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 6.3 Code validation Due to the lack of experimental apparatus, model testing has been carried on over detailed experimental data available in literature and, in particular, the standard CFR, single cylinder, engine has been chosen for the simulations. Two fuels were selected that are present on syngas: hydrogen and methane. As far as hydrogen fueling is concerned, the extensive measurements of Verhelst, (2005) have been chosen as a reference, while the in-cylinder pressures traces by Bade and Karim, (2001) have been considered when dealing with methane. An attempt to validate the code by comparison with experimental results obtained in this work in the RCM is made. 6.3.1 CFR engine tel-00623090, version 1 - 13 Sep 2011 A Cooperative Fuel Research engine, known as the CFR engine, is an engine originally used for the determination of fuel octane numbers, now also equipped for gaseous fuels. It is characterized by its engine speed kept constant by coupled electric motor, and its variable compression ratio. The main engine specifications are given in Table 6.1. Table 6.1 - Basic CFR engine data Items Specification Engine type Cooperative Fuel Research (CFR) Number of cylinders 1 Bore × Stroke 82.55 × 114.2 (mm) Connecting rod length 254 mm Displacement 611.7 cm 3 Compression ratio Variable Engine speed Variable 6.3.1.1 Sub-models Most of the predictive capability of a quasi-dimensional model relies on the accuracy of the implemented sub-models. Sub-models are needed for closing the equations for pressure, temperatures and masses of the two zones: in particular, a combustion submodel for computing the mass burning rate, and a model of heat transfer through the walls; a detailed description of them is given in the following for hydrogen-air and methane-air mixtures. 178
Chapter 6 Heat transfer Wei et al., (2001) and Shudo and Suzuki, (2002) have measured instantaneous heat transfer coefficients in hydrogen fuelled engines. Wei et al. (2001) found transient heat transfer coefficients during hydrogen combustion to be twice as high as during gasoline combustion. They evaluate heat transfer correlations and found Woschni’s equation to underpredict the heat transfer coefficient by a factor of two. tel-00623090, version 1 - 13 Sep 2011 Shudo and Suzuki (2002) compared the heat transfer coefficients during stoichiometric hydrogen and methane combustion, finding them to be larger in the case of hydrogen. The shorter quenching distance of a hydrogen flame is put forward as the cause of this increased heat transfer, leading to a thinner thermal boundary layer. Furthermore, for near-stoichiometric combustion, flame speeds are high and cause intensified convection. Hydrogen has also a higher thermal conductivity compared to hydrocarbons. Shudo and Suzuki, (2002) construct an alternative heat transfer correlation with an improved correspondence with their measurements. However, the correlation contains two calibration parameters, dependent on ignition timing and equivalence ratio. These dependencies are started to be the subject of further studies, so the correlation is not useful for the present work. The correlation by Woschni and Annand have cited to be inadequate [Borman and Nishiwaki, (1987)], even for gasoline and diesel engines, although the correlations have been based on measurements on such engines and use hydrocarbon mixture properties. However, the development of heat transfer correlation for SI engines is not within the scope of this work, it was decided to use the standard model of Woschni with separate values during compression, combustion and expansion as reported by Verhelst and Sierens, (2007). This calibration was made by matching a simulated cylinder pressure trace to a measured pressure trace. The compression heat transfer coefficient can be calibrated to a motored pressure trace. The other coefficients need to be set more or less simultaneously. Turbulent burning velocity The turbulent burning velocity models need laminar burning velocity data of the air/fuel/residuals mixture at the instantaneous pressure and temperature. As most models use the laminar burning velocity as the local burning velocity, such as the DamkÖhler model, the stretched burning velocity should be used. 179
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Chapter 6<br />
Heat transfer<br />
Wei et al., (2001) and Shudo and Suzuki, (2002) have measured instantaneous heat<br />
transfer coefficients in hydrogen fuelled engines. Wei et al. (2001) found transient heat<br />
transfer coefficients during hydrogen <strong>combustion</strong> to be twice as high as during gasoline<br />
<strong>combustion</strong>. They evaluate heat transfer corre<strong>la</strong>tions and found Woschni’s equation to<br />
un<strong>de</strong>rpredict the heat transfer coefficient by a factor of two.<br />
tel-00623090, version 1 - 13 Sep 2011<br />
Shudo and Suzuki (2002) compared the heat transfer coefficients during stoichiometric<br />
hydrogen and methane <strong>combustion</strong>, finding them to be <strong>la</strong>rger in the case of hydrogen.<br />
The shorter quenching distance of a hydrogen f<strong>la</strong>me is put forward as the cause of this<br />
increased heat transfer, leading to a thinner thermal boundary <strong>la</strong>yer. Furthermore, for<br />
near-stoichiometric <strong>combustion</strong>, f<strong>la</strong>me speeds are high and cause intensified<br />
convection. Hydrogen has also a higher thermal conductivity compared to<br />
hydrocarbons. Shudo and Suzuki, (2002) construct an alternative heat transfer<br />
corre<strong>la</strong>tion with an improved correspon<strong>de</strong>nce with their measurements. However, the<br />
corre<strong>la</strong>tion contains two calibration parameters, <strong>de</strong>pen<strong>de</strong>nt on ignition timing and<br />
equivalence ratio. These <strong>de</strong>pen<strong>de</strong>ncies are started to be the subject of further studies,<br />
so the corre<strong>la</strong>tion is not useful for the present work.<br />
The corre<strong>la</strong>tion by Woschni and Annand have cited to be ina<strong>de</strong>quate [Borman and<br />
Nishiwaki, (1987)], even for gasoline and diesel engines, although the corre<strong>la</strong>tions<br />
have been based on measurements on such engines and use hydrocarbon mixture<br />
properties. However, the <strong>de</strong>velopment of heat transfer corre<strong>la</strong>tion for SI engines is not<br />
within the scope of this work, it was <strong>de</strong>ci<strong>de</strong>d to use the standard mo<strong>de</strong>l of Woschni with<br />
separate values during compression, <strong>combustion</strong> and expansion as reported by<br />
Verhelst and Sierens, (2007). This calibration was ma<strong>de</strong> by matching a simu<strong>la</strong>ted<br />
cylin<strong>de</strong>r pressure trace to a measured pressure trace. The compression heat transfer<br />
coefficient can be calibrated to a motored pressure trace. The other coefficients need<br />
to be set more or less simultaneously.<br />
Turbulent burning velocity<br />
The turbulent burning velocity mo<strong>de</strong>ls need <strong>la</strong>minar burning velocity data of the<br />
air/fuel/residuals mixture at the instantaneous pressure and temperature. As most<br />
mo<strong>de</strong>ls use the <strong>la</strong>minar burning velocity as the local burning velocity, such as the<br />
DamkÖhler mo<strong>de</strong>l, the stretched burning velocity should be used.<br />
179