Etude de la combustion de gaz de synthèse issus d'un processus de ...

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Numerical simulation of a syngas-fuelled engine In order to compare pressure evolution of the different fuels at the same ignition timing, figure 6.13 shows this cylinder pressure comparison. 50 Pressure (bar) 40 30 20 Updraft Dow ndraft Methane 10 tel-00623090, version 1 - 13 Sep 2011 0 240 270 300 330 360 390 420 450 480 Crank Angle (degrees) Figure 6.13- Cylinder pressure versus crank angle for various fuels. ε= 8.5, IT= 20º BTDC, 900 rpm. Figure 6.13 shows that higher peak pressure is obtained for methane-air (39 bar) mixture in comparison to both syngas compositions. Syngas compositions have similar behavior. Peak pressures are 35 bar for downdraft syngas and 34 bar for updraft syngas. These results are qualitatively in agreement with the RCM experimental results. However, quantitatively the difference in the maximum pressure is not as high as in RCM. This could be endorsed to the different characteristics of the experimental set ups, emphasized in sections 6.3.1 and 6.3.2. 6.5 Conclusion A simulation code for the power cycle of syngas-fuelled engines has been described, using a quasi-dimensional model with ‘standard’ modeling assumptions. A combustion model consisting of two differential equations was used, one for the mass conservation and one for energy conservation. Model testing has been carried on over detailed experimental data available in literature for hydrogen and methane, two of the main constituents of syngas. The very good agreement found allows validating the developed model and applied it to typical syngas compositions. An attempt to adapt the model to the RCM is made by changing several aspects of the model namely the in-cylinder volume function and burning rate model. The comparison 192
Chapter 6 with experimental results obtained in this work in the RCM shows that the adapted code is able to reproduce fairly well the in-cylinder pressure. The validated model is then applied to a syngas-fuelled engine in order determine its performance. Conclusions can be drawn that typical syngas compositions besides its lower heat value and burning velocities can be used on SI engines even at elevated rotation speeds. Another conclusion is that varying the ignition timing is possible to keep closely the same peak pressure for different rotation speeds. tel-00623090, version 1 - 13 Sep 2011 193
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THÈSE Pour l’obtention du Grade
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Acknowledgements Acknowledgements T
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Résumé __________________________
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Nomenclature Nomenclature Roman tel
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Nomenclature Subscripts tel-0062309
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Contents tel-00623090, version 1 -
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Contents 6.4. SYNGAS FUELLED-ENGINE
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Introduction CHAPTER 1 INTRODUCTION
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Introduction proves to have higher
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Introduction Chapter 3 - Experiment
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Bibliographic revision CHAPTER 2 BI
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Bibliographic revision point today
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Bibliographic revision - Boudouard
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Bibliographic revision Table 2.1 -
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Bibliographic revision Biomass Dryi
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Bibliographic revision Circulating
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Bibliographic revision or eliminate
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Bibliographic revision established
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Bibliographic revision Hydrogen Hyd
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Bibliographic revision of low moist
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Bibliographic revision scrubbing an
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Bibliographic revision suggests tha
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Bibliographic revision 1 d( δ A) 1
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Bibliographic revision Since n is
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Bibliographic revision 2 ( rsr ) 2
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Bibliographic revision This evoluti
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Bibliographic revision The burning
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Bibliographic revision δVG = − a
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Bibliographic revision 2 1 − −
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Bibliographic revision where the su
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Bibliographic revision the stretche
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Bibliographic revision burning velo
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Experimental set ups and diagnostic
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Chapter 4 CHAPTER 4 EXPERIMENTAL AN
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Chapter 4 4.1 Laminar burning veloc
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Chapter 4 4.1.1.1 Flame morphology
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Chapter 4 P i = 1.0 bar, Ti = 293 K
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Chapter 4 Figure 4.5 shows schliere
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Chapter 4 P i = 2.0 bar, T i = 293
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Chapter 4 Sn (m/s) 3.0 2.5 2.0 1.5
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Chapter 4 5 ms 10 ms 15 ms 20 ms 25
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Chapter 4 behaviour of the curves r
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Chapter 4 1.50 Sn (m/s) 1.25 1.00 0
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Chapter 4 0.5 0.4 φ =1.0 Su (m/s)
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Chapter 4 variation of the normaliz
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Chapter 4 4.1.1.6 Comparison with o
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Chapter 4 The values of laminar bur
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Chapter 4 Pressure (bar) 7 6 5 4 3
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Chapter 4 0.5 0.4 φ=1.2 Su (m/s) 0
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Chapter 4 0.3 φ=0.8 Su (m/s) 0.2 0
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Chapter 4 a minimum pressure to exp
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Chapter 4 Notice the similar behavi
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Chapter 4 A very good agreement bet
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Chapter 4 ( ) Q = h T − T (4.21)
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Chapter 4 tel-00623090, version 1 -
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Chapter 4 are tested and discussed.
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Chapter 4 7 500 Pressure (bar) 6 5
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Chapter 4 Pressure (bar) 7 6 5 4 3
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Chapter 4 4.2.3.4 Quenching distanc
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Chapter 4 10000 Quenching distance
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Chapter 5 CHAPTER 5 EXPERIMENTAL ST
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Page 159 and 160: Chapter 5 From figure 5.15 is possi
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Page 163 and 164: Chapter 5 80 Pressure (bar) 70 60 5
Page 165 and 166: Chapter 5 80 10 Pmax (bar) 70 60 50
Page 167 and 168: Chapter 5 -5.0 ms -3.75 ms -2.5 ms
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Page 171 and 172: Chapter 6 CHAPTER 6 NUMERICAL SIMUL
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Page 175 and 176: Chapter 6 H 2 O, (3) N 2 , (4) O 2
Page 177 and 178: Chapter 6 For all the above express
Page 179 and 180: Chapter 6 motions within the cylind
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Page 183 and 184: Chapter 6 Heat transfer Wei et al.,
Page 185 and 186: Chapter 6 The calibration coefficie
Page 187 and 188: Chapter 6 6.3.2.2 In-cylinder volum
Page 189 and 190: Chapter 6 40 Experimental 30 Numeri
Page 191 and 192: Chapter 6 80 70 60 Numerical Experi
Page 193 and 194: Chapter 6 downdraft syngas than for
Page 195: Chapter 6 80 23º BTDC 60 29.5º BT
Page 199 and 200: Conclusions CHAPTER 7 CONCLUSIONS 7
Page 201 and 202: Conclusions radius and time for syn
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Page 207 and 208: References References tel-00623090,
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Page 221 and 222: Appendix A - Overdetermined linear
Page 223 and 224: Appendix A - Overdetermined linear
Page 225 and 226: Appendix B- Syngas-air mixtures pro
Page 227 and 228: Appendix C -Rivère model Heat flux
Page 229 and 230: Appendix C -Rivère model The work
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