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 ...

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Numerical simulation of a syngas-fuelled engine 1200 1000 Volume (cm3) 800 600 400 200 Experimental Polynomial 0 180 210 240 270 300 330 360 390 420 450 480 510 540 Crank Angle (degrees) tel-00623090, version 1 - 13 Sep 2011 Figure 6.7 – In-cylinder volume polynomial fitting: compression and expansion of downdraft syngas with ignition 12.5 ms BTDC. For this reason, the volume fitting function was divided into two parts one for compression and another for expansion reducing the fitting error to 0.5%. 6.2.2.3 Heat transfer A common practice in engine testing for combustion diagnostic is, prior to the usual firing tests, to test the engine in motored conditions, with air as the only working gas, and the in-cylinder pressure being recorded by a piezoelectric transducer (Lapuerta et al., 2003). The study of the compression process in a RCM operating without combustion is useful to identify different parameters related with its operation, namely the heat transfer to the walls. Once determined, these parameters can also be used during the usual firing cycle. In fact, a determinant parameter in the code is the heat transfer coefficient, which should be calibrated. The pressure signals of single compression are used to determine the heat transfer on the RCM. Figure 6.8 shows the comparison between experimental and numerical in-cylinder pressure without combustion. 184

Chapter 6 40 Experimental 30 Numerical Pressure (bar) 20 10 0 180 210 240 270 300 330 360 Crank Angle (degrees) tel-00623090, version 1 - 13 Sep 2011 Figure 6.8 - Comparison between experimental and numerical in-cylinder pressure during compression of downdraft syngas without combustion. From figure 6.8 is seen that the Woschni model works well in its original formulation and represent the heat transfer of the RCM compression stroke. 6.3.2.4 Turbulent burning velocity As reported in section 3.2.5 the turbulence intensity was experimentally determined for the RCM, and was implemented in the code in the expression (6.26) for validation proposes. The laminar burning velocity formulation obtained in the section 4.1.2.3 was also used to close expression (6.26). 6.3.2.5 Results and discussion Figures 6.9-6.10 show experimental and numerical cylinder pressure for typical downdraft syngas-air mixture and methane-air mixture for various ignition timings, respectively. 185

Chapter 6<br />

40<br />

Experimental<br />

30<br />

Numerical<br />

Pressure (bar)<br />

20<br />

10<br />

0<br />

180 210 240 270 300 330 360<br />

Crank Angle (<strong>de</strong>grees)<br />

tel-00623090, version 1 - 13 Sep 2011<br />

Figure 6.8 - Comparison between experimental and numerical in-cylin<strong>de</strong>r pressure during<br />

compression of downdraft syngas without <strong>combustion</strong>.<br />

From figure 6.8 is seen that the Woschni mo<strong>de</strong>l works well in its original formu<strong>la</strong>tion<br />

and represent the heat transfer of the RCM compression stroke.<br />

6.3.2.4 Turbulent burning velocity<br />

As reported in section 3.2.5 the turbulence intensity was experimentally <strong>de</strong>termined for<br />

the RCM, and was implemented in the co<strong>de</strong> in the expression (6.26) for validation<br />

proposes. The <strong>la</strong>minar burning velocity formu<strong>la</strong>tion obtained in the section 4.1.2.3 was<br />

also used to close expression (6.26).<br />

6.3.2.5 Results and discussion<br />

Figures 6.9-6.10 show experimental and numerical cylin<strong>de</strong>r pressure for typical<br />

downdraft syngas-air mixture and methane-air mixture for various ignition timings,<br />

respectively.<br />

185

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