvious. The MSBs shift to left with the
increase of pressure on the plane ofNpch and Nsub.
(5) The three-dimensional stability spaces of parallel multichan-
nels systems are obtained under the rolling motion condition.
(6) The system will become more unstable with the increase of
rolling amplitudes.
(7) The critical power and the system instability will appear ahead
of time since the rolling motion.
Acknowledgments
This work has been performed in the frameworkof the program
of the New Century Excellent Talents in University (NCET-06-0837)
andsupported by theNationalNatural Science Foundation of China
(10675096).
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