Etude de la combustion de gaz de synthèse issus d'un processus de ...
Etude de la combustion de gaz de synthèse issus d'un processus de ... Etude de la combustion de gaz de synthèse issus d'un processus de ...
Numerical simulation of a syngas-fuelled engine ⎛ VT ⎞ s r v = ⎜2. 28Sp + 0. 00324 ( P −Pmot) ⎟ ⎝ Pr Vr ⎠ (6.25) Where P mot =P r (V r /V) γ is the motored pressure. S p is mean piston speed (m/s), V s is swept volume (m 3 ), V r , T r and P r are volume, temperature and pressure (m 3 , K, bar) evaluated at any reference condition, such as inlet valve closure, V is instantaneous cylinder volume (m 3 ) and γ is the specific heat ratio. The second term in the velocity expression allows for movement of the gases as they are compressed by the advancing flame. 6.1.4 Mass burning rate tel-00623090, version 1 - 13 Sep 2011 In the combustion modeling studies, the main purpose is to specify the mass fraction of burned gases at any time during the combustion process. This is achieved by using several approaches. In general, two approaches have been widely used for determining the mass fraction burned. In the first approach, the mass fraction burned at any crank angle is specified by using empirical burning laws, such as the cosine burn rate formula and Wiebe function (Heywood et al., 1979). This approach does not necessitate detailed combustion modeling, hence modeling of combustion in this manner is more practical, but it gives less reliable or less sensitive results about SI engine combustion [Heywood et al., (1979); Bayraktar and Durgun, (2003)]. Empirical burning equations include some constants that must be determined suitably at the beginning of computation. In the case of using the Wiebe function, these are the efficiency parameter, the form factor, the crank angle at the start of combustion and the combustion duration. For the cosine burn rate formula, these are spark advance and combustion duration. In such models, these parameters are generally determined either by matching the experimental mass fraction burned curves obtained from the cylinder pressure measurements with the calculated ones or by making an engineering judgment [Zeleknik (1976); Heywood et al. (1979)]. If sufficient agreement is achieved between the calculated and measured pressures, then the chosen parameters are used for parametric studies. In the second approach, the combustion is modeled by considering the turbulent flame propagation process (Heywood, 1988). This modeling technique is generally called quasi-dimensional modeling because it accounts for the details of engine geometry and the flame propagation process and therefore will be followed in this work. The role of in-cylinder air motion begins from the very start of the engine cycle. During the intake stroke, the incoming air generates flow structures with large-scale turbulent 174
Chapter 6 motions within the cylinder, which in turn determines the extent of mixing between the fresh charge and the residuals, as well as internal and external heat transfer rates. The key to the premixed combustion modeling is the prediction of S te, the turbulent flame speed normal to the surface of the flame. In turbulent flames, the flame speed depends on both chemical kinetics and the local turbulence characteristics. Many methods for describing and calculating the turbulent flame speed have been developed (see for instance the excellent review of Lipatnikov and Chomiak, (2002)). The goal of this work is to develop a fast simulation program for the combustion of syngas in spark ignition engines. The main interest is the pressure development in the engine cylinders, which is directly related to the power output and the efficiency. Therefore, in this work the so-called DamkÖhler method is used and according to this model turbulent flame speed is as follows (Blizard and Keck, 1974): tel-00623090, version 1 - 13 Sep 2011 S = C u + S (6.26) te 2 ' Where, u’ is the root mean square (rms) turbulent velocity, C 2 a calibration constant dependent of the engine geometry and S u the laminar burning velocity. Obviously, proper in-cylinder turbulence modeling needs to be estimated. For this propose, a simple turbulence model, firstly proposed by Hall and Bracco, (1987) and used by several authors [Verhelst and Sierens, (2007); Farhad et al., (2009); Federico et al., (2010)] has been considered: ⎛ θ − 360 ⎞ u' TDC = 0.75up = 0.75(2 sn), u' = u' TDC ⎜1−0.5 45 ⎟ (6.27) ⎝ ⎠ u where u’ TDC is the rms turbulent velocity at TDC, taken to be 0.75 times the mean piston speed; θ is the crank angle and, s, is the stoke. A linear decay of the rms turbulent velocity u’ from top dead center is imposed. 6.2. Numerical solution procedure The basic concept of the model is the division of the burned gas region into several distinct zones for taking into account the temperature stratification of the burned gas. The multi-zone simulation model is applied throughout the closed part of the engine cycle, between IVC and EVO, i.e. compression, combustion and expansion. Admission phase is also included in the code in order to take into account the heating of the 175
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Chapter 6<br />
motions within the cylin<strong>de</strong>r, which in turn <strong>de</strong>termines the extent of mixing between the<br />
fresh charge and the residuals, as well as internal and external heat transfer rates. The<br />
key to the premixed <strong>combustion</strong> mo<strong>de</strong>ling is the prediction of S te, the turbulent f<strong>la</strong>me<br />
speed normal to the surface of the f<strong>la</strong>me. In turbulent f<strong>la</strong>mes, the f<strong>la</strong>me speed <strong>de</strong>pends<br />
on both chemical kinetics and the local turbulence characteristics.<br />
Many methods for <strong>de</strong>scribing and calcu<strong>la</strong>ting the turbulent f<strong>la</strong>me speed have been<br />
<strong>de</strong>veloped (see for instance the excellent review of Lipatnikov and Chomiak, (2002)).<br />
The goal of this work is to <strong>de</strong>velop a fast simu<strong>la</strong>tion program for the <strong>combustion</strong> of<br />
syngas in spark ignition engines. The main interest is the pressure <strong>de</strong>velopment in the<br />
engine cylin<strong>de</strong>rs, which is directly re<strong>la</strong>ted to the power output and the efficiency.<br />
Therefore, in this work the so-called DamkÖhler method is used and according to this<br />
mo<strong>de</strong>l turbulent f<strong>la</strong>me speed is as follows (Blizard and Keck, 1974):<br />
tel-00623090, version 1 - 13 Sep 2011<br />
S = C u + S<br />
(6.26)<br />
te<br />
2<br />
'<br />
Where, u’ is the root mean square (rms) turbulent velocity, C 2 a calibration constant<br />
<strong>de</strong>pen<strong>de</strong>nt of the engine geometry and S u the <strong>la</strong>minar burning velocity.<br />
Obviously, proper in-cylin<strong>de</strong>r turbulence mo<strong>de</strong>ling needs to be estimated. For this<br />
propose, a simple turbulence mo<strong>de</strong>l, firstly proposed by Hall and Bracco, (1987) and<br />
used by several authors [Verhelst and Sierens, (2007); Farhad et al., (2009); Fe<strong>de</strong>rico<br />
et al., (2010)] has been consi<strong>de</strong>red:<br />
⎛ θ − 360 ⎞<br />
u' TDC<br />
= 0.75up = 0.75(2 sn), u' = u' TDC ⎜1−0.5<br />
45<br />
⎟<br />
(6.27)<br />
⎝<br />
⎠<br />
u<br />
where u’ TDC is the rms turbulent velocity at TDC, taken to be 0.75 times the mean<br />
piston speed; θ is the crank angle and, s, is the stoke. A linear <strong>de</strong>cay of the rms<br />
turbulent velocity u’ from top <strong>de</strong>ad center is imposed.<br />
6.2. Numerical solution procedure<br />
The basic concept of the mo<strong>de</strong>l is the division of the burned gas region into several<br />
distinct zones for taking into account the temperature stratification of the burned gas.<br />
The multi-zone simu<strong>la</strong>tion mo<strong>de</strong>l is applied throughout the closed part of the engine<br />
cycle, between IVC and EVO, i.e. compression, <strong>combustion</strong> and expansion. Admission<br />
phase is also inclu<strong>de</strong>d in the co<strong>de</strong> in or<strong>de</strong>r to take into account the heating of the<br />
175