# Development of a FPI Detailed Chemistry Tabulation Methodology for Internal Combustion Engines

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Outils de simulation pour la conception et le contrôle du groupe motopropulseur

## Methodology for Internal Combustion Engines

### , O. Colin and S. Jay

Institut français du pétrole, IFP, Direction Techniques d’Applications énergétiques, 1-4 avenue de Bois-Préau, 92852 Rueil-Malmaison Cedex - France

e-mail: cecile.pera@ifp.fr - olivier.colin@ifp.fr - stephane.jay@ifp.frCorresponding author

Résumé — Développement d’une tabulation FPI pour la prise en compte de la chimie complexe dans la simulation 3D moteurs — L’objectif de cette étude est d’utiliser une tabulation de la chimie

de type FPI (Flame Prolongation of ILDM) pour la simulation 3D de la combustion dans les moteurs. La première diﬃculté a été d’adapter la méthode à des codes compressibles tout en se limitant à des tailles de tables raisonnables. Pour satisfaire ces contraintes, une nouvelle formulation a été proposée. Elle permet de garder une structure de code basée sur le transport de quelques espèces chimiques tout en assurant la cohérence de l’évolution du système grâce à une équation pour l’avancement de la réaction. Le terme source chimique impliqué dans cette dernière est directement extrait de la tabulation. L’approche retenue permet également d’appliquer la modélisation FPI à des problématiques moteur comme l’utilisation de carburants complexes caractérisés par des chimies détaillées très lourdes ou la combustion fortement diluée. Le modèle proposé, introduit dans le code de simulation moteur IFP-C3D, a été validé sur des configurations homogènes à volume constant et à volume variable contrôlé. Enfin, le modèle complet a été appliqué avec succès à un cas moteur Diesel à injection directe.

Abstract — Development of a FPI Detailed Chemistry Tabulation Methodology for Internal Com-bustion Engines — In this paper, the FPI (Flame Prolongation of ILDM) approach for chemistry

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NOMENCLATURE

c Progress variable

e Internal energy

es Sensible energy of the mixture

hif Formation enthalpy of the species i

Mi Molar weight of species i

p Pressure

t Time

T Temperature

Yc Linear combinaison of species mass fractions

YD Dilution mass fraction

Yi Species i mass fraction

YD

i Mass fraction for dilution species

YiFPI Species i tabulated mass fraction YiT Tracer mass fraction of species i

δt Current computation time step

φ Fuel/air equivalence ratio

ρ Density

τ Characteristic time

˙

ωc Progress variable source term

˙

ωe Energy source term

˙

ωi Species i source terms

INTRODUCTION

Ecological and economical issues motivate engine research to develop advanced technologies and dedicated engine con-trol management. In this context, concon-trol targets are becom-ing more and more diﬃcult to reach. For this purpose, CFD (Computational Fluid Dynamics) is used to better under-stand new concepts such as Diesel HCCI (Homogeneous Charge Compression Ignition) and LTC (Low Tempera-ture Combustion) combustion modes or Controlled Auto-Ignition (CAIT M). It is also useful to optimize the engine

lay-outs in order to fully benefit from these new combustion concepts.

In particular, one key-point is to reduce pollutant emis-sions revealing a crucial challenge for combustion and chemistry modeling. Basically, modeling pollutant emis-sions involve two coupled models: the chemical mechanism and the turbulent combustion model. The chemical scheme needs to be complete enough to recover the correct tem-perature, pressure and dilution dependence. This chemical mechanism cannot be directly used in the CFD code at least for two reasons: first, it involves untractable computation times; secondly, pollutant chemistry in engines is not usu-ally taking place in a perfectly mixed mixture. Therefore, a turbulent combustion model is necessary to account for the local species and temperature stratification.

The question is then how can we include the complex chemistry information into the turbulent combustion model in a way that maintains reasonable computation times.

Over the past decade, various strategies such as ILDM (Intrinsic Low-Dimensional Manifolds) [1-3] or ISAT (in

situ adaptive tabulation)  have been investigated to

answer this question. ILDM [1-3] uses chemical character-istic time scale analysis to construct low-dimensional sur-faces (manifolds) in phase space for given thermodynamic conditions (pressure, fuel/air equivalence ratio, ...) consid-ering eigenvalues and eigenvectors of the chemical system. This approach allows to parametrize the evolution of the whole chemical system using a small number of coordi-nates (relevant species mass fraction) that are stored in a look-up table. The details of this procedure can be found in [1, 2]. The ISAT approach  was originally developed for eﬃcient computation of combustion chemistry. It cor-responds to a storage/retrieval technique for the calculation of composition changes due to chemical reaction in order to optimize chemical CPU time. The tabulation is built on the fly within the 3D CFD code because its pre-computation for all possible states would lead to an extremely large and unmanageable database as the simulation proceeds. When a constitutive response to an integration point is needed, the system either returns a tabulated response from the database or runs the underlying complex constitutive model adding the response to the database. The accuracy of the method depends on a parameter called error tolerance which con-trols the retrieving error from the ISAT constructed tabula-tion.

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Even if diﬀerent examples have demonstrated the abil-ity to apply the FPI approach to laboratory and industrial situations [9, 14, 16, 17], its implementation within a 3D engine simulation code has not yet been performed to our knowledge. Indeed, the large number of variable thermo-dynamic parameters (temperature, pressure, fuel/air equiva-lence ratio, dilution, ...) in addition to their large range of variation makes the use of reasonable database size diﬃcult to achieve.

A new formulation of the FPI method is proposed in this paper allowing application of this strategy to internal combustion engine industrial calculations. First, we point out the coupling with a fully compressible solver. Then, atomic equations are written to ensure mass conservation of the method for complex engine fuel chemistry. Finally, the method is applied to real engine calculations (includ-ing huge ranges of variable operat(includ-ing conditions dur(includ-ing the whole cycle) leading to an adapted tabulation generation and methodology applicable to internal combustion engines.

The aim of this paper is to present adaptations and val-idations of the FPI tabulation method for engine applica-tions which allow to use this approach with a maximum coherence and minimum requirement on the database size. In particular, a serious diﬃculty is to limit the number of discretization points for the progress variable.

This paper is organized as follows. First, an approach is proposed to use the FPI model within a fully compress-ible solver which is often the case of internal combustion engine codes. It includes a strategy to deal with complex engine fuel in particular atomic mass conservation issue thanks to specific species reconstruction. The second sec-tion is devoted to the definisec-tion of a progress variable com-patible with variable dilution fractions. Then, the FPI tab-ulation generation as well as an adapted methodology for internal combustion engine are detailed. Finally, the pro-posed model is implemented within the turbulent combus-tion model ECFM3Z (3-Zones Extended Coherent Flame Model)  in the IFP-C3D code . IFP-C3D is a 3D CFD code using unstructured meshes and ALE (Arbitrary Lagrangian Eulerian) finite volume method dedicated to internal combustion engine simulations. The FPI approach is first validated in constant volume homogeneous reactor configurations for diﬀerent conditions. It is then extended to variable volume in order to test tabulation crossing inter-polation. Finally, it is applied to a Diesel engine case to illustrate its ability to reproduce a real engine configuration.

1 FPI APPROACH FOR COMPRESSIBLE FLOW SOLVERS 1.1 Relaxation Method Towards Tabulated Manifolds:

Database Size Reduction

The FPI method is based on manifold trajectories in the con-tinuity of ILDM, and was initially developped from simple

structure flame collection [9-11, 14]. It assumes that the species trajectories (for given thermodynamic conditions) are uniquely related to a progress variable, c, allowing for chemistry representation with a small database. Hence, for each property:

AFPI = A(−

X, c) (1) whereA is the chemical state (species composition, temper-ature...) of the considered system and −→X is the phase space

vector of thermodynamic conditions including, for instance, local temperature, pressure, fuel/air equivalence ratio, dilu-tion, heat losses, ...

Two diﬀerent strategies can be used to couple this tabula-tion approach with a fully compressible flow solver: 1. The mean density equation is deduced from a balance

equation and a Yc (linear combinaison of some species

mass fractions) equation is introduced. The Yc

combi-naison allows the definition of the progress variable c (see Eq. 11). Consequently, species concentrations are directly retrieved from the tabulation and do not need to be transported. The temperature is deducted from an energy equation. In addition, the only reaction rate needed is that of Ycthat is also tabulated.

2. In other codes, species transport equations need to be solved and temperature is reconstructed from species mass fractions and energy. This is the case for most 3D engine codes because spray evaporation coupling, pollu-tant modeling and variable density accounting are much easily handeled using species transport equations. In this case, Ycis a function of transported species mass

frac-tions (most of the time the choice Yc = YCO+ YCO2 is

done).

When species are transported (second case above), two dif-ferent approaches can also be considered to define the reac-tion rate:

– 2.1 Species reaction rates, ˙ωi, are tabulated from the FPI

collection flamelets,

– 2.2 Species mass (or mole) fractions are tabulated. Most of previous works have used option 1, Ycand

den-sity equation [12, 14] or option 2.1, species transport equa-tions and tabulated reaction rates . Because of their target applications involving fewer input data within rela-tively small variations (in comparison with engine operating points), their number of tabulated points were not strictly limited. So, they were able to perform highly refined tab-ulations. Unfortunately, in engine applications, numerous operating conditions (temperature, pressure, fuel/air equiv-alence ratio, dilution...) over a large range limit the num-ber of tabulated points to conserve a manageable database size. In this context, species transport (option 2.1), unlike Yc

transport (option 1), can lead to trajectory inconsistencies in composition space if no refined tabulation discretisation is used.

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source terms must be considered. In that case, coarse FPI tabulation involves reaction rate integration errors that may be cumulated and, in some cases, induce trajectory diver-gence in composition space. To overcome this problem, a new approach (option 2.2 above) has been proposed in this paper: species source terms, ˙ωi, are reconstructed from

tab-ulated species mass fraction through the first approximation: ˙ ωi=∂Y i ∂t = YFPI i (c(t+ τ)) − Yi(t) τ (2)

where Yidenotes species mass fraction and YiFPI is the FPI

tabulated species. t is the current time andτ is a characteris-tic time scale allowing to relax towards tabulated chemistry. It must be greater than the current time step but very small compared to the characteristic combustion reaction time. τ is then limited by:

δt < τ << 1− c ˙ ωc

(3) withδt denoting the current computation time step and ˙ωc

the progress variable source term. Then, Equation (2) allows FPI chemistry trajectories to relax towards tabulated mani-folds within a characteristic timeτ. Boundaries of relation (3) are the following:

– ifτ = δt: the FPI composition trajectory goes back to the detailed chemistry manifold within only one compu-tational time-step;

– ifτ → 1/ ˙ωc: the composition relaxes towards

equilib-rium values. This philosophy can be linked with the CLEH (Combustion Limited by Equilibrium Enthalpy) model .

In Equation (2), c(t+ τ) is the progress variable at time

t+ τ. It is approximated by a linear interpolation:

c(t+ τ) = c(t) + τ ˙ωFPIc (4)

where ˙ωFPI

c is the tabulated progress variable reaction rate.

The value YiFPI(c(t+ τ)) in Equation (2) is then the corre-sponding mass fraction for a combustion progress c(t+ τ).

The progress variable reaction rate ˙ωFPI

c was initially

directly taken from the complex chemistry calculation. It was observed in this case that very small increments of the progress variable of the order of 1/100 were necessary to construct the FPI table in order to follow correctly the com-plex chemistry calculation. Therefore, we propose instead to assume a constant progress variable reaction rate ˙ωFPI

c

between two consecutive values cj−1and cjof the FPI table:

˙ ωFPI cj = cj− cj−1 tj− tj−1 for c∈ [cj−1; cj[, j = 2, ..., Nc (5)

with time tjsuch as c(tj) = cjextracted from the complex

chemistry simulations. For the first interval ( j= 1), a linear

evolution of the progress variable is imposed assuming it corresponds to a small advancement (c 10−3):

˙ ωFPI cj=1= c1 t1 (6) This formulation allows us to recover correctly the auto-ignition delay with no extreme refinement in progress vari-able close to c = 0. Theoretically, at the beginning of combustion, the progress variable is zero and as well as its source term given by the complex chemistry and no reac-tion can therefore occur. Instead, Equareac-tion (6) means that the first tabulated progress variable point (c1) is reached

after a physical time t1. An alternative strategy is that used

in the TKI approach (Tabulated Kinetics Ignition)  for the auto-ignition delay, where a fictive species equation is used to recover the moment when the auto-ignition delay is reached.

Even if Equation (5) involves an approximation of the evolution of the reaction rate with piecewise constant val-ues (order one in time), it was observed that the proposed methodology (Eq. (2-6)) allows the FPI trajectory to repro-duce the detailed chemistry manifold with a rerepro-duced num-ber of tabulated points for the progress variable (31 values in our case). Consequently, contrary to the other tabulated variables, reaction rate is not interpolated in the direction of the progress variable. Equation (5) rather imposes constant value within each progress variable intervals.

The explained methodology (Eq. 2-6) allows FPI trajec-tories to reproduce the detailed chemistry manifold with a reduced number of tabulated points particularly concerning the progress variable.

1.2 Mass Conservation

Complex chemistry for hydrocarbons involves hundreds of species. However, it is not possible to tabulate all of them and a selection has to be made. Let N be the number of species involved in the detailed chemistry. The FPI tabula-tion may take into account only M species (M ≤ N). If no continuity equation is solved, the combustion energy source term is constructed from the M species source terms:

˙ ωe=

M≤N i=1

hifω˙i (7)

where hif is the formation enthalpy of the species i. Clearly,

M << N species are tabulated because real engine fuels

involve hundreds of intermediate species (about 400 species for the DCPR-laboratory  mechanism). Consequently, the method does not exactly conserve either mass or energy.

M major species must be chosen so that Equation (7) should

be as close as possible to the actual energy source term N

i=1h f

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Selection of main species is straight forward for light hydrocarbons like methane . However, it is more dif-ficult for complex fuels like n-heptane because of the cool flame chemistry involving hundreds of radicals . In fact, in spite of their small individual contribution, their total con-tribution may not be negligible compared to Equation (7) approximation. At this point, two diﬀerent strategies can be adopted:

– the mass of species not accounted for in the M species tabulated is reported on N2. This method is simple but

does not conserve the mass of individual atomic elements (C, H and O), that are "transformed" in N2. This solution

oﬀers the advantage that only the N2profile is perturbed

compared to complex chemistry. This method cannot be applied to cool flame chemistry for which omitted inter-mediate hydrocarbons are crucial to represent correctly the global heat release;

– atomic conservation equations are written. For hydro-carbon combustion, H, C and O balance equations are considered. Consequently, three species evolutions are reconstructed and only M− 3 species are retrieved from the tabulation. The selection of the three reconstructed species is rather tricky: as they are reconstructed and represent the mass of all other non tabulated species, their mass fractions diﬀer significantly from that given by complex chemistry. As a consequence, their impact on the combustion energy source term (Eq. 7) can be artif-ically important and lead to approximate evolutions of the temperature. This method is physically more accept-able but it leads to diﬀerences between detailed chemistry and reconstructed species profiles. Reconstructed species must therefore be carefully selected.

For the reasons mentioned above, considering engine fuel chemistry, the second method has been kept.

After various tests, we have finally chosen the following set of species: CO, CO2, H2O, the engine fuel CxHyand the

radical H are tabulated from the complex chemistry auto-ignition simulations. Notice that atomic H is considered because of its energy contribution (see Eq. 7) despite of its negligible mass. To conserve H and O atomic elements, respectively O2and H2atomic budgets are written. Because

most of the energy variation during the cool flame is due to intermediate and radical hydrocarbons, C conservation is the most diﬃcult equation to close. It must involve a hydrocarbon species which energy source term is represen-tative of the global contribution of intermediate species not accounted for. Meeting this requirement is quite complex, and after various tests, considering n-heptane as the fuel, the C7H14was found to give a good match between the

approx-imate source term of Equation (7) and the exact one. Once again, this reconstructed C7H14species does not represent a

real species involved in the reference complex chemistry. It must be seen as a "dummy species" which evolution reflects

missing tabulated carbon atoms in the system compared to detailed kinetics.

Finally, for C7H16 with the FPI tabulation of the DCPR

 mechanism, nine species are transported (M= 9): CO2,

CO, H2O, C7H16, H, N2, O2, H2and C7H14. The tabulated

species are CO2, CO, H2O, C7H16and H, while, O2, H2and

C7H14are deduced from atomic budgets:

YO2 = − MO2 2  YCO MCO + 2 YCO2 MCO2 + YH2O MH2O  + YT O2 (8) YC7H14 = − MC7H14 7 ⎡ ⎢⎢⎢⎢⎢ ⎣−7Y T C7H16− YC7H16 MC7H16 + YCO MCO + YCO2 MCO2  (9) YH2 = − MH2 2 ⎡ ⎢⎢⎢⎢⎢ ⎣16 YT C7H16− YC7H16 MC7H16 + 14YC7H14 MC7H14 + 2 YH2O MH2O + YH MH  (10) where Yi is the mass fraction of species i and YiT is the

concentration of the tracer of species i known from the ECFM3Z framework (for details on tracer species and ECFM3Z model see Reference ).Midenotes the molar

weight of species i. The reader may notice that the N2source

term is zero if NOx chemistry is not considered and conse-quently the atomic budget in N simply leads to no correction of the N2 mass fraction. As a first step in the FPI-engine

development, NOx chemistry is not considered in this study. Once the five tabulated species (CO2, CO, H2O, C7H16

and H) have been advanced in time using their reaction rates

(Eq. 2), the three remaining species (O2, C7H14and O2) are

obtained applying the above atomic budgets (in addition to N2that is conserved).

Following Equations (8-10), not only the mass is con-served but also the nature of the atoms which is physically more acceptable than an N2adjustment.

2 CHOICE OF COORDINATES: PROGRESS VARIABLE DEFINITION

As explained previously, the FPI approach assumes the com-bustion state to be uniquely defined by a progress variable

c. In the context of simple hydrocarbon fuels like methane

or propane, previous FPI works [9, 14, 25] have suggested to define the progress variable as a linear combination of major species, Yc = YCO+ YCO2. Nevertheless, concerning

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0 0.05 0.1 0.15 0.2 0.25 0.3 YCO+YCO2 500 800 1100 1400 1700 2000 2300 2600 Temperature (K) φ = 0.3 φ = 0.5 φ = 0.7 φ = 1.2 φ = 1. φ = 1.5 φ = 1.7 φ = 2. φ = 2.5 φ = 3 Figure 1

Evolution of temperature versus YCO+ YCO2for homoge-neous constant volume auto-ignition calculations for dif-ferent values of the fuel/air equivalence ratio. Initial condi-tions: T0= 600 K, p0= 20 bar, no dilution.

0 5 10 15 20 Time (ms) 600 1000 1400 1800 2200 2600 Temperature (K) N2 N2+CO2+H2O 830K 60bar 10bar 830K 10bar 60bar 700K 700K Figure 2

Comparison of temperature profiles (homogeneous con-stant volume auto-ignition calculations) obtained with a realistic dilution composition (N2 + CO2 + H2O) and the pure N2simplification. Chemkin computations for n-heptane with detailed chemistry ,φ = 1, 20% of dilution (volume).

proposed Yc= YCO+YCO2−YO2because of the relatively

reg-ular oxygen consumption during the combustion reaction. In each case, the progress variable is defined as :

c= Yc− Y 0 c Yceq− Yc0 (11) where Y0 cand Y eq

c are respectively the initial and the

equilib-rium mass fraction of the Ycadvancement.

All these definitions have been verified to be monotonic in time (see for instance the progress variable evolution in

Fig. 9). Indeed, for the CO + CO2 definition, no turning

points appear even if rich mixtures are considered as illus-trated in Figure 1. This means that each value of the progress variable corresponds to a unique set of mixture composi-tion and temperature (Fig. 1). For rich condicomposi-tions, this phe-nomenon is attributed to chemical equilibrium between CO and CO2as observed in . Diﬀerent progress variable

def-initions have been tested and the "classical FPI definition" (Yc= YCO+ YCO2) is finally chosen.

This definition assumes that the initial amount of carbon in the fuel is oxidized into final products CO and CO2during

the combustion process. However, CO and CO2can also be

found initially inside the combustion reactor within residual burnt gases or exhaust burnt gases:

Yc0= YCO0 + Y 0

CO2  0 (12)

For instance, considering LTC (Low Temperature Combus-tion), operating points with large dilution rates (about 50% in mass) are common issues. In that case, at the beginning of combustion, the progress variable must be zero in spite of the fact that YCO+ YCO2 is not zero. Consequently, CO

and CO2 coming from combustion reaction must be

distin-guished from residual burnt gases. For this purpose, the total mass fraction of any species i, YT OT

i is decomposed

into a "combustion contribution" Yiand a dilution part YiD

which corresponds to the species mass fraction present prior to combustion:

YiT OT = Yi+ YiD (13)

The dilution part, YD

i , can be given by a specific transport

equation as explained in . In practice, for Diesel engine applications, most of the time, YD

i = 0 except for species

CO, CO2, H2O and N2 which represent the main

constitu-ants of burnt gases.

However, the decomposition coming from Equation (13) assumes that the dilution fraction YD

i is not involved in

the combustion process. This is, of course, an approx-imation since there is no chemical diﬀerence nor segre-gation between dilution gases and combustion products. The authors recognize that making no allowance for resid-ual burnt gases composition can be discussed, in particu-lar in the context of several studies on chemical dilution eﬀects on combustion . Nevertheless, this hypothesis is used instead of taking into account complete dilution gases composition because in this case, the complete dilu-tion gases composidilu-tion would appear as input parameters of the database, which would increase the database size by at least two orders of magnitude. In spite of its simplic-ity, this assumption is reasonable, as shown by Figure 2, since dilution gases are mainly composed of N2with a small

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are assimilated to N2 and only their total mass fraction YD defined by: YD= M  i=1 YiD (14)

is considered as an input in the FPI table. Consequently, the progress variable is defined by substracting to the total CO and CO2mass fractions, their dilution contribution:

c= (YCO− Y D CO)+ (YCO2− Y D CO2) (YCOeq − YD CO)+ (Y eq CO2− Y D CO2) (15) This definition corresponds to the "classical FPI" definition assuming initial burnt gases are chemically neutral. It has been verified to be a monotonic function of time for all thermodynamic conditions: it strictly increases in time from

c= 0 (fresh gases) to c = 1 (burnt gases). Thus, the

com-bustion reaction state is uniquely defined by this progress variable.

3 FPI CHEMISTRY DATABASE GENERATION AND FPI-ENGINE METHODOLOGY 3.1 FPI Database Generation

Originally, the FPI method assumes that the flamelet con-sidered for tabulation is a laminar premixed flame or a diﬀu-sion laminar counter-flow flame. In the present study we instead consider auto-ignition homogeneous constant vol-ume reactors using the Senkin code from the Chemkin pack-age . Although this reactor is not properly speaking a flame, we still employ the expression “FPI table’’ to desig-nate it because the methodology is exactly the same as with premixed or non-premixed flames. Homogeneous reactor simulations were chosen because, in the context of Diesel engine calculations, the ignition delay must be evaluated with precision. Premixed or diﬀusion flames cannot lead to a good estimation of this delay for two reasons:

1. When using premixed flames, an equivalent “ignition delay’’ can be obtained by a simple integration of the progress variable reaction rate over time. But this delay does not necessarily correspond to the auto-ignition delay because the space diﬀusion of species and temperature in the premixed flame alters the chemical path compared to a homogenous auto-ignition.

2. It was observed that reduced chemical mechanisms do not allow a precise estimation of cool and main auto-ignition delays over the wide range of pressure, temperature, fuel/air equivalence ratio and dilution rates encountered in Diesel piston engines. Consequently, only complex mechanisms with hundred of species incor-porating the most complete description of auto-ignition reactions can be used. These mechanisms cannot be today used in premixed or diﬀusion laminar flames because of the excessive CPU time required to solve these large systems.

Diesel fuel is known to be composed of many hydrocar-bons for which complex chemical mechanisms are not avail-able today. In this paper, n-heptane has been chosen, as a first step, as a surrogate fuel to represent Diesel kinetics. The DCPR kinetics  is employed for the complex chemistry calculations. This mechanism includes about 400 species and 1500 reactions and has been widely validated [6,24,30]. The mechanism used in this paper was generated automati-cally by the EXGAS-ALKANES software developped at the DCPR laboratory in Nancy. It includes three sub sets:

– A C0− C2reaction base involving species with up to two

carbon atoms.

– A comprehensive primary mechanism which only

con-siders initial organic compounds and oxygen as reactants.

– A lumped secondary mechanism. The molecules

pro-duced in the primary mechanism, with the same molec-ular formula and the same functional groups are lumped into one unique species without distinction between dif-ferent isomers.

For a complete description of the detailed chemical mecha-nism used in this work, we refer the reader to .

In a piston engine, auto-ignition takes place, most of the time, near the top dead center inducing a strong pres-sure increase within a small and almost constant volume variation. In this situation, perfoming the a priori chemi-cal kinetic simulations in a constant volume configuration seems more justified than doing so at constant pressure. Consequently, we generated our FPI table from constant volume Perfectly Stirred Reactor (PSR) calculations.

3.2 Tabulation of Inputs and Outputs

The full variety of compositions and initial conditions is described by four inputs: the initial temperature, T0 and

pressure, p0, the fuel/air equivalence ratio, φ and the

dilu-tant volumic fraction (corresponding to the mass fraction YD

given by Eq. 14). As explained in Section 2, we approx-imate the dilutant composition by uniquely considering N2

dilution for the FPI tabulation generation (of course, the real exhaust burnt gases composition can be included in the 3D CFD calculation). The progress variable (Eq. 15) is added to describe the combustion reaction state. The following ranges are used to construct the complete FPI database: – 8 initial pressures between 10 bar and 100 bar,

– 6 fuel/air equivalence ratios between φ = 0.3 and φ = 3, – 4 dilutant rates between 0% and 80% of the total volume, – 55 initial temperatures between 550 K and 1500 K, – 31 values of the progress variable c (Eq. 15).

Therefore, for all these operating points, auto-ignition is calculated in a constant volume reactor using Chemkin  with the DCPR detailed kinetics for n-heptane .

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(compression, heat release, heat losses, ...), the definition of FPI input coordinates for each computational cell needs to be adressed. Determining cell composition (fuel/air equiva-lence ratio and dilution) is trivial. However, local database input temperature and pressure are less easy to find. Indeed, the local temperature T and pressure p are known in each computational cell, but, the FPI table is based on the initial temperature T0and pressure p0of the constant volume PSR

calculation. We now explain how these variables can be linked.

Even if species composition is varying in the constant volume PSR calculation, internal energy is conserved during auto-ignition: e= es(T )+ M  i=1 Δhf iYi= cst (16)

with esthe sensible energy of the mixture defined by:

es= hs− p/ρ (17)

where the sensible enthalpy is hs =

T

Tre fCpdT with Cp the

heat capacity at constant pressure of the mixture and Tre f a

reference temperature for which the standard reference state is usually used (Tre f = 298.15 K).

The tracer species (cf. ECFM3Z model ) allow to define entirely the initial composition of the mixture Y0

i.

Using Equation (16), the initial sensible energy can be calcu-lated: es(T0)= e−iM=1Δh

f

iYi0. This initial temperature T0is

finally deduced from es(T0) and Yi0, and the initial pressure

p0is given by the equation of state:

p0=ρ0

RT0

M0

(18) whereM0 is the molar mass of the mixture, R the perfect

gas constant andρ0the initial density.

Regarding FPI outputs, the progress variable reaction rate ˙

ωFPI

cj is given by Equation (5) and species mass fractions

YFPI

i (T0, p0, φ, YD, c), i = CO, CO2, H2O, C7H16, H are

directly read from the PSR stored calculations. An example of a FPI tabulation point is displayed in Figures 3 (species) and 4 (progress variable reaction rate).

In the 3D CFD calculation, in each cell and at each time-step, local conditions (T0, p0,φ, YDand c) are determined

to be used as tabulation inputs. Concerning the interpola-tion, the method uses polynomial matrix coeﬃcient for each output variable. For instance, dealing with reaction rate, only four interpolation directions are considered (tempera-ture, pressure, fuel/air equivalence ratio and dilution) and no interpolation on progress variable direction is needeed as explained previously. Consequently, the reaction rate is

0 0.2 0.4 0.6 0.8 1 Progress variable 0 0.02 0.04 0.06 0.08 0.1 0.12 0.14 Mass fraction CO2 C7H16 CO H2O H Figure 3

FPI tabulation example for the point: T0= 700 K, p0= 30 bar, φ = 0.7 and no dilution. Species tabulation (Circles: CO, Diamonds: CO2, squares: fuel, triangles: H2O and stars: H) extracted from detailed chemistry (lines). Between two tabu-lated points (progress variable discretization), the method will linearly interpolate the corresponding mass fractions.

ωc

c Figure 4

FPI tabulation example for the point: T0= 700 K, p0= 30 bar, φ = 0.7 and no dilution. Reaction rate tabulation constructed from detailed chemistry using Equation (5). Between two tab-ulated points (progress variable discretization), reaction rate is a constant according to Equation (5).

interpolated using 24= 16 coeﬃcients with: ˙

ωc= a0+ a1T0+ a2p0+ a3φ + a4YD+ a5T0p0 (19)

+ a6T0φ + a7T0YD+ a8p0φ + a9p0YD

+ a10φYD+ a11T0p0φ + a12T0p0YD

+ a13T0φYD+ a14p0φYD+ a15T0p0φYD

in which T0and p0are the local cell input temperature and

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iFPI

irecons

(Eq. 4)

iFPI

PSR cst volume

iFPI ,C H H

### )

H2O 7 16, CO , CO 2

,

### FPI tabulation

(Eq. 5) , H C H7 16 ,H2O, CO , CO 2 C H7 14,H2 O2,N2 ,

### c(t)

(Eq. 15) Figure 5

FPI-engine method sketch.

local fuel/air equivalence ratio and YDis the local dilution of

each cell. The coeﬃcients a0to a15are constant only in each

hyper-cube defined by pi 0 < p0< p i+1 0 , T j 0 < T0< T j+1 0 etc.

(where i and j suﬃxes are respectively FPI discretization points in the pressure and the temperature directions). Note that these coeﬃcients a0to a15are function of the progress

variable c.

3.3 Methodology for Internal Combustion Engine Applications

The above FPI tabulation technique has been implemented in the CFD engine code IFP-C3D . The calculation algorithm of the model is the following (see Fig. 5): – The nine species presented above are transported in the

CFD code. Five are tabulated (CO, CO2, H2O, C7H16

and H) and four are built from atomic balance equations (C7H14, O2, H2and N2).

– In each computational cell, the amont of dilution gases

YD

i is known thanks to the tracer species transport

equa-tions. These dilution gases are subtracted from the total species mass fractions as in Equation (13).

– At each calculated point, the progress variable is evalu-ated by Equation (15).

– Local input conditions (T0, p0,φ, YD) for FPI tables are

determined.

– Progress variable reaction rate, ˙ωc(T0, p0, φ, YD, ci), with

ci< c < ci+1is obtained by interpolation in the FPI

tabu-lation (along (T0, p0, φ, YD) directions) and the evolution

of the progress variable at time t+τ is estimated according to Equation (4).

– Tabulated species mass fractions Yi(T0, p0, φ, YD, c(t +τ))

are retrieved by interpolation in the FPI table. The next time step mass fractions are then deduced:

Yi(t+ δt) = Yi(t)+δt τ YiFPI(t+ τ) − Yi(t) (20) – Reconstructed species are built from atomic balance

(Eq. 8-10).

– Dilution gases are added to recover the total mass frac-tions (Eq. 13).

4 VALIDATIONS

4.1 Constant Volume Reactors

The model is first validated on the simple configuration of a homogeneous constant volume reactor. Considering adia-batic conditions, the FPI-engine simulation and the complex chemistry obtained with Chemkin solver are compared in Figures 6 to 8. Diﬀerent conditions were tested varying the fuel/air equivalence ratio (from φ = 0.3 to φ = 3) and the initial thermodynamic conditions within engine ranges (from atmospheric pressure to 100 bar, low (< 700 K) and high (> 1200 K) temperature, from no dilution to high EGR (Exhaust Gas Recirculation) level (80%).

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Figure 6

Comparison of temperature profiles obtained with the FPI-engine model on IFP-C3D code (symbols) and with the Chemkin detailed chemistry computations (solid line). Perfect Stirred Reactor at constant volume for a lean case (φ = 0.7) with initial conditions: T0= 700 K, p0= 30 bar, no dilution.

Figure 7

Comparison of main species profiles obtained with the FPI-engine model on IFP-C3D code (symbols) and with the Chemkin detailed chemistry computations (solid line). Perfect Stirred Reactor at constant volume for a lean case (φ = 0.7) with initial conditions: T0= 700 K, p0= 30 bar, no dilution.

the detailed chemistry of DCPR  and for the FPI-engine model run in IFP-C3D. In the same way, Figures 7 and 8 illustrate main species evolutions respectively for a lean (φ = 0.7) and a rich case (φ = 1.5). In all tested cases, the FPI modeling shows good agreement compared to detailed chemistry in terms of reactor temperature evolution but also in terms of species dynamics. It can be noticed that both temperature and tabulated species profiles slightly diﬀer from complex chemistry reference due to the small num-ber (31) of progress variable values. As it can be clearly seen

Figure 8

Comparison of main species profiles obtained with the FPI-engine model on IFP-C3D code (symbols) and with the Chemkin detailed chemistry computations (solid line). Perfect Stirred Reactor at constant volume for a rich case (φ = 1.5) with initial conditions: T0= 700 K, p0= 30 bar, no dilution.

in Figure 6, 7 and 8, the temperature and tabulated species evolution is piecewise linear due to the piecewise constant progress variable reaction rate (Eq. 5). But by construction, the complex chemistry temperature and tabulated species evolution are exactly recovered at each discretized progress variable point ci.

On the contrary, reconstructed species like O2 can

sig-nificantly diﬀer from complex chemistry calculation, espe-cially in the cool flame region (see Fig. 7). As explained above, because all intermediate and radical species are not taken into account (for example: CH4, CH3, OH, ...),

reconstructed species represent all "omitted" species. For instance, oxygen atoms can be involved in many products such as oxygenated intermediate hydrocarbons that are not considered in the present table. Instead, missing oxygen atoms are reported by the oxygen balance equation into O2.

Consequently, the O2evolution is diﬀerent from that of the

detailed chemistry. Authors agree that reporting the oxygen mass balance into the O2species might not be the optimum

solution since O2 is a major species involved in pollutant

formation for instance. Actually, work is planed to realize a coupling between this FPI model and pollutant models of NOx and soot. In this context, this assumption will be reconsidered and a minor species containing the oxygen ele-ment will be selected to close the oxygen atomic budget. Nevertheless, as a first step of modeling development, this approach has been chosen for the present paper.

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Figure 9

Influence of the characteristic relaxation timeτ (Eq. 2-4) on temperature description. Line: reference detailed chemistry of C7H16-mechanism of DCPR . Dashed-lines: FPI simulation withτ = 0.001 ms, 0.1 ms, and 1 ms. Auto-ignition for a constant volume homogeneous reactor atφ = 1 with no dilution. Initial conditions: T0= 700 K, p0= 30 bar. 6.2 6.3 6.4 6.5 6.6 Time (ms) 10−4 10−3 10−2 10−1 100

Effective relaxation time (ms)

τ = 0.001ms τ = 1ms

Figure 10

Eﬀective relaxation time during the calculation: relaxation timeτ limited by relation (3). Auto-ignition for a constant volume homogeneous reactor atφ = 1 with no dilution. Initial conditions: T0= 700 K, p0= 30 bar.

the FPI tabulated chemistry approach to complex internal combustion engine simulations.

Moreover, it can be noticed that even if only nine species are considered, the method allows to correctly reproduce the temperature evolution (see Fig. 6), not only the final value but also the cool flame heat release (reminding that tem-perature is computed from transported species mass fraction and sensible energy). These first results confirm that C7H14

allows a correct representation of the impact of omitted intermediate species on the heat release. It can be pointed out that most important errors are observed, of course, for rich conditions in which unburnt hydrocarbons are numer-ous but results are still acceptable considering the very lim-ited database size.

4.2 Influence ot the Relaxation Time,τ

The presented FPI methodology involves a characteristic time,τ, within Equations (2) to (4). In practice, this parame-ter can be used to handle numerical stiﬀness which might be problematic in case of a sudden change in the FPI manifold. This situation can happen for instance when gaseous fuel is added by spray evaporation or when very large spatial gradients of mixture fraction are encountered.

First, the influence of parameter τ is investigated on a simple homogeneous constant volume reactor with initial conditions: p0 = 30 bar, T0 = 700 K, φ = 1 without

dilution. Progress variable evolutions with diﬀerent relax-ation times for Equrelax-ations (2-4) are plotted in Figure 9. For this case, the global chemical timeτc(measured as the time

needed for c to go from 0.01 to 0.99 in the detailed chemistry

calculation results) is approximately 0.5 ms. When τ << τc

(0.001 ms in Fig. 9), the FPI trajectory follows very pre-cisely the detailed chemistry one. Forτ = 0.1 ms  0.2τc,

the exact trajectory is still approximately recovered. Finally forτ = 1 ms  2τc, only the cool flame period is correctly

reproduced while an important smoothing of the main flame reaction rate is observed.

This test shows that choosing a very small value for τ will allow in any case, to follow precisely the FPI trajectory but might lead to reaction rate stiﬀness. On the contrary, increasing τ may lead to important trajectory errors. For this reason, a limitation ofτ (Eq. 3) was introduced which guarranties thatτ always remains smaller than a characteris-tic chemical time. The evolution of the eﬀective relaxation time τ (limited by (1 − c)/ ˙ωc) is given in Figure 10 for

τ = 0.001 ms and τ = 1 ms. In the case τ = 0.001 ms, no limitation occurs excepted close to the maximum reaction rate occuring between times 6.5 and 6.6 ms. In the case τ = 1 ms, limitations occur during cool flame (between times 6.2 and 6.3 ms) and during an important part of the main auto-ignition.

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5 6 7 8 Time (ms) 0 0.02 0.04 0.06 0.08 0.1 CO ma ss fraction Detailed chemistry FPI model τ (ms) 0.001ms 1ms Figure 11

Influence of the characteristic relaxation time τ (Eq. 2-4) on CO mass fraction. Line: reference detailed chemistry of C7H16-mechanism of DCPR . Dashed-lines: FPI simula-tion with τ = 0.001 ms and 1 ms (Circles). Auto-ignition for a constant volume homogeneous reactor atφ = 1 with no dilution. Initial conditions: T0= 700 K, p0= 30 bar.

tabulated species (see Fig. 11). This feature is specific to this relaxation method and is not found when tabulated species reaction rates (option 2.1 in the introduction) are used.

4.3 Homogeneous Engine: Variable Volume

In order to better reproduce engine conditions, a variable volume test case corresponding to an engine rotation speed of 2000 rpm has been computed. These tests allow to check numerical time integration accuracy in particular concerning interpolation in the FPI tabulation across temperature and pressure directions. Once again, direct comparisons with Chemkin computations are performed at the same operating conditions (initial pressure and temperature, fuel/air equiva-lence ratio and dilution rate) along with engine volume vari-ation law.

TABLE 1

Volume variable operating point

Bore (mm) 86

Stroke (mm) 73.4

Engine speed (rpm) 2000

Compression ratio 8.55

The present test case corresponds to the following condi-tions: initial temperature, T0 = 750 K and initial pressure,

p0= 20 bar at 30 cad (crank angle degree) before TDC (Top

Dead Center). The example is for a stoichiometric case, φ = 1 with no dilution. The engine-like operating system

−25 −20 −15 −10 −5 0 5 10 15 20 Crank angle (o) 0 0.02 0.04 0.06 0.08 0.1 0.12 0.14 0.16 Mass fraction CO2 CO Figure 12

Homogeneous reactor auto-ignition with variable volume (2000 rpm). CO and CO2mass fractions comparisons between detailed chemistry (lines) and FPI-engine model on IFP-C3D code (symbols). −30 −20 −10 0 10 20 30 Crank angle (o) 600 1000 1400 1800 2200 2600 3000 3400 Temperature (K) Figure 13

Homogeneous reactor auto-ignition with variable volume (2000 rpm). Temperature comparison between detailed chem-istry (line) and FPI-engine model on IFP-C3D code (symbols).

is summarized in Table 1. Results plotted in Figure 12 com-pare CO and CO2mass fraction evolutions predicted by the

FPI approach and the reference detailed chemistry. Once again, an excellent agreement is observed. In particular, it must be pointed out that the cool flame behavior is very well predicted as illustrated in Figure 13.

5 APPLICATION TO A 3D INTERNAL COMBUSTION ENGINE SIMULATION

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5.1 The 3D CFD Code

IFP-C3D  is a 3D CFD parallel code developed at IFP based on Navier-Stokes equations resolved on unstruc-tured meshes using ALE (Arbitrary Lagrangian Eulerian) finite volume method. The turbulent combustion model is the 3-Zone Extended Coherent Flame Model (ECFM3Z) described in . In this model, the local mixture fraction stratification is described thanks to three mixing zones: a pure air zone, a pur gaseous fuel zone and finally a mixed air/fuel zone in which combustion takes place. In this mixed zone, auto-ignition combustion was originally mod-eled by the TKI model . In the present paper, this TKI model is replaced by the proposed FPI approach. Note that as we assume fuel and air to be perfectely mixed in this mixed zone, no statistical averaging over mixture fraction or progress variable of the FPI table needs to be performed like in the FPI-PCM model . Therefore, the FPI model can be directly implemented in ECFM3Z.

5.2 Engine Applications

To illustrate the FPI tabulation approach on Diesel engine simulation, a full load engine naturally aspiratd configu-ration at 1250 rpm with a single spray injection has been calculated. This application is a first step towards full FPI complex chemistry tabulation used for industrial engine research. The purpose of this example is to test the complete methodology on a real engine configuration. Nevertheless, at this stage of the modeling development, only qualitative comparisons are considered since no pollutant models for soot and NOx emissions are included.

Calculations are performed on a single-cylinder engine based on a PSA DW10 DI Diesel engine using a 3D wedge mesh with homogeneous initial conditions at inlet valve clo-sure (146 cad before TDC). Table 2 summarizes the geo-metrical characteristics of the engine and the operating con-ditions.

TABLE 2

Characteristics of the PSA DW10 engine and operating conditions

Bore (mm) 85

Stroke (mm) 88

Compression ratio 18

Engine speed (rpm) 1250

Air flow rate (kg/h) 17.7

Intake Fuel/Air ratio 0.83

Injection timing (cad before TDC) -5

Because FPI-engine methodology involves balance atom equations for none-tabulated species, the choice of a repre-sentative surrogate fuel is crucial. The definition of a real Diesel fuel detailed kinetics is not yet possible. Reminding

−60 −30 0 30 60 90 Crank angle (o) 0 2 4 6 8 Pressure (MPa) Experiment FPI model (IFP−C3D)

Figure 14

Diesel engine pressure: experimental measurement (circles) and calculated pressure profiles (solid line) given by the FPI-engine tabulation method. Case-1.

−60 −30 0 30 60 90 Crank angle (o) 0 2 4 6 8 Pressure (MPa) Experiment FPI model (IFP−C3D)

Figure 15

Diesel engine pressure: experimental measurement (circles) and calculated pressure profiles (solid line) given by the FPI-engine tabulation method. Case-2.

that our purpose is to demonstrate FPI approach feasibil-ity on a complete engine calculation, the surrogate fuel is supposed to have the same chemical global formulation as C7H16including its thermodynamics properties. In contrast,

liquid properties entering the evaporation rate calculation of the spray droplets, are treated as a single component lumped fuel as proposed in  or .

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Auto-ignition delay, maximum cylinder pressure and max-imum pressure timing as well as heat release energy are globally retrieved. Of course, the pressure profiles in diesel engines highly depend on the considered detailed chem-istry because the mechanism defines the auto-ignition delay. Indeed, to be able to correctly predict Diesel engine behav-ior, the auto-ignition timing must be known accurately. To this purpose, it must take into account fine chemistry response and coupling with other physical variations that can be modified by the internal engine geometry or by using diﬀerent engine control strategies. Concerning the IMEP (Indicated Mean Eﬀective Pressure), FPI-engine model sim-ulations are very close to measurements. For the first case, FPI modeling leads to IMEP= 7.8 bar while experiment gives 7.6 bar. Similarly, for the second case the diﬀerence is very small: 6.7 bar for the measurement versus 6.9 bar for FPI prediction.

Species profiles during the calculation, plotted in Fig-ures 16 and 17, show a general good behavior for all con-sidered species (tabulated or reconstructed). Maximum of CO occurs around 10 cad after TDC, then, it is oxidized in CO2 during the expansion stroke. The "dummy species"

C7H14 represents intermediate carbon species. Even if its

mass fraction remains very small (about 0.1% of the total mass), it must be included in the list transported species to reproduce correctly the heat release as explained previ-ously. The final computed CO emission is about 0.32 kg/h for the first case, which is comparable to the measurement, 0.26 kg/h. For the second case (Fig. 17), CO final emission is larger than the first one according to experiment observa-tion. These results allow us to confirm the potential of the FPI method. It must be pointed out that, at this stage of the model development, CO predictions diﬀer from experimen-tal measurements mainly because of the assumption of the surrogate fuel and the lack of information concerning the coupling with other pollutants, in particular soot emissions.

CONCLUSION

A new version of the FPI tabulation chemistry is developed in the context of CFD codes transporting species mass frac-tions. In order to deal with Diesel type engine applications, the FPI approach is modified in three main aspects:

– The premixed laminar flame is replaced by

homoge-neous constant volume calculations to generate the FPI database. These PSR calculations allow the use of large complex chemical mechanisms (with hundreds of species) and a precise estimation of the auto-ignition delay and heat release rate.

– The species reaction rate is not given by the complex

chemistry tabulation as in the original FPI approach but is instead deduced from tabulated mass fractions and the progress variable reaction rate.

5 35 65 95 125 Crank angle (o) 0 0.05 0.1 0.15 Mass fraction CO2 H2O CO O2 C7H14 Figure 16

Main species mass fraction profiles. Circles: O2. Squares: CO2. Diamonds: H2O. Up triangles: CO. Right triangles: "Dummy species" for carbon balance, C7H14. Case-1.

5 35 65 95 125 Crank angle (o) 0 0.05 0.1 0.15 Mass fraction CO2 H2O CO O2 C7H14 Figure 17

Main species mass fraction profiles. Circles: O2. Squares: CO2. Diamonds: H2O. Up triangles: CO. Right triangles: "Dummy species" for carbon balance, C7H14. Case-2.

– Transported species are divided into tabulated and

recon-structed species: tabulated species are chosen as the reac-tants and main products while reconstructed species need to be chosen with care depending on the fuel and chem-ical mechanism. These reconstructed species allow to guaranty atomic conservation in the CFD calculation and to reproduce correctly the heat release rate during the combustion.

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solver of Chemkin for a set of test cases: auto-ignition in a homogeneous reactor with constant and variable volumes over a wide range of thermochemical conditions. Species evolutions as well as reaction heat release are correctly pre-dicted by the FPI-model.

At last, it has been applied to the 3D simulation of a Diesel engine and demonstrated the model capability to reproduce industrial applications. The first results show good agreement with available experimental data. This approach allows a reasonable computation time as well as a manageable FPI database size thanks to the reduced number of progress variable points allowed by the proposed species reaction rate expression.

Future research topics have been identified and will be the subject of coming publications. These include the coupling between the FPI tabulation and other pollutant models such as unburnt hydrocarbons, NOx emission or soot formation. Another stage of the development will consist in applying the proposed model to compounds more representative of Diesel fuel than pure n-heptane. At last, the model achieve-ment will be tested on a wide range of operating engine points (conventional and HCCI Diesel combustion, classic spark ignition, CAIT M engines, ...) in order to verify its capacity to reproduce engine geometric parametric varia-tions or fuel eﬀects.

ACKNOWLEDGEMENTS

This research was partially funded by the GSM (Groupe-ment Scientifique Moteur: PSA Peugeot Citroen, Renault and IFP). Authors wish to thank DCPR laboratory particu-larly F. Battin-Leclerc and its collaborators for providing the n-heptane mechanism of Buda et al. .

REFERENCES

1 Maas U., Pope S. (1992) Simplifying chemical kinetics: Intrin-sic Low-Dimensional manifolds in composition space,

Com-bust. Flame 88, 239-264.

2 Gicquel O., Thevenin D., Hilka M., Darabiha N. (1999) Direct numerical simulation of turbulent premixed flames using intrinsic low-dimensional manifolds, Combust. Theor.

Model. 3, 3, 479-502.

3 Correa C., Niemann H., Schramm B., Warnatz J. (2000) Reac-tion mechanism reducReac-tion for higher hydrocarbons by the ILDM method, Proc. Combust. Inst. 28, 2, 1607-1614. 4 Pope S.B. (1997) Computationally eﬃcient implementation of

combustion chemistry using in situ adaptive tabulation,

Com-bust. Theor. Model. 1, 41-63.

5 Halstead M., Kirsh L., Quinn C. (1977) The autoignition of hydrocarbon fuels at high temperatures and pressures - Fitting of a mathematical model, Combust. Flame 30, 45-60.

6 Buda F., Bounaceur R., Warth V., Glaude P.A., Founet R., Battin Leclerc F. (2005) Progress toward a unified detailed kinetic model for the autoignition of alkanes from C4 to C10 between 600 and 1200 K, Combust. Flame 142, 170-186. 7 Curran H.J., Gaﬀuri P., Pitz W.J., Westbrook C.K. (2002) A

comprehensive modeling study of iso-octane oxidation,

Com-bust. Flame 129, 3, 253-280.

8 Gicquel O., Darabiha N., Thevenin D. (2000) Laminar pre-mixed hydrogen / air counterflow flame simulations using flame prolongation of ILDM with diﬀerential diﬀusion, Proc.

Combust. Inst. 28, 2419-2425.

9 Fiorina B., Baron R., Gicquel O., Thevenin D., Carpentier S., Darabiha N. (2003) Modelling non-adiabatic partially pre-mixed flames using flame-prolongation of ILDM, Combust.

Theor. Model. 7, 3, 449-470.

10 Fiorina B., Gicquel O., Vervisch L., Carpentier S., Darabiha N. (2005) Approximating the chemical structure of partially premixed and diﬀusion counterflow flames using FPI flamelet tabulation, Combust. Flame 140, 3, 147-160.

11 Fiorina B., Gicquel O., Carpentier S., Darabiha N. (2005) Vali-dation of the FPI chemistry reduction method for diluted nona-diabatic premixed flames, Combust. Sci. Technol. 176, 785-797.

12 Domingo P., Vervisch L., Payet S., Hauguel R. (2005) DNS of a premixed turbulent V flame and LES of a ducted flame using a FSD-PDF subgrid scale closure with FPI-tabulated chemistry,

Combust. Flame 143, 4, 566-586.

13 Van Oijen J.A., Lammers F.A., de Goey L.P.H. (2001) A com-prehensive modeling study of iso-octane oxid, Combust. Flame

127, 3, 2124-2134.

14 Vervisch L., Hauguel R., Domingo P., Rullaud M. (2004) Three facets of turbulent combustion modelling: DNS of premixed V-flame, LES of lifted nonpremixed flame and RANS of jet-flame, J. Turbulence 5.

15 Michel J.B., Colin O., Veynante D. (2008) Modeling ignition and chemical structure of partially premixed turbulent flames using tabulated chemistry, Combust. Flame 152, 80-99. 16 Domingo P., Vervisch L., Veynante D. (2008) Large-eddy

sim-ulation of a lifted methane jet flame in a vitiated coflow,

Com-bust. Flame 152, 415-432.

17 Fiorina B., Gicquel O., Vervisch L., Carpentier S., Darabiha N. (2005) Premixed turbulent combustion modeling using tab-ulated detailed chemistry and PDF, Proc. Combust. Inst. 30, 1, 867-874.

18 Colin O., Benkenida A. (2004) The 3-Zones Extended Coherent Flame Model (ECFM3Z) for Computing Pre-mixed/Diﬀusion Combustion, Oil Gas Sci. Technol. 59, 593-609.

19 Zolver M., Klahr D., Bohbot J., Laget O., Torres A. (2003) Reactive CFD in Engines with a New Unstructured Parallel Solver, Oil Gas Sci. Technol. 58, 33-46.

20 Galpin J., Angelberger C., Naudin A., Vervisch L. (2008) Large-eddy simulation of H2-air auto-ignition using tabulated detailed chemistry, J. Turbulence 9, 13, 1-21.

(17)

22 Colin O., Pires da Cruz A., Jay S. (2005) Detailed chemistry-based auto-ignition model including low temperature phenom-ena applied to 3-D engine calculations, Proc. Combust. Inst.

30, 2, 2649-2656.

23 Galpin J., Naudin A., Vervisch L., Angelberger C., Colin O., Domingo P. (2008) Large-eddy simulation of a fuel-lean pre-mixed turbulent swirl-burner, Combust. Flame 155, 1-2, 247-266.

24 Battin-Leclerc F. (2008) Detailed chemical kinetic models for the low-temperature combustion of hydrocarbons with applica-tion to gasoline and diesel fuel surrogates, Prog. Energy

Com-bust. Sci. 34, 4, 440-498.

25 Ribert G., Gicquel O., Darabiha N., Veynante D. (2006) Tabu-lation of complex chemistry based on self-similar behavior of laminar premixed flames, Combust. Flame 146, 649-664. 26 Embouazza M., Gicquel O., Darabiha N. (2003) Modelling

autoignition of HCCI engine by reduced tabulated chemistry,

Proc. Third Mediterranean Comb. Symp.

27 Mauviot G., Albrecht A., Poinsot T.J. (2006) A new 0D approach for Diesel Combustion Modeling coupling probabil-ity densprobabil-ity function with complex chemistry, SAE paper 2006-01-3332.

28 Anderlohr J.M., Piperel A., Pires da Cruz A., Bounaceur R., Battin-Leclerc F., Montagne X. (2008) Influence of EGR compounds of the oxidation of an HCCI-Diesel surrogate,

Proc. Combust. Inst. 32, 2, 2851-2859.

29 Kee R.J., Rupley F.M., Miller J.A., Coltrin M.E., Grcar J.F., Meeks E., Moﬀat H.K., Lutz A.E., Dixon-Lewis G.,

Smooke M.D., Warnatz J., Evans G.H., Larson R.S., Mitchell R.E., Petzold L.R., Reynolds W.C., Caracotsios M., Stewart W.E., Glarborg P., Wang C., McLellan C.L., Adigun O., Houf W.G., Chou C.P., Miller S.F., Ho P., Young P.D., Young D.J., Hodgson D.W., Petrova M.V., Puduppakkam K.V. (2006) Chemkin Release 4.1, Reaction Design Report - San Diego. 30 Pires da Cruz A., Pera C., Anderlohr J., Bounaceur R.,

Battin-Leclerc F.A. (2007) Complex chemical kinetic mechanism for the oxidation of gasoline surrogate fuels: n-heptane, iso-octane and toluene - mechanism development and validation, Proc.

Third European Combustion Meeting, Chania.

31 Anderlohr J.M., Bounaceur R., Pires da Cruz A., Battin-leclerc F. (2008) Modelling of autoignition and NO sensitization for the oxidation of IC-engine surrogate fuels, Combust. Flame

156, 2, 505-521.

32 Jay S., Beard P., Pires da Cruz A. (2007) Modeling Coupled Processes of CO and Soot Formation and Oxidation for con-ventional and HCCI Diesel Combustion, SAE paper 2007-01-0162.

33 Habchi C., Lafossas F.A., Beard P. (2004) Formulation of a fuel lumping model to assess the eﬀects of fuel thermodynamic properties on internal combustion engine mixture preparation and combustion, SAE paper 2004-01-1996.

Final manuscript received in July 2008 Published online in June 2009
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