# Analysis of the NUPEC PSBT Tests with FLICA-OVAP

Authors: Matteo Bucci; Philippe Fillion
Journal: Science and Technology of Nuclear Installations
 (2012)

---

## Abstract

This paper discusses the results of a computational activity devoted to the prediction of two-phase flows in subchannels and in rod bundles. The capabilities of the FLICA-OVAP code have been tested against an extensive experimental database made available by the Japanese Nuclear Power Energy Corporation (NUPEC) in the frame of the PWR subchannel and bundle tests (PSBT) international benchmark promoted by OECD and NRC. The experimental tests herein addressed involve void fraction distributions and boiling crisis phenomena in rod bundles with uniform and nonuniform heat flux conditions. Both steady-state and transient scenarios have been addressed, including power increase, flow reduction, temperature increase, and depressurization, representative of PWR thermal-hydraulics conditions. After a brief description of the main features of FLICA-OVAP, the relevant physical models available within the code are detailed. Results obtained in the different tests included in the PSBT void distribution and DNB benchmarks are therefore reported. The relevant role of selected physical models is discussed.


---

## Body

## 1. Introduction

Based on NUPEC PWR subchannel and bundle tests (PSBT), an international benchmark has been promoted by OECD and NRC and has been coordinated by Penn State University [1]. The aim of this benchmark is to encourage advancement and assessment of numerical models in subchannel analysis of fluid flow in rod bundles, which has very important relevance for the nuclear reactor safety margin evaluation. An important database of void fraction and critical heat flux measurements in steady-state and transient conditions has been carried out by NUPEC on a prototypical PWR rod bundle. Different types of subchannel or rod bundle geometries and a wide range of flow conditions at high pressure have been investigated (see Table 1) allowing the assessment of the key models and correlations in these conditions.Table 1
Operating conditions of the NUPEC PWR test facility.
Quantity
Range
Pressure
4.9–16.6 MPa
Mass flux
550–4150 kg/m2/s
Inlet coolant temperature
140–345°C
Wall heat flux
0.37–1.86 MW/m2The Service de Thermohydraulique et de Mécanique des fluides (STMF) at the Commissariat à l’Energie Atomique et aux Energies Alternatives (CEA), France, has been involved in the PSBT benchmark performing calculations with the FLICA-OVAP code [2]. FLICA-OVAP is an advanced two-phase flow thermal-hydraulics code based on a full 3D subchannel approach. It is designed to analyze flows in light water reactors cores such as PWRs, BWRs, and experimental reactors. To provide a relevant answer to different core concepts and multiple industrial applications, several models coexist in the FLICA-OVAP platform: the homogeneous equilibrium model, the four equations drift flux model, the two-fluid model, and finally, a general multifield model, with a variable number of fields for both vapor and liquid phases. For each model, an adapted set of closure laws is proposed concerning heat and mass transfer, interfacial and wall forces, and turbulence.


## 2. The FLICA-OVAP Code

A detailed description of the FLICA-OVAP code can be found in [3]. In this section we give a summary description of the four-equation drift flux model and the relevant closure laws adopted in this analysis. Details of the models adopted to predict boiling crisis in the PSBT benchmark will be also presented extensively.


### 2.1. The Four-Equation Drift Flux Model

The four balance equations describing two-phase flows in the drift flux model are, respectively, the mixture mass balance equation, the mixture momentum balance equation, the mixture energy balance equation, and the steam mass balance equation (porosities are omitted for the sake of simplicity):(i)
mixture mass conservation(1)∂∂t(∑k=v,lαkρk)+∇·(∑k=v,lαkρkuk)=0,whereαk,ρk,uk are the volume fraction, the density, and the velocity for the phase k.(ii)
mixture momentum balance(2)∂∂t(∑k=v,lαkρkuk)+∇·(∑k=v,lαkρkuk⊗uk)222+∇P-∇·(∑k=v,lαkτk__)=ρg+Fw,whereP is the pressure, g, the gravity, and Fw, the friction forces. The tensor τk__ represents the viscous and the Reynolds stress terms for the phase k. The mixture density ρ is defined as
(3)ρ=∑k=v,lαkρk.(iii)
mixture energy balance(4)∂∂t(∑k=v,lαkρkEk)+∇·(∑k=v,lαkρkHkuk)222-∇·(∑k=v,lαkqk)=qw+ρg·u,whereEk and Hk are the total energy and the total enthalpy of the phase k,qk includes molecular and turbulent heat fluxes, and qw is the volumetric source term of thermal power.(iv)
steam mass(5)∂∂t(αvρv)+∇·(αvρvuv)-∇·(Kc∇c)=Γv,The model is closed by a drift flux correlation and a general equation of state with the assumption that, in presence of liquid, the vapor is in saturation conditions.


### 2.2. The Drift Flux Correlation

FLICA-OVAP includes several Zuber-Findlay type correlations in order to estimate the relative velocityur between the vapor velocity uv and the liquid velocity ul. The general form of these correlations is:
(6)uv=C0〈j〉+〈〈vg,j〉〉=C0〈j〉+〈Vg,j〉,
where C0 is the distribution parameter, 〈j〉=αuv+(1-α)ul is the area-averaged total volumetric flux, and Vg,j is the void-weighted area-averaged drift velocity. The Chexal-Lellouche correlation [4] and a correlation derived from Ishii [5] are implemented in the code. The Chexal-Lellouche correlation covers a large range of pressure, diameters, flows whereas the Ishii correlation, firstly established for bubbly, slug, and churn turbulent flow in adiabatic conditions, allows taking into account nucleate boiling on heated walls.


### 2.3. Pressure Drop

Friction forcesFw are given by the sum of distributed Ffric and singular pressure drops Fsing(7)Fw=Fsing+Ffric.
Singular friction due to spacer or mixing grids or other pressure drops are given by
(8)Fsing=-12ρK__sing∥u∥u,
where K__sing is an antisymmetric tensor. Distributed friction at walls is instead accounted for by
(9)Ffric=-12Dhρ(fwXfwYfwZ),
where the different friction terms fw are given by the product of the isothermal friction factor fiso, the heating wall correction fheat, and the two-phase flow multiplier f2ϕ. The isothermal friction factor in turbulent flows is given by
(10)fiso=0.194Re-0.2,
whereas the heating wall correction was estimated by an in-house model already used in the FLICA-4 code [6]. In this analysis the Chisholm correlation [7] was used for f2ϕ, given by
(11)f2ϕ=1+(ϕlo2-1)(1+DheatDhCϕq′′),
where ϕlo2 is the adiabatic two-phase frictional pressure drop multiplier, Cϕ, a parameter accounting for heat flux, Dheat is the heated diameter, and q′′, the wall heat flux. In the runs of the PSBT benchmark Cϕ was set equal to 0 and thus f2ϕ=ϕlo2.


### 2.4. Diffusion Effects

To account for viscous and turbulent diffusion effects, the tensorτk__ is introduced in the momentum equation, given by
(12)τkij=μk(1+Mt,kij)(∂uki∂xj+∂ukj∂xi-23∑l=x,y,z∂ukl∂xlδij),
where μkMt,kij is the turbulent viscosity, which is limited to the liquid phase. An anisotropic formulation is used for turbulent viscosity
(13)Mt,lij=Mt0ij(Re-Ret)bMfM(f2φ),
where Re=GDh/μl is the Reynolds number, Mt0ij, bM, Ret are parameters, and fM(f2φ) is a function of the two-phase flow multiplier.Similarly, molecular and turbulent heat fluxes are given by(14)∑k=v,lαkqk=λlCpl(1__+K__t,l)∇hx,
where hx=xhv+(1-x)hl is the flow enthalpy based on the flow quality x. The turbulent conductivity is given by
(15)Kt,lij=Kt0ij(Re-Ret)bKfK(f2φ),
where Kt0ij,bK,Ret are parameters and fK(f2φ) is a function of the two-phase flow multiplier. In this analysis, the value of Mt0ij and Kt0ij was varied as a function of the axial position. Two different values have been adopted for each parameter depending whether the considered axial position was downward a mixing or a spacer grid.


### 2.5. Wall Temperature

Wall temperatures are estimated on the basis of the bulk temperature and the heat transfer coefficient as(16)Tw=Tb+q′′h=Tb+q′′Nuλ/Dh.
The Nusselt number and the bulk temperature depend on the heat transfer regime. Four different regimes can be distinguished: single-phase convection heat transfer, subcooled nucleate boiling (SNB), saturated nucleate boiling (SANB) and post-critical-heat-flux (post-CHF) heat transfer. In single-phase heat transfer and SNB, the bulk temperature is equal to the liquid phase temperature, whereas in SANB it is equal to the saturation temperature. In forced convection conditions, the single-phase heat transfer coefficient is estimated by the Dittus-Boelter correlation. The onset of significant void (OSV), which is the transition between single-phase heat transfer and SNB can be predicted with the Forster and Grief correlation in low-pressure conditions or the Jens and Lottes correlation in high pressure conditions. In the present analysis, the Jens and Lottes correlation was used [8], which allows estimating the minimum wall superheat ΔTsat demanded to achieve net vapor generation
(17)ΔTsat=7.91(q′′104)0.25exp(-P62·105).
Vapor generation starts when wall temperature estimated with Dittus-Boelter correlation exceeds this value. Finally, in post-CHF conditions, the choice of correlation depends on the boiling characteristics, whether it is IAFB (inverted annular film boiling) or DFFB (dispersed flow film boiling).


### 2.6.  The Mass Transfer TermΓv

The mass transfer termΓv appearing in the steam mass balance equation is given by the sum of two contributions: the vapor generation on walls Γwv and the mass transfer between the liquid and the vapor phase Γvl. In subcooled nucleate boiling, only a portion χv of the heat flux transferred from the wall to the mixture is used to vaporize the liquid phase, whereas the remaining part is used to heat the liquid phase up.The vapor generation at walls is thus given by(18)Γwv=χvq′′hlv4Dheat,
where χv is a function of the saturation temperature, the liquid phase temperature, and the wall superheat demanded to have subcooled nucleate boiling, given by
(19)χv=Tw,lc-Tsat-ΔTsatTw,lc-Tl-ΔTsat.
If the mixture is in saturation conditions, it is χv=1.The mass transfer between the two phasesΓvl is instead given by
(20)Γlv=qvlhv-hl,
where hv and hl are vapor and liquid enthalpy and qvl is the heat transferred between the two phases, given by
(21)qvl=Kv0G2log(1+Re/Re0)f(P,ρ,μl,u,ur)ρc(c*-c)1-c,
where Kv0 is a mass transfer parameter, G is the mass flux, Re=GDh/μl is the Reynolds number, c*, the equilibrium quality based on the mixture enthalpy h=chv+(1-c)hl, f(P,ρ,μl,u,ur), a function depending on local conditions, Dh, the hydraulic diameter, and μl, the liquid viscosity. Re0 is a parameter of the model.


## 2.1. The Four-Equation Drift Flux Model

The four balance equations describing two-phase flows in the drift flux model are, respectively, the mixture mass balance equation, the mixture momentum balance equation, the mixture energy balance equation, and the steam mass balance equation (porosities are omitted for the sake of simplicity):(i)
mixture mass conservation(1)∂∂t(∑k=v,lαkρk)+∇·(∑k=v,lαkρkuk)=0,whereαk,ρk,uk are the volume fraction, the density, and the velocity for the phase k.(ii)
mixture momentum balance(2)∂∂t(∑k=v,lαkρkuk)+∇·(∑k=v,lαkρkuk⊗uk)222+∇P-∇·(∑k=v,lαkτk__)=ρg+Fw,whereP is the pressure, g, the gravity, and Fw, the friction forces. The tensor τk__ represents the viscous and the Reynolds stress terms for the phase k. The mixture density ρ is defined as
(3)ρ=∑k=v,lαkρk.(iii)
mixture energy balance(4)∂∂t(∑k=v,lαkρkEk)+∇·(∑k=v,lαkρkHkuk)222-∇·(∑k=v,lαkqk)=qw+ρg·u,whereEk and Hk are the total energy and the total enthalpy of the phase k,qk includes molecular and turbulent heat fluxes, and qw is the volumetric source term of thermal power.(iv)
steam mass(5)∂∂t(αvρv)+∇·(αvρvuv)-∇·(Kc∇c)=Γv,The model is closed by a drift flux correlation and a general equation of state with the assumption that, in presence of liquid, the vapor is in saturation conditions.


## 2.2. The Drift Flux Correlation

FLICA-OVAP includes several Zuber-Findlay type correlations in order to estimate the relative velocityur between the vapor velocity uv and the liquid velocity ul. The general form of these correlations is:
(6)uv=C0〈j〉+〈〈vg,j〉〉=C0〈j〉+〈Vg,j〉,
where C0 is the distribution parameter, 〈j〉=αuv+(1-α)ul is the area-averaged total volumetric flux, and Vg,j is the void-weighted area-averaged drift velocity. The Chexal-Lellouche correlation [4] and a correlation derived from Ishii [5] are implemented in the code. The Chexal-Lellouche correlation covers a large range of pressure, diameters, flows whereas the Ishii correlation, firstly established for bubbly, slug, and churn turbulent flow in adiabatic conditions, allows taking into account nucleate boiling on heated walls.


## 2.3. Pressure Drop

Friction forcesFw are given by the sum of distributed Ffric and singular pressure drops Fsing(7)Fw=Fsing+Ffric.
Singular friction due to spacer or mixing grids or other pressure drops are given by
(8)Fsing=-12ρK__sing∥u∥u,
where K__sing is an antisymmetric tensor. Distributed friction at walls is instead accounted for by
(9)Ffric=-12Dhρ(fwXfwYfwZ),
where the different friction terms fw are given by the product of the isothermal friction factor fiso, the heating wall correction fheat, and the two-phase flow multiplier f2ϕ. The isothermal friction factor in turbulent flows is given by
(10)fiso=0.194Re-0.2,
whereas the heating wall correction was estimated by an in-house model already used in the FLICA-4 code [6]. In this analysis the Chisholm correlation [7] was used for f2ϕ, given by
(11)f2ϕ=1+(ϕlo2-1)(1+DheatDhCϕq′′),
where ϕlo2 is the adiabatic two-phase frictional pressure drop multiplier, Cϕ, a parameter accounting for heat flux, Dheat is the heated diameter, and q′′, the wall heat flux. In the runs of the PSBT benchmark Cϕ was set equal to 0 and thus f2ϕ=ϕlo2.


## 2.4. Diffusion Effects

To account for viscous and turbulent diffusion effects, the tensorτk__ is introduced in the momentum equation, given by
(12)τkij=μk(1+Mt,kij)(∂uki∂xj+∂ukj∂xi-23∑l=x,y,z∂ukl∂xlδij),
where μkMt,kij is the turbulent viscosity, which is limited to the liquid phase. An anisotropic formulation is used for turbulent viscosity
(13)Mt,lij=Mt0ij(Re-Ret)bMfM(f2φ),
where Re=GDh/μl is the Reynolds number, Mt0ij, bM, Ret are parameters, and fM(f2φ) is a function of the two-phase flow multiplier.Similarly, molecular and turbulent heat fluxes are given by(14)∑k=v,lαkqk=λlCpl(1__+K__t,l)∇hx,
where hx=xhv+(1-x)hl is the flow enthalpy based on the flow quality x. The turbulent conductivity is given by
(15)Kt,lij=Kt0ij(Re-Ret)bKfK(f2φ),
where Kt0ij,bK,Ret are parameters and fK(f2φ) is a function of the two-phase flow multiplier. In this analysis, the value of Mt0ij and Kt0ij was varied as a function of the axial position. Two different values have been adopted for each parameter depending whether the considered axial position was downward a mixing or a spacer grid.


## 2.5. Wall Temperature

Wall temperatures are estimated on the basis of the bulk temperature and the heat transfer coefficient as(16)Tw=Tb+q′′h=Tb+q′′Nuλ/Dh.
The Nusselt number and the bulk temperature depend on the heat transfer regime. Four different regimes can be distinguished: single-phase convection heat transfer, subcooled nucleate boiling (SNB), saturated nucleate boiling (SANB) and post-critical-heat-flux (post-CHF) heat transfer. In single-phase heat transfer and SNB, the bulk temperature is equal to the liquid phase temperature, whereas in SANB it is equal to the saturation temperature. In forced convection conditions, the single-phase heat transfer coefficient is estimated by the Dittus-Boelter correlation. The onset of significant void (OSV), which is the transition between single-phase heat transfer and SNB can be predicted with the Forster and Grief correlation in low-pressure conditions or the Jens and Lottes correlation in high pressure conditions. In the present analysis, the Jens and Lottes correlation was used [8], which allows estimating the minimum wall superheat ΔTsat demanded to achieve net vapor generation
(17)ΔTsat=7.91(q′′104)0.25exp(-P62·105).
Vapor generation starts when wall temperature estimated with Dittus-Boelter correlation exceeds this value. Finally, in post-CHF conditions, the choice of correlation depends on the boiling characteristics, whether it is IAFB (inverted annular film boiling) or DFFB (dispersed flow film boiling).


## 2.6.  The Mass Transfer TermΓv

The mass transfer termΓv appearing in the steam mass balance equation is given by the sum of two contributions: the vapor generation on walls Γwv and the mass transfer between the liquid and the vapor phase Γvl. In subcooled nucleate boiling, only a portion χv of the heat flux transferred from the wall to the mixture is used to vaporize the liquid phase, whereas the remaining part is used to heat the liquid phase up.The vapor generation at walls is thus given by(18)Γwv=χvq′′hlv4Dheat,
where χv is a function of the saturation temperature, the liquid phase temperature, and the wall superheat demanded to have subcooled nucleate boiling, given by
(19)χv=Tw,lc-Tsat-ΔTsatTw,lc-Tl-ΔTsat.
If the mixture is in saturation conditions, it is χv=1.The mass transfer between the two phasesΓvl is instead given by
(20)Γlv=qvlhv-hl,
where hv and hl are vapor and liquid enthalpy and qvl is the heat transferred between the two phases, given by
(21)qvl=Kv0G2log(1+Re/Re0)f(P,ρ,μl,u,ur)ρc(c*-c)1-c,
where Kv0 is a mass transfer parameter, G is the mass flux, Re=GDh/μl is the Reynolds number, c*, the equilibrium quality based on the mixture enthalpy h=chv+(1-c)hl, f(P,ρ,μl,u,ur), a function depending on local conditions, Dh, the hydraulic diameter, and μl, the liquid viscosity. Re0 is a parameter of the model.


## 3. Prediction of the Boiling Crisis

To predict boiling crisis conditions, several models are currently available within FLICA-OVAP. The W3 correlation [9] is appropriate to predict departure from nucleate boiling (DNB) phenomena of interest for pressurized water reactors. However, boiling crisis experienced in NUPEC tests can be close to dryout conditions. Two models have been therefore implemented in the code: the model of Shah [10] and the model of Katto and Ohno [11]. Both models can predict critical heat flux values for both DNB and dryout conditions. An accurate description of them is given in the following sections.


### 3.1.  The Shah Model

The Shah model [10] consists of two separate correlations to determine the boiling number Bo, defined as
(22)Bo=qchf′′Ghlv.
The first correlation covers conditions where the critical heat flux depends on the upstream conditions, named UCC (upstream conditions correlation). The second, named LCC (local conditions correlation), depends only on local quantities.


#### 3.1.1. The UCC Correlation

The UCC correlation is(23)Bo=0.124(Dzeff)0.89(104Y)n(1-xi,eff),
with
(24)Y=[GDCpfλf][G2ρf2gD]0.4[μfμg]0.6.
In the previous equations, zeff is the effective tube length and xi,eff is the effective inlet quality, defined as
(25)xi,eff=xi,zeff=zcrit,forxi<0,xi,eff=0,zeff=zsat,forxi>0,
where zcrit is the distance from the inlet section and the location of the boiling crisis, where the critical heat flux is calculated, and zsat is the boiling length, which for uniformly heated tubes is given by
(26)zsatD=zcritD+xi4Bo.
For water flows, when Y≤104,n=0, otherwise it is given by
(27)n=(Dzeff)0.54forY≤106,n=0.12(1-Xi,eff)0.5forY>106.


#### 3.1.2. The LCC Correlation

The LCC correlation is expressed by(28)Bo=FEFXBo0.
The entrance factor FE is given by
(29)FE=1.54-0.032(zcritD).
When the previous correlation gives FE<1, it is used FE=1.B
o
0 is defined as the boiling number at xcrit=0, given by the maximum value obtained by the following equations
(30)Bo0=15Y-0.612,Bo0=0.082Y-0.3(1+1.45Pr4.03),Bo0=0.0024Y-0.105(1+1.15Pr3.39),
where Pr is the reduced pressure given by Pr=P/Pc where Pc is the critical pressure, that is 22.064 MPa for water. The value of FX depends on the quality at the location of the boiling crisis xcrit. When xcrit>0, the following equation is used
(31)FX=F3[1+(F3-0.29-1)(Pr-0.6)0.35]c.
When Pr>0.6,c=1, otherwise c=0. F3 is instead given by
(32)F3=(1.25×105Y)0.833xcrit.
When xcrit<0, FX is given by
(33)FX=F1[1-(1-F2)(Pr-0.6)0.35]b.
As in the previous case, when Pr>0.6,b=1, otherwise b=0. F1 is given by
(34)F1=1+0.0052(-xcrit0.88)Y0.41forY≤1.4×107,F1=1+0.0052(-xcrit0.88)(1.4×107)0.41forY>1.4×107.
Finally, F2 is given by
(35)F2=F1-0.42forF1≤4,F2=0.55forF1>4.


#### 3.1.3. Choice between UCC and LCC Correlation

For water, the UCC correlation is used whenY≤106. When Y>106, the correlation giving the lower value of the boiling number Bo is used, with exception of cases where zeff>160/Pr1.14, for which the UCC formulation is always adopted. In this analysis, the UCC correlation was used in all calculations.


#### 3.1.4. Range Covered by the Shah Correlation

The Shah correlation was tested against 62 experimental databases with 23 different fluids, covering the following operating conditions:(i)
0.315×10-3<D<37.5×10-3 m,(ii)
1.3<z/D<940,(iii)
4<G<29051 kg/m2/s,(iv)
-4<xi<0.85,(v)
-2.6<xcrit<1.Only 15 tests over the whole database are not included in the range covered by the Shah correlation. In Table2 the values of experimental quantities relevant for the Shah model are reported.Table 2
Range of parameters for the Shah model covered by the NUPEC tests.
D [m]
z/D
G (max/min)
x
i (max/min)
x
crit (max/min)
Series 0
0.009711
376.67
4944.4/1408.3
−0.062/−0.96
0.49/−0.20
Series 2
0.009711
376.67
4769.4/316.7
−0.053/−0.97
1.00/−0.06
Series 3
0.009989
366.21
4702.8/1361.1
−0.045/−0.87
0.58/−0.05
Series 4
0.009711
376.67
4725.0/566.7
−0.058/−0.98
1.00/0.06
Series 13
0.009711
376.67
3861.1/1361.1
−0.057/−0.50
0.50/0.20
Series 8
0.008867
412.55
4816.7/575.0
−0.058/−0.97
1.00/0.11


### 3.2. The Katto and Ohno Model

The correlation of Katto and Ohno [11] provides the value of the critical heat flux as
(36)qchf′′=XG(hlv+KΔhsub,i),
where Δhsub,i is the subcooling inlet enthalpy. The terms X and K are functions of three-dimensionless terms:
(37)Z′=zD,R′=ρgρf,W′=σρf(G2z).
Five different values of X must be determined
(38)X1=CW'0.043Z',X2=0.1R'0.133W'0.3331+0.0031Z',X3=0.098R'0.133W'0.433Z'0.271+0.0031Z',X4=0.0384R'0.6W'0.1731+0.28W'0.233Z',X5=0.234R'0.513W'0.433Z'0.271+0.0031Z'.
The value of C in the relationship of X1 is given by
(39)C=0.25forZ′<50,C=0.25+0.0009(Z′-50)for50<Z′<150,C=0.34forZ′>150.
Three values of K must be determined
(40)K1=0.261CW'0.043,(41)K2=0.833[0.0124+(1/Z')]R'0.133W'0.333,(42)K3=1.12[1.52W'0.233+(1/Z')]R'0.6W'0.173.
The appropriate values of X and K must be determined according to Table 3.Table 3
Choice ofX and K for the Katto and Ohno model.
R
'
<
0.15
R
'
>
0.15
X
1
<
X
2
X
=
X
1
X
1
<
X
5
X
=
X
1
X
1
>
X
2
X
2
<
X
3
}
X
=
X
2
X
1
>
X
5
X
5
>
X
4
}
X
=
X
5
X
1
>
X
2
X
2
>
X
3
}
X
=
X
3
X
1
>
X
5
X
5
<
X
4
}
X
=
X
4
K
1
>
K
2
K
=
K
1
K
1
>
K
2
K
=
K
1
K
1
<
K
2
K
=
K
2
K
1
<
K
2
K
2
<
K
3
}
K
=
K
2
K
1
<
K
2
K
2
>
K
3
}
K
=
K
3


#### 3.2.1. Range Covered by the Katto and Ohno Correlation

The Katto and Ohno correlation covers the following operating conditions:(i)
0.01<z<8.8 m,(ii)
0.001<D<0.038 m,(iii)
5<Z′<880,(iv)
0.0003<R′<0.41,(v)
3×10-9<W′<2×10-2.All experimental tests are included in the range covered by the Katto and Ohno correlation (see Table4).Table 4
Range of parameters for the Katto and Ohno model covered by the NUPEC tests.
Z [m]
D [m]
Z
′
R
′ (max/min)
W
′ (max/min)
Series 0
3.658
0.009711
376.67
0.159185/0.070185
1.28 × 10−6/3.97 × 10−8
Series 2
3.658
0.009711
376.67
0.158337/0.030672
5.04 × 10−5/4.13 × 10−8
Series 3
3.658
0.009989
366.21
0.156657/0.070549
1.33 × 10−6/4.28 × 10−8
Series 4
3.658
0.009711
376.67
0.156156/0.031256
1.35 × 10−5/4.17 × 10−8
Series 13
3.658
0.009711
376.67
0.156156/0.096048
6.76 × 10−7/8.28 × 10−8
Series 8
3.658
0.008867
412.55
0.156323/0.031191
1.48 × 10−5/3.99 × 10−8


## 3.1.  The Shah Model

The Shah model [10] consists of two separate correlations to determine the boiling number Bo, defined as
(22)Bo=qchf′′Ghlv.
The first correlation covers conditions where the critical heat flux depends on the upstream conditions, named UCC (upstream conditions correlation). The second, named LCC (local conditions correlation), depends only on local quantities.


### 3.1.1. The UCC Correlation

The UCC correlation is(23)Bo=0.124(Dzeff)0.89(104Y)n(1-xi,eff),
with
(24)Y=[GDCpfλf][G2ρf2gD]0.4[μfμg]0.6.
In the previous equations, zeff is the effective tube length and xi,eff is the effective inlet quality, defined as
(25)xi,eff=xi,zeff=zcrit,forxi<0,xi,eff=0,zeff=zsat,forxi>0,
where zcrit is the distance from the inlet section and the location of the boiling crisis, where the critical heat flux is calculated, and zsat is the boiling length, which for uniformly heated tubes is given by
(26)zsatD=zcritD+xi4Bo.
For water flows, when Y≤104,n=0, otherwise it is given by
(27)n=(Dzeff)0.54forY≤106,n=0.12(1-Xi,eff)0.5forY>106.


### 3.1.2. The LCC Correlation

The LCC correlation is expressed by(28)Bo=FEFXBo0.
The entrance factor FE is given by
(29)FE=1.54-0.032(zcritD).
When the previous correlation gives FE<1, it is used FE=1.B
o
0 is defined as the boiling number at xcrit=0, given by the maximum value obtained by the following equations
(30)Bo0=15Y-0.612,Bo0=0.082Y-0.3(1+1.45Pr4.03),Bo0=0.0024Y-0.105(1+1.15Pr3.39),
where Pr is the reduced pressure given by Pr=P/Pc where Pc is the critical pressure, that is 22.064 MPa for water. The value of FX depends on the quality at the location of the boiling crisis xcrit. When xcrit>0, the following equation is used
(31)FX=F3[1+(F3-0.29-1)(Pr-0.6)0.35]c.
When Pr>0.6,c=1, otherwise c=0. F3 is instead given by
(32)F3=(1.25×105Y)0.833xcrit.
When xcrit<0, FX is given by
(33)FX=F1[1-(1-F2)(Pr-0.6)0.35]b.
As in the previous case, when Pr>0.6,b=1, otherwise b=0. F1 is given by
(34)F1=1+0.0052(-xcrit0.88)Y0.41forY≤1.4×107,F1=1+0.0052(-xcrit0.88)(1.4×107)0.41forY>1.4×107.
Finally, F2 is given by
(35)F2=F1-0.42forF1≤4,F2=0.55forF1>4.


### 3.1.3. Choice between UCC and LCC Correlation

For water, the UCC correlation is used whenY≤106. When Y>106, the correlation giving the lower value of the boiling number Bo is used, with exception of cases where zeff>160/Pr1.14, for which the UCC formulation is always adopted. In this analysis, the UCC correlation was used in all calculations.


### 3.1.4. Range Covered by the Shah Correlation

The Shah correlation was tested against 62 experimental databases with 23 different fluids, covering the following operating conditions:(i)
0.315×10-3<D<37.5×10-3 m,(ii)
1.3<z/D<940,(iii)
4<G<29051 kg/m2/s,(iv)
-4<xi<0.85,(v)
-2.6<xcrit<1.Only 15 tests over the whole database are not included in the range covered by the Shah correlation. In Table2 the values of experimental quantities relevant for the Shah model are reported.Table 2
Range of parameters for the Shah model covered by the NUPEC tests.
D [m]
z/D
G (max/min)
x
i (max/min)
x
crit (max/min)
Series 0
0.009711
376.67
4944.4/1408.3
−0.062/−0.96
0.49/−0.20
Series 2
0.009711
376.67
4769.4/316.7
−0.053/−0.97
1.00/−0.06
Series 3
0.009989
366.21
4702.8/1361.1
−0.045/−0.87
0.58/−0.05
Series 4
0.009711
376.67
4725.0/566.7
−0.058/−0.98
1.00/0.06
Series 13
0.009711
376.67
3861.1/1361.1
−0.057/−0.50
0.50/0.20
Series 8
0.008867
412.55
4816.7/575.0
−0.058/−0.97
1.00/0.11


## 3.1.1. The UCC Correlation

The UCC correlation is(23)Bo=0.124(Dzeff)0.89(104Y)n(1-xi,eff),
with
(24)Y=[GDCpfλf][G2ρf2gD]0.4[μfμg]0.6.
In the previous equations, zeff is the effective tube length and xi,eff is the effective inlet quality, defined as
(25)xi,eff=xi,zeff=zcrit,forxi<0,xi,eff=0,zeff=zsat,forxi>0,
where zcrit is the distance from the inlet section and the location of the boiling crisis, where the critical heat flux is calculated, and zsat is the boiling length, which for uniformly heated tubes is given by
(26)zsatD=zcritD+xi4Bo.
For water flows, when Y≤104,n=0, otherwise it is given by
(27)n=(Dzeff)0.54forY≤106,n=0.12(1-Xi,eff)0.5forY>106.


## 3.1.2. The LCC Correlation

The LCC correlation is expressed by(28)Bo=FEFXBo0.
The entrance factor FE is given by
(29)FE=1.54-0.032(zcritD).
When the previous correlation gives FE<1, it is used FE=1.B
o
0 is defined as the boiling number at xcrit=0, given by the maximum value obtained by the following equations
(30)Bo0=15Y-0.612,Bo0=0.082Y-0.3(1+1.45Pr4.03),Bo0=0.0024Y-0.105(1+1.15Pr3.39),
where Pr is the reduced pressure given by Pr=P/Pc where Pc is the critical pressure, that is 22.064 MPa for water. The value of FX depends on the quality at the location of the boiling crisis xcrit. When xcrit>0, the following equation is used
(31)FX=F3[1+(F3-0.29-1)(Pr-0.6)0.35]c.
When Pr>0.6,c=1, otherwise c=0. F3 is instead given by
(32)F3=(1.25×105Y)0.833xcrit.
When xcrit<0, FX is given by
(33)FX=F1[1-(1-F2)(Pr-0.6)0.35]b.
As in the previous case, when Pr>0.6,b=1, otherwise b=0. F1 is given by
(34)F1=1+0.0052(-xcrit0.88)Y0.41forY≤1.4×107,F1=1+0.0052(-xcrit0.88)(1.4×107)0.41forY>1.4×107.
Finally, F2 is given by
(35)F2=F1-0.42forF1≤4,F2=0.55forF1>4.


## 3.1.3. Choice between UCC and LCC Correlation

For water, the UCC correlation is used whenY≤106. When Y>106, the correlation giving the lower value of the boiling number Bo is used, with exception of cases where zeff>160/Pr1.14, for which the UCC formulation is always adopted. In this analysis, the UCC correlation was used in all calculations.


## 3.1.4. Range Covered by the Shah Correlation

The Shah correlation was tested against 62 experimental databases with 23 different fluids, covering the following operating conditions:(i)
0.315×10-3<D<37.5×10-3 m,(ii)
1.3<z/D<940,(iii)
4<G<29051 kg/m2/s,(iv)
-4<xi<0.85,(v)
-2.6<xcrit<1.Only 15 tests over the whole database are not included in the range covered by the Shah correlation. In Table2 the values of experimental quantities relevant for the Shah model are reported.Table 2
Range of parameters for the Shah model covered by the NUPEC tests.
D [m]
z/D
G (max/min)
x
i (max/min)
x
crit (max/min)
Series 0
0.009711
376.67
4944.4/1408.3
−0.062/−0.96
0.49/−0.20
Series 2
0.009711
376.67
4769.4/316.7
−0.053/−0.97
1.00/−0.06
Series 3
0.009989
366.21
4702.8/1361.1
−0.045/−0.87
0.58/−0.05
Series 4
0.009711
376.67
4725.0/566.7
−0.058/−0.98
1.00/0.06
Series 13
0.009711
376.67
3861.1/1361.1
−0.057/−0.50
0.50/0.20
Series 8
0.008867
412.55
4816.7/575.0
−0.058/−0.97
1.00/0.11


## 3.2. The Katto and Ohno Model

The correlation of Katto and Ohno [11] provides the value of the critical heat flux as
(36)qchf′′=XG(hlv+KΔhsub,i),
where Δhsub,i is the subcooling inlet enthalpy. The terms X and K are functions of three-dimensionless terms:
(37)Z′=zD,R′=ρgρf,W′=σρf(G2z).
Five different values of X must be determined
(38)X1=CW'0.043Z',X2=0.1R'0.133W'0.3331+0.0031Z',X3=0.098R'0.133W'0.433Z'0.271+0.0031Z',X4=0.0384R'0.6W'0.1731+0.28W'0.233Z',X5=0.234R'0.513W'0.433Z'0.271+0.0031Z'.
The value of C in the relationship of X1 is given by
(39)C=0.25forZ′<50,C=0.25+0.0009(Z′-50)for50<Z′<150,C=0.34forZ′>150.
Three values of K must be determined
(40)K1=0.261CW'0.043,(41)K2=0.833[0.0124+(1/Z')]R'0.133W'0.333,(42)K3=1.12[1.52W'0.233+(1/Z')]R'0.6W'0.173.
The appropriate values of X and K must be determined according to Table 3.Table 3
Choice ofX and K for the Katto and Ohno model.
R
'
<
0.15
R
'
>
0.15
X
1
<
X
2
X
=
X
1
X
1
<
X
5
X
=
X
1
X
1
>
X
2
X
2
<
X
3
}
X
=
X
2
X
1
>
X
5
X
5
>
X
4
}
X
=
X
5
X
1
>
X
2
X
2
>
X
3
}
X
=
X
3
X
1
>
X
5
X
5
<
X
4
}
X
=
X
4
K
1
>
K
2
K
=
K
1
K
1
>
K
2
K
=
K
1
K
1
<
K
2
K
=
K
2
K
1
<
K
2
K
2
<
K
3
}
K
=
K
2
K
1
<
K
2
K
2
>
K
3
}
K
=
K
3


### 3.2.1. Range Covered by the Katto and Ohno Correlation

The Katto and Ohno correlation covers the following operating conditions:(i)
0.01<z<8.8 m,(ii)
0.001<D<0.038 m,(iii)
5<Z′<880,(iv)
0.0003<R′<0.41,(v)
3×10-9<W′<2×10-2.All experimental tests are included in the range covered by the Katto and Ohno correlation (see Table4).Table 4
Range of parameters for the Katto and Ohno model covered by the NUPEC tests.
Z [m]
D [m]
Z
′
R
′ (max/min)
W
′ (max/min)
Series 0
3.658
0.009711
376.67
0.159185/0.070185
1.28 × 10−6/3.97 × 10−8
Series 2
3.658
0.009711
376.67
0.158337/0.030672
5.04 × 10−5/4.13 × 10−8
Series 3
3.658
0.009989
366.21
0.156657/0.070549
1.33 × 10−6/4.28 × 10−8
Series 4
3.658
0.009711
376.67
0.156156/0.031256
1.35 × 10−5/4.17 × 10−8
Series 13
3.658
0.009711
376.67
0.156156/0.096048
6.76 × 10−7/8.28 × 10−8
Series 8
3.658
0.008867
412.55
0.156323/0.031191
1.48 × 10−5/3.99 × 10−8


## 3.2.1. Range Covered by the Katto and Ohno Correlation

The Katto and Ohno correlation covers the following operating conditions:(i)
0.01<z<8.8 m,(ii)
0.001<D<0.038 m,(iii)
5<Z′<880,(iv)
0.0003<R′<0.41,(v)
3×10-9<W′<2×10-2.All experimental tests are included in the range covered by the Katto and Ohno correlation (see Table4).Table 4
Range of parameters for the Katto and Ohno model covered by the NUPEC tests.
Z [m]
D [m]
Z
′
R
′ (max/min)
W
′ (max/min)
Series 0
3.658
0.009711
376.67
0.159185/0.070185
1.28 × 10−6/3.97 × 10−8
Series 2
3.658
0.009711
376.67
0.158337/0.030672
5.04 × 10−5/4.13 × 10−8
Series 3
3.658
0.009989
366.21
0.156657/0.070549
1.33 × 10−6/4.28 × 10−8
Series 4
3.658
0.009711
376.67
0.156156/0.031256
1.35 × 10−5/4.17 × 10−8
Series 13
3.658
0.009711
376.67
0.156156/0.096048
6.76 × 10−7/8.28 × 10−8
Series 8
3.658
0.008867
412.55
0.156323/0.031191
1.48 × 10−5/3.99 × 10−8


## 4. Void Distribution Results

### 4.1. Subchannel Exercises

Four series of measurements of void fraction were performed in sections representative of subchannel types in a PWR assembly. Table5 gives the geometry (center, typical, and thimble subchannels, side and corner subchannels) and power shape for these series. The heated length is 1555 mm, and the void measurement section is located at 1400 mm from the bottom of the heated section.Table 5
Geometry and power shape of rod bundle test assembly (from [1]).
Item
Data
Assembly (subjected subchannel)
Subchannel type
Center (typical)
Center (thimble)
Side
Corner
Number of heaters
4
×
1
/
4
3
×
1
/
4
2
×
1
/
4
1
×
1
/
4
Axial-heated length (mm)
1555
1555
1555
1555
Axial power shape
Uniform
Uniform
Uniform
Uniform
Number of runs
43
43
20
20According to the given test matrix (power value and boundary conditions), the flow is saturated at the location where the void fraction is measured for the most runs. This situation allows only partial assessment of the subcooled boiling models. In contrast, drift flux model plays a major role to obtain good agreement with experimental data. Chexal-Lellouche and Ishii correlations have been compared for series 1 (Figure1). It is shown that the Ishii correlation tends to underpredict the void fraction more than the Chexal-Lellouche one. Even if it is not obvious to extend this conclusion to other configurations, the Chexal-Lellouche correlation has been thus adopted for other subchannel and bundle calculations.Figure 1
Comparison of void fractions predicted by the Chexal-Lellouche and the Ishii drift correlations against experimental data (subchannel S1 series).Calculated densities and void fractions are compared against the experimental data in Figure2. Experimental densities measured by CT scan are declared to be affected by an uncertainty of 15 kg/m3 (σexp=15 kg/m3 in Figure 2(b)) [12]. Experimental void fraction resumed basing on measured densities are presumed to be affected by an uncertainty of 3% of void fraction (σexp=3% in Figure 2(a)) [12]. It happens that densities obtained by the code match well the experimental ones, whereas void fractions are slightly underestimated for the lowest value of this quantity. Indeed, physical properties and correlations adopted to convert density to void fraction could be the cause for this discrepancy.Calculated void fractions (a) and densities (b) versus experimental data for subchannel series 1 to 4 with the Chexal-Lellouche drift correlation.
(a)
(b)


### 4.2. Subchannel Exercises

A partial section of the full length17×17 type PWR fuel assemblies was considered. The rod bundle test is a 5×5 square array. The heated section is 3658 mm high, and density measurements are set at 2216 mm (Lower), 2669 mm (Middle), and 3177 mm (Upper). In Table 6 are shown the geometry and power shape of the rod bundle test assemblies considered. Three assembly configurations were considered: B5, B6, and B7. The main difference between these three configurations is in the power distribution. Assembly B5 has a uniform axial power distribution and pattern A radial power distribution. Assembly B6 has the same radial power distribution of assembly B5 but cosine axial power distribution. Assembly B7 has a cosine axial power distribution and pattern B radial power distribution. For this radial power distribution, the central rod is a thimble rod (i.e., no power is generated inside this rod) of larger diameter with respect to the fuel rods. The gamma-ray transmission method (chordal averaged) was adopted in the tests performed to measure the density and then converted to the void fraction of the gas-liquid two-phase flow. The declared uncertainties are 4% of void fraction (σexp=4% in Figures 3 and 4) for steady-state bundle tests and 5% of void fraction (σexp=5% in Figures 5 and 6) for transient bundle tests. In Table 7 are shown the test series for void fraction measurements.Table 6
Geometry and power shape of rod bundle test assembly.
Item
Data
Assembly
Rods array
5
×
5
5
×
5
5
×
5
Number of heated rods
25
25
24
Number of thimble rods
0
0
1
Heated rod outer diameter (mm)
9.50
9.50
9.50
Thimble rod outer diameter (mm)
—
—
12.24
Heated rod pitch (mm)
12.60
12.60
12.60
Axial-heated length (mm)
3658
3658
3658
Flow channel inner width (mm)
64.9
64.9
64.9
Radial power shape
Axial power shape
Uniform
Cosine
Cosine
Number of mixing vane spacers
7
7
7
Number of no mixing vane spacers
2
2
2
Number of simple spacers
8
8
8
Mixing vane spacer location (mm) (Loss coefficient 1.0 [1])
471, 925, 1378, 1832, 2285, 2739, 3247 from the beginning of the test section
No mixing vane spacer location (mm) (Loss coefficient 0.7 [1])
2.5, 3755 from the beginning of the test section
Simple spacer location (mm) (Loss coefficient 0.4 [1])
237, 698, 1151, 1605, 2059, 2512, 2993, 3501 from the beginning of the heated sectionTable 7
Test series for void fraction measurements.
Test series
Assembly
Test mode
Steady-state
Transient
5
B5
74 runs
4 runs
5T
6
B6
74 runs
4 runs
6T
7
B7
74 runs
4 runs
7T
8
B5
31 runsPSBT run 5.2442. Sensitivity analysis forKv0 (a), kts and mts (b) on the void fraction profile in the central subchannel.
(a)
(b)Steady-state rod bundle exercises. Comparison of calculated void fraction profiles in the central subchannel against experimental data: lower (a), medium (b), and upper (c) elevations.
(a)
(b)
(c)Transient T5: comparison between calculated and measured void fractions.
(a)
(b)
(c)
(d)Temperature increase transient T6: original (a) and delayed (b) inlet temperature boundary conditions.
(a)
(b)


#### 4.2.1. Steady-State Exercises

For the results at the lower and middle elevations, subcooled nucleate boiling models (condensation and wall heat transfer) play a major role for the prediction of void fraction. At the upper elevation, the fluid is generally saturated, and the drift model becomes important. Moreover, diffusion terms play also a major role, and turbulent diffusion promoted by the presence of mixing grid spacers must be taken into account. Standard parametersKt0ij(z)=ktb and Mt0ij(z)=mtb (the turbulent Prandtl number is assumed equal to 1) adopted for bare bundles (without any spacer) have to be increased in the region upstream mixing grid spacers in order to reproduce the enhancement of turbulent mixing. In (15) and (13), Kt0ij and Mt0ij have been therefore adapted for the PSBT assemblies by means of piecewise functions: it was assumed that Kt0ij(z)=kts and Mt0ij(z)=mts downstream a mixing grid spacer, instead of taking the standard values ktb and mtb. Despite the values of ktb and mtb are reliably assessed to be around 0.010 for PWR type bundles [6], the appropriate values to be adopted for kts and mts are not known for these particular mixing grid spacers and thus, to better identify reasonable values for these coefficients, a sensitivity analysis has been performed. A sensitivity analysis for the coefficient Kv0 in the condensation model was also conducted. A sample result is shown in Figure 3, where combined effects of these parameters are reported for run 5.2442. In the subcooled and at the beginning of the saturated region, void fraction is strongly reduced as Kv0 increases, but this parameter does not affect results at the end of the bundle, where the flow is fully saturated. On the other hand, the effect of the turbulent diffusion coefficients kts and mts is significant when the void fraction increases, since it determines the flatness of the void distribution profile in the bundle. Detailed experimental density maps would have been useful to assess a reliable value for the turbulent diffusion coefficients, but these maps are not readily exploitable. As far as we could deduce basing on the void fraction profile in the central subchannel, a value for kts and mts was chosen equal to 0.045. The value of Kv0 was instead taken equal to 1.5×10-4, which is in the standard range of values adopted in thermal-hydraulic analysis performed with this model. Figure 4 shows the calculated void fraction against the experimental values for series 5, 6, and 7, with the following parameters: Kv0=1.5×10-4,kts=mts=0.045,ktb=mtb=0.01.


#### 4.2.2. Transient Exercises

For the transient simulations, three different configurations were taken into account as shown in Table7. Test series 5T considers the same assembly conditions used for steady-state series 5, with a uniform axial power distribution, and pattern A of radial power distribution.For transient test series 6T the same assembly conditions used for steady-state series 6 were applied, which means a cosine axial power distribution, and pattern A radial power distribution. Test series 7T considers the same assembly conditions used for steady-state test series 7, which are cosine axial power distribution, and pattern B radial power distribution.For each transient analysis, four different scenarios were considered: power increase, flow reduction, depressurization, and temperature increase. Boundary conditions were provided for each scenario, using table where the dependent variables (i.e., power, pressure, mass flux, and inlet temperature resp.,) were specified as function of the simulation time. Same parameters and models as for steady-state bundle computations were used.Figure5 shows complete results for transients 5T, also representative of the other transient series 6T and 7T. FLICA-OVAP presents an overall agreement against the experimental void fraction for the transients, although discrepancies with experimental data can be observed, in particular for the temperature increase transient. For the power increase transient, the evolution of the void fraction follows the data, but the void fraction is under-estimated at the middle and upper locations. The results concerning the depressurization have more discrepancy as time increases, but are consistent with the experimental evolution.For the temperature increase transient, a shift of calculated void fractions profiles with respect to experimental values can be noticed. This discrepancy has been noticed by several participants to the first PSBT/OECD workshop in Pisa. Fluid temperature probe is located in a pipe between the preheater and the inlet nozzle of the test section [12]. It is therefore reasonable to guess that a delay of several seconds occurs between the measurement point and the inlet of the heated section. This point has been investigated by JNES [12] but the distance from the measurement location to the inlet of the heated section (where the temperature boundary condition has to be applied in thermal-hydraulics codes) was not clarified. As far as we can say basing on the result obtained by FLICA-OVAP, if a delay of 6 s is assumed for the inlet temperature with respect to other boundary conditions (i.e., the initial temperature is maintained during 6 s and then the temperature variation is applied), the agreement between calculated and experimental void fraction profiles is improved. It can clearly be seen in Figure 6, where these profiles are compared for the calculations with and without the time delay of 6 seconds.


## 4.1. Subchannel Exercises

Four series of measurements of void fraction were performed in sections representative of subchannel types in a PWR assembly. Table5 gives the geometry (center, typical, and thimble subchannels, side and corner subchannels) and power shape for these series. The heated length is 1555 mm, and the void measurement section is located at 1400 mm from the bottom of the heated section.Table 5
Geometry and power shape of rod bundle test assembly (from [1]).
Item
Data
Assembly (subjected subchannel)
Subchannel type
Center (typical)
Center (thimble)
Side
Corner
Number of heaters
4
×
1
/
4
3
×
1
/
4
2
×
1
/
4
1
×
1
/
4
Axial-heated length (mm)
1555
1555
1555
1555
Axial power shape
Uniform
Uniform
Uniform
Uniform
Number of runs
43
43
20
20According to the given test matrix (power value and boundary conditions), the flow is saturated at the location where the void fraction is measured for the most runs. This situation allows only partial assessment of the subcooled boiling models. In contrast, drift flux model plays a major role to obtain good agreement with experimental data. Chexal-Lellouche and Ishii correlations have been compared for series 1 (Figure1). It is shown that the Ishii correlation tends to underpredict the void fraction more than the Chexal-Lellouche one. Even if it is not obvious to extend this conclusion to other configurations, the Chexal-Lellouche correlation has been thus adopted for other subchannel and bundle calculations.Figure 1
Comparison of void fractions predicted by the Chexal-Lellouche and the Ishii drift correlations against experimental data (subchannel S1 series).Calculated densities and void fractions are compared against the experimental data in Figure2. Experimental densities measured by CT scan are declared to be affected by an uncertainty of 15 kg/m3 (σexp=15 kg/m3 in Figure 2(b)) [12]. Experimental void fraction resumed basing on measured densities are presumed to be affected by an uncertainty of 3% of void fraction (σexp=3% in Figure 2(a)) [12]. It happens that densities obtained by the code match well the experimental ones, whereas void fractions are slightly underestimated for the lowest value of this quantity. Indeed, physical properties and correlations adopted to convert density to void fraction could be the cause for this discrepancy.Calculated void fractions (a) and densities (b) versus experimental data for subchannel series 1 to 4 with the Chexal-Lellouche drift correlation.
(a)
(b)


## 4.2. Subchannel Exercises

A partial section of the full length17×17 type PWR fuel assemblies was considered. The rod bundle test is a 5×5 square array. The heated section is 3658 mm high, and density measurements are set at 2216 mm (Lower), 2669 mm (Middle), and 3177 mm (Upper). In Table 6 are shown the geometry and power shape of the rod bundle test assemblies considered. Three assembly configurations were considered: B5, B6, and B7. The main difference between these three configurations is in the power distribution. Assembly B5 has a uniform axial power distribution and pattern A radial power distribution. Assembly B6 has the same radial power distribution of assembly B5 but cosine axial power distribution. Assembly B7 has a cosine axial power distribution and pattern B radial power distribution. For this radial power distribution, the central rod is a thimble rod (i.e., no power is generated inside this rod) of larger diameter with respect to the fuel rods. The gamma-ray transmission method (chordal averaged) was adopted in the tests performed to measure the density and then converted to the void fraction of the gas-liquid two-phase flow. The declared uncertainties are 4% of void fraction (σexp=4% in Figures 3 and 4) for steady-state bundle tests and 5% of void fraction (σexp=5% in Figures 5 and 6) for transient bundle tests. In Table 7 are shown the test series for void fraction measurements.Table 6
Geometry and power shape of rod bundle test assembly.
Item
Data
Assembly
Rods array
5
×
5
5
×
5
5
×
5
Number of heated rods
25
25
24
Number of thimble rods
0
0
1
Heated rod outer diameter (mm)
9.50
9.50
9.50
Thimble rod outer diameter (mm)
—
—
12.24
Heated rod pitch (mm)
12.60
12.60
12.60
Axial-heated length (mm)
3658
3658
3658
Flow channel inner width (mm)
64.9
64.9
64.9
Radial power shape
Axial power shape
Uniform
Cosine
Cosine
Number of mixing vane spacers
7
7
7
Number of no mixing vane spacers
2
2
2
Number of simple spacers
8
8
8
Mixing vane spacer location (mm) (Loss coefficient 1.0 [1])
471, 925, 1378, 1832, 2285, 2739, 3247 from the beginning of the test section
No mixing vane spacer location (mm) (Loss coefficient 0.7 [1])
2.5, 3755 from the beginning of the test section
Simple spacer location (mm) (Loss coefficient 0.4 [1])
237, 698, 1151, 1605, 2059, 2512, 2993, 3501 from the beginning of the heated sectionTable 7
Test series for void fraction measurements.
Test series
Assembly
Test mode
Steady-state
Transient
5
B5
74 runs
4 runs
5T
6
B6
74 runs
4 runs
6T
7
B7
74 runs
4 runs
7T
8
B5
31 runsPSBT run 5.2442. Sensitivity analysis forKv0 (a), kts and mts (b) on the void fraction profile in the central subchannel.
(a)
(b)Steady-state rod bundle exercises. Comparison of calculated void fraction profiles in the central subchannel against experimental data: lower (a), medium (b), and upper (c) elevations.
(a)
(b)
(c)Transient T5: comparison between calculated and measured void fractions.
(a)
(b)
(c)
(d)Temperature increase transient T6: original (a) and delayed (b) inlet temperature boundary conditions.
(a)
(b)


### 4.2.1. Steady-State Exercises

For the results at the lower and middle elevations, subcooled nucleate boiling models (condensation and wall heat transfer) play a major role for the prediction of void fraction. At the upper elevation, the fluid is generally saturated, and the drift model becomes important. Moreover, diffusion terms play also a major role, and turbulent diffusion promoted by the presence of mixing grid spacers must be taken into account. Standard parametersKt0ij(z)=ktb and Mt0ij(z)=mtb (the turbulent Prandtl number is assumed equal to 1) adopted for bare bundles (without any spacer) have to be increased in the region upstream mixing grid spacers in order to reproduce the enhancement of turbulent mixing. In (15) and (13), Kt0ij and Mt0ij have been therefore adapted for the PSBT assemblies by means of piecewise functions: it was assumed that Kt0ij(z)=kts and Mt0ij(z)=mts downstream a mixing grid spacer, instead of taking the standard values ktb and mtb. Despite the values of ktb and mtb are reliably assessed to be around 0.010 for PWR type bundles [6], the appropriate values to be adopted for kts and mts are not known for these particular mixing grid spacers and thus, to better identify reasonable values for these coefficients, a sensitivity analysis has been performed. A sensitivity analysis for the coefficient Kv0 in the condensation model was also conducted. A sample result is shown in Figure 3, where combined effects of these parameters are reported for run 5.2442. In the subcooled and at the beginning of the saturated region, void fraction is strongly reduced as Kv0 increases, but this parameter does not affect results at the end of the bundle, where the flow is fully saturated. On the other hand, the effect of the turbulent diffusion coefficients kts and mts is significant when the void fraction increases, since it determines the flatness of the void distribution profile in the bundle. Detailed experimental density maps would have been useful to assess a reliable value for the turbulent diffusion coefficients, but these maps are not readily exploitable. As far as we could deduce basing on the void fraction profile in the central subchannel, a value for kts and mts was chosen equal to 0.045. The value of Kv0 was instead taken equal to 1.5×10-4, which is in the standard range of values adopted in thermal-hydraulic analysis performed with this model. Figure 4 shows the calculated void fraction against the experimental values for series 5, 6, and 7, with the following parameters: Kv0=1.5×10-4,kts=mts=0.045,ktb=mtb=0.01.


### 4.2.2. Transient Exercises

For the transient simulations, three different configurations were taken into account as shown in Table7. Test series 5T considers the same assembly conditions used for steady-state series 5, with a uniform axial power distribution, and pattern A of radial power distribution.For transient test series 6T the same assembly conditions used for steady-state series 6 were applied, which means a cosine axial power distribution, and pattern A radial power distribution. Test series 7T considers the same assembly conditions used for steady-state test series 7, which are cosine axial power distribution, and pattern B radial power distribution.For each transient analysis, four different scenarios were considered: power increase, flow reduction, depressurization, and temperature increase. Boundary conditions were provided for each scenario, using table where the dependent variables (i.e., power, pressure, mass flux, and inlet temperature resp.,) were specified as function of the simulation time. Same parameters and models as for steady-state bundle computations were used.Figure5 shows complete results for transients 5T, also representative of the other transient series 6T and 7T. FLICA-OVAP presents an overall agreement against the experimental void fraction for the transients, although discrepancies with experimental data can be observed, in particular for the temperature increase transient. For the power increase transient, the evolution of the void fraction follows the data, but the void fraction is under-estimated at the middle and upper locations. The results concerning the depressurization have more discrepancy as time increases, but are consistent with the experimental evolution.For the temperature increase transient, a shift of calculated void fractions profiles with respect to experimental values can be noticed. This discrepancy has been noticed by several participants to the first PSBT/OECD workshop in Pisa. Fluid temperature probe is located in a pipe between the preheater and the inlet nozzle of the test section [12]. It is therefore reasonable to guess that a delay of several seconds occurs between the measurement point and the inlet of the heated section. This point has been investigated by JNES [12] but the distance from the measurement location to the inlet of the heated section (where the temperature boundary condition has to be applied in thermal-hydraulics codes) was not clarified. As far as we can say basing on the result obtained by FLICA-OVAP, if a delay of 6 s is assumed for the inlet temperature with respect to other boundary conditions (i.e., the initial temperature is maintained during 6 s and then the temperature variation is applied), the agreement between calculated and experimental void fraction profiles is improved. It can clearly be seen in Figure 6, where these profiles are compared for the calculations with and without the time delay of 6 seconds.


## 4.2.1. Steady-State Exercises

For the results at the lower and middle elevations, subcooled nucleate boiling models (condensation and wall heat transfer) play a major role for the prediction of void fraction. At the upper elevation, the fluid is generally saturated, and the drift model becomes important. Moreover, diffusion terms play also a major role, and turbulent diffusion promoted by the presence of mixing grid spacers must be taken into account. Standard parametersKt0ij(z)=ktb and Mt0ij(z)=mtb (the turbulent Prandtl number is assumed equal to 1) adopted for bare bundles (without any spacer) have to be increased in the region upstream mixing grid spacers in order to reproduce the enhancement of turbulent mixing. In (15) and (13), Kt0ij and Mt0ij have been therefore adapted for the PSBT assemblies by means of piecewise functions: it was assumed that Kt0ij(z)=kts and Mt0ij(z)=mts downstream a mixing grid spacer, instead of taking the standard values ktb and mtb. Despite the values of ktb and mtb are reliably assessed to be around 0.010 for PWR type bundles [6], the appropriate values to be adopted for kts and mts are not known for these particular mixing grid spacers and thus, to better identify reasonable values for these coefficients, a sensitivity analysis has been performed. A sensitivity analysis for the coefficient Kv0 in the condensation model was also conducted. A sample result is shown in Figure 3, where combined effects of these parameters are reported for run 5.2442. In the subcooled and at the beginning of the saturated region, void fraction is strongly reduced as Kv0 increases, but this parameter does not affect results at the end of the bundle, where the flow is fully saturated. On the other hand, the effect of the turbulent diffusion coefficients kts and mts is significant when the void fraction increases, since it determines the flatness of the void distribution profile in the bundle. Detailed experimental density maps would have been useful to assess a reliable value for the turbulent diffusion coefficients, but these maps are not readily exploitable. As far as we could deduce basing on the void fraction profile in the central subchannel, a value for kts and mts was chosen equal to 0.045. The value of Kv0 was instead taken equal to 1.5×10-4, which is in the standard range of values adopted in thermal-hydraulic analysis performed with this model. Figure 4 shows the calculated void fraction against the experimental values for series 5, 6, and 7, with the following parameters: Kv0=1.5×10-4,kts=mts=0.045,ktb=mtb=0.01.


## 4.2.2. Transient Exercises

For the transient simulations, three different configurations were taken into account as shown in Table7. Test series 5T considers the same assembly conditions used for steady-state series 5, with a uniform axial power distribution, and pattern A of radial power distribution.For transient test series 6T the same assembly conditions used for steady-state series 6 were applied, which means a cosine axial power distribution, and pattern A radial power distribution. Test series 7T considers the same assembly conditions used for steady-state test series 7, which are cosine axial power distribution, and pattern B radial power distribution.For each transient analysis, four different scenarios were considered: power increase, flow reduction, depressurization, and temperature increase. Boundary conditions were provided for each scenario, using table where the dependent variables (i.e., power, pressure, mass flux, and inlet temperature resp.,) were specified as function of the simulation time. Same parameters and models as for steady-state bundle computations were used.Figure5 shows complete results for transients 5T, also representative of the other transient series 6T and 7T. FLICA-OVAP presents an overall agreement against the experimental void fraction for the transients, although discrepancies with experimental data can be observed, in particular for the temperature increase transient. For the power increase transient, the evolution of the void fraction follows the data, but the void fraction is under-estimated at the middle and upper locations. The results concerning the depressurization have more discrepancy as time increases, but are consistent with the experimental evolution.For the temperature increase transient, a shift of calculated void fractions profiles with respect to experimental values can be noticed. This discrepancy has been noticed by several participants to the first PSBT/OECD workshop in Pisa. Fluid temperature probe is located in a pipe between the preheater and the inlet nozzle of the test section [12]. It is therefore reasonable to guess that a delay of several seconds occurs between the measurement point and the inlet of the heated section. This point has been investigated by JNES [12] but the distance from the measurement location to the inlet of the heated section (where the temperature boundary condition has to be applied in thermal-hydraulics codes) was not clarified. As far as we can say basing on the result obtained by FLICA-OVAP, if a delay of 6 s is assumed for the inlet temperature with respect to other boundary conditions (i.e., the initial temperature is maintained during 6 s and then the temperature variation is applied), the agreement between calculated and experimental void fraction profiles is improved. It can clearly be seen in Figure 6, where these profiles are compared for the calculations with and without the time delay of 6 seconds.


## 5. DNB Results

The two models adopted in this work, the Shah and the Katto and Ohno models, have been developed and tested mostly in single-channel uniform heat flux conditions.In this work, the applicability of them to bundle geometries with nonuniform heat flux profile has been investigated. Each experimental series of the NUPEC database has been calculated by the two models, adopting a twofold approach.In a first step, homogenized one-dimensional calculations have been performed, adopting a bundle-averaged description.In a second step, three-dimensional calculations have been performed, adopting a subchannel description. In this case, the two boiling crisis models are applied at the sub-channels scale. The fundamental difference with the first approach consists in having different hydraulic diameters depending on whether the selected subchannel is a central, a side or a corner subchannel. However, some special approach has to be taken for side and corner subchannels, since CHF models tend to underestimate their critical heat flux. Moreover, as observed by Tong and Tang [13, Section 5.4.5.2, Figure 5.54], for a given inlet enthalpy, critical heat fluxes in the presence of cold walls are even higher than for internal subchannels. For the sake of simplicity, the possibility to have boiling crisis in side and corner subchannels was thus excluded.In the following paragraphs, for each series, results obtained via the bundle-averaged and the subchannel approach will be shown for the two models. The performances of the different models are also summarized in Table8.Table 8
Average absolute errors in steady-state DNB tests (%).
1D Shah
1D Katto and Ohno
3D Shah
3D Katto and Ohno
Series 0
15.5
10.9
13.7
5.6
Series 2
13.5
16.0
12.3
18.3
Series 3
8.5
10.9
10.0
15.0
Series 4
14.8
14.6
13.7
19.1
Series 8
11.5
15.6
14.3
12.9
Series 13
4.8
16.4
4.6
19.6


### 5.1. Steady-State Series

#### 5.1.1. Series 0, Series 2, and Series 3

Series 0, Series 2 investigate boiling crisis in rod bundle (rods array:5×5) and uniform heat flux. The two series differ only for the position of mixing and spacer grids. In Series 3, the bundle is also modified, adopting an array of 36 rods (6×6). The axial power shape is uniform for all series, but peripheral rods have a slightly lower power with respect to central rods: the radial power distribution factor is 0.85 for peripheral rods and 1.0 for central rods.In Figures7, 8, and 9, calculated and experimental critical heat fluxes are compared, respectively, for Series 1, Series 2, and Series 3. It is ascertained that the Shah model tends to predict higher critical heat flux values than the Katto and Ohno model, for both the bundle-averaged and the subchannel approach. Moreover, in this particular configuration with uniform heat flux and a moderate radial offset, 1D or 3D calculations give very similar results.Computed versus experimental critical heat fluxes (Series 0).
(a)
(b)
(c)
(d)Computed versus experimental critical heat fluxes (Series 2).
(a)
(b)
(c)
(d)Computed versus experimental critical heat fluxes (Series 3).
(a)
(b)
(c)
(d)


#### 5.1.2. Series 4 and Series 13

Series 4 and Series 13 introduce the effect of nonuniform axial profile. A cosine shape was adopted on the same bundle geometry used for Series 2. To deal with nonuniform heat flux, a correction factor was adopted, as proposed by Tong and Tang [13]. In Figures 10 and 11 calculated and experimental critical heat fluxes are compared, respectively, for Series 4, Series 13. As for previous tests, the Shah model predicts higher critical heat flux values than the Katto and Ohno model, providing a better agreement with experimental values. Minor differences are experienced between the homogenized and the subchannel description.Computed versus experimental critical heat fluxes (Series 4).
(a)
(b)
(c)
(d)Computed versus experimental critical heat fluxes (Series 13).
(a)
(b)
(c)
(d)


#### 5.1.3. Series 8

Series 8 includes the presence of a central thimble rod, representing guide tube for control rods. Contrarily to the previous series, the results of the homogenized and the subchannel approaches are different (see Figure12). As expected, in the presence of a radial heterogeneous power shape, a better description is achieved with the subchannel approach. In general the Shah model gives a better estimate of critical heat fluxes.Computed versus experimental critical heat fluxes (Series 8).
(a)
(b)
(c)
(d)


### 5.2. Transient Series

Two experimental campaigns have been consecrated to detect boiling crisis in transient conditions. Different transient conditions have been investigated by NUPEC, including power increase, inlet temperature decrease, flow reduction, and depressurization. Two series of data have been proposed, Series 11 and Series 12, involving different bundle configurations. Series 11 is based on the bundle configuration adopted for Series 4 (cosine axial power shape, rods array5×5), whereas Series 12 involves a central thimble rod. In the following tables, results obtained by the Shah model with the subchannel approach are listed. Boiling crisis is relatively well predicted for Series 11, whereas a larger discrepancy is ascertained for Series 12 (see Table 9).Table 9
Comparison between calculated and experimental boiling crisis detection time.
Boiling crisis
Series 11
Series 12
detection time (s)
EXP
CALC
EXP
CALC
Power increase
106.7
108.7
86.6
72.2
Flow reduction
52.9
48.8
55.0
42.9
Depressurization
88.8
90.8
143.8
140.9
Temperature decrease
140.6
143.3
128.8
121.4


## 5.1. Steady-State Series

### 5.1.1. Series 0, Series 2, and Series 3

Series 0, Series 2 investigate boiling crisis in rod bundle (rods array:5×5) and uniform heat flux. The two series differ only for the position of mixing and spacer grids. In Series 3, the bundle is also modified, adopting an array of 36 rods (6×6). The axial power shape is uniform for all series, but peripheral rods have a slightly lower power with respect to central rods: the radial power distribution factor is 0.85 for peripheral rods and 1.0 for central rods.In Figures7, 8, and 9, calculated and experimental critical heat fluxes are compared, respectively, for Series 1, Series 2, and Series 3. It is ascertained that the Shah model tends to predict higher critical heat flux values than the Katto and Ohno model, for both the bundle-averaged and the subchannel approach. Moreover, in this particular configuration with uniform heat flux and a moderate radial offset, 1D or 3D calculations give very similar results.Computed versus experimental critical heat fluxes (Series 0).
(a)
(b)
(c)
(d)Computed versus experimental critical heat fluxes (Series 2).
(a)
(b)
(c)
(d)Computed versus experimental critical heat fluxes (Series 3).
(a)
(b)
(c)
(d)


### 5.1.2. Series 4 and Series 13

Series 4 and Series 13 introduce the effect of nonuniform axial profile. A cosine shape was adopted on the same bundle geometry used for Series 2. To deal with nonuniform heat flux, a correction factor was adopted, as proposed by Tong and Tang [13]. In Figures 10 and 11 calculated and experimental critical heat fluxes are compared, respectively, for Series 4, Series 13. As for previous tests, the Shah model predicts higher critical heat flux values than the Katto and Ohno model, providing a better agreement with experimental values. Minor differences are experienced between the homogenized and the subchannel description.Computed versus experimental critical heat fluxes (Series 4).
(a)
(b)
(c)
(d)Computed versus experimental critical heat fluxes (Series 13).
(a)
(b)
(c)
(d)


### 5.1.3. Series 8

Series 8 includes the presence of a central thimble rod, representing guide tube for control rods. Contrarily to the previous series, the results of the homogenized and the subchannel approaches are different (see Figure12). As expected, in the presence of a radial heterogeneous power shape, a better description is achieved with the subchannel approach. In general the Shah model gives a better estimate of critical heat fluxes.Computed versus experimental critical heat fluxes (Series 8).
(a)
(b)
(c)
(d)


## 5.1.1. Series 0, Series 2, and Series 3

Series 0, Series 2 investigate boiling crisis in rod bundle (rods array:5×5) and uniform heat flux. The two series differ only for the position of mixing and spacer grids. In Series 3, the bundle is also modified, adopting an array of 36 rods (6×6). The axial power shape is uniform for all series, but peripheral rods have a slightly lower power with respect to central rods: the radial power distribution factor is 0.85 for peripheral rods and 1.0 for central rods.In Figures7, 8, and 9, calculated and experimental critical heat fluxes are compared, respectively, for Series 1, Series 2, and Series 3. It is ascertained that the Shah model tends to predict higher critical heat flux values than the Katto and Ohno model, for both the bundle-averaged and the subchannel approach. Moreover, in this particular configuration with uniform heat flux and a moderate radial offset, 1D or 3D calculations give very similar results.Computed versus experimental critical heat fluxes (Series 0).
(a)
(b)
(c)
(d)Computed versus experimental critical heat fluxes (Series 2).
(a)
(b)
(c)
(d)Computed versus experimental critical heat fluxes (Series 3).
(a)
(b)
(c)
(d)


## 5.1.2. Series 4 and Series 13

Series 4 and Series 13 introduce the effect of nonuniform axial profile. A cosine shape was adopted on the same bundle geometry used for Series 2. To deal with nonuniform heat flux, a correction factor was adopted, as proposed by Tong and Tang [13]. In Figures 10 and 11 calculated and experimental critical heat fluxes are compared, respectively, for Series 4, Series 13. As for previous tests, the Shah model predicts higher critical heat flux values than the Katto and Ohno model, providing a better agreement with experimental values. Minor differences are experienced between the homogenized and the subchannel description.Computed versus experimental critical heat fluxes (Series 4).
(a)
(b)
(c)
(d)Computed versus experimental critical heat fluxes (Series 13).
(a)
(b)
(c)
(d)


## 5.1.3. Series 8

Series 8 includes the presence of a central thimble rod, representing guide tube for control rods. Contrarily to the previous series, the results of the homogenized and the subchannel approaches are different (see Figure12). As expected, in the presence of a radial heterogeneous power shape, a better description is achieved with the subchannel approach. In general the Shah model gives a better estimate of critical heat fluxes.Computed versus experimental critical heat fluxes (Series 8).
(a)
(b)
(c)
(d)


## 5.2. Transient Series

Two experimental campaigns have been consecrated to detect boiling crisis in transient conditions. Different transient conditions have been investigated by NUPEC, including power increase, inlet temperature decrease, flow reduction, and depressurization. Two series of data have been proposed, Series 11 and Series 12, involving different bundle configurations. Series 11 is based on the bundle configuration adopted for Series 4 (cosine axial power shape, rods array5×5), whereas Series 12 involves a central thimble rod. In the following tables, results obtained by the Shah model with the subchannel approach are listed. Boiling crisis is relatively well predicted for Series 11, whereas a larger discrepancy is ascertained for Series 12 (see Table 9).Table 9
Comparison between calculated and experimental boiling crisis detection time.
Boiling crisis
Series 11
Series 12
detection time (s)
EXP
CALC
EXP
CALC
Power increase
106.7
108.7
86.6
72.2
Flow reduction
52.9
48.8
55.0
42.9
Depressurization
88.8
90.8
143.8
140.9
Temperature decrease
140.6
143.3
128.8
121.4


## 6. Conclusions and Perspectives

This paper has presented the current capabilities of the FLICA-OVAP code in predicting void distribution and boiling crisis phenomena. The NUPEC database released in the frame of the OECD/PSBT international benchmark has been addressed.Void fraction measurements in the subchannel configurations are of major interest for the validation of mass transfer model and the OSV criterion. In this analysis, the attention was focused on the mass transfer model, but further improvement of this work could include the analysis of other OSV criteria. Results obtained by FLICA-OVAP with a set of standard coefficients for the different models show a good agreement of the calculated densities and a slight underestimation of the void fraction at the measurement location, mainly located in the saturated regime for the considered runs.For the steady-state bundle tests, theKv0 coefficient and diffusion coefficients kt and mt are the key parameters to fit the void fraction. In particular, mixing grid spacers play a major role, since they enhance the turbulence in the downstream flow. It was found that a reasonably good agreement between calculated and experimental void fraction profiles is achieved when the turbulent diffusion associated to mixing grid is taken equal to kts=mts=0.045. Adopting the same set of parameters, a reasonably good agreement between calculated and experimental void fraction was also ascertained for transient tests, even if a systematic underestimation of void fraction at the middle and upper measurement locations has been found.Discrepancies noticed on temperature increase transients were corrected by applying a delay of 6 s of the original inlet temperature boundary conditions, in order to simulate the residence time of the fluid between the temperature probe where the boundary conditions are given and the inlet of the test section.Results obtained from the subcooled region suggest possible directions to be pursued in order to improve the current modeling: further developments and validation will involve the OSV criterion and the modeling of heat flux and heat flux partitioning in subcooled nucleate boiling, but also the modeling of inter-phase mass transfer and turbulent diffusion terms.To predict boiling crisis, two different models have been tested: the Shah and the Katto and Ohno model. Both a bundle-averaged and subchannel approaches have been investigated. The Shah model, as implemented in the FLICA-OVAP code allows achieving a better prediction of critical heat fluxes in the different investigated configurations. Nevertheless, when the details of the radial power shape become important, better agreement was obtained with the subchannel approach permitting a local description of bundle thermal-hydraulics. Encouraging results were also obtained from the analysis of transient tests aimed at predicting the onset of boiling crisis. Future activities are also planned for future developments of the code, including the implementation of Groeneveld’s look-up table [14] and other models based on local approaches.



---

*Source: 436142-2012-10-09.xml*