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Design and Simulation of Two Stroke Engines

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<strong>Design</strong> <strong>and</strong> <strong>Simulation</strong> <strong>of</strong> <strong>Two</strong>-<strong>Stroke</strong> <strong>Engines</strong><br />

Appendix A7.1 The effect <strong>of</strong> compression ratio on performance characteristics <strong>and</strong> exhaust<br />

emissions<br />

Appendices A4.1 <strong>and</strong> A4.2 describe a two-zone combustion model, with equilibrium<br />

thermodynamics giving dissociation for the burn zone constituents <strong>and</strong> a formation model for<br />

nitric oxide based on reaction kinetics. This model is sufficiently fundamentally based as to<br />

be able to calculate the local thermodynamic conditions during combustion <strong>and</strong>, when combined<br />

with a GPB simulation <strong>of</strong> the open cycle behavior <strong>of</strong> an engine <strong>and</strong> its ducting, is able<br />

to provide design guidance for the effect <strong>of</strong> compression ratio on the engine performance<br />

characteristics <strong>of</strong> power output, fuel consumption, the intake <strong>and</strong> exhaust noise emissions,<br />

<strong>and</strong> the gaseous exhaust emissions. In short, as mentioned at the beginning <strong>of</strong> Sec. 7.3.3, a<br />

full debate can be conducted on the design compromises which inevitably have to be made<br />

for any given engine to satisfy the market <strong>and</strong> legislative requirements for it.<br />

The engine used as the design example is the st<strong>and</strong>ard chainsaw engine, used frequently<br />

throughout the book, but first introduced with geometrical input data in Sec. 5.5.1. The data<br />

are as presented there, but with the trapped compression ratio, CRt, changed successively<br />

from 6.5 to 7.0 (the "st<strong>and</strong>ard" value), 7.5 <strong>and</strong> 8.0. The engine will assuredly give some<br />

detonation at a CRt value <strong>of</strong> 8.0. For each <strong>of</strong> the simulations the engine speed employed is<br />

9600 rpm, together with an air-to-fuel ratio <strong>of</strong> 13.0 on unleaded gasoline, which translates to<br />

a X value <strong>of</strong> 0.9. The combustion model is exactly as described in Sec. 5.5.1, i.e., as it is<br />

shown in Fig. 4.7(d), with an ignition timing at 24° btdc used within each simulation.<br />

The results <strong>of</strong> the modeling are shown in Figs. A7.1-A7.4. It should be noted that the<br />

delivery ratio <strong>and</strong> charging efficiency are ostensibly constant for all <strong>of</strong> these simulations, thus<br />

any changes in performance characteristics are almost entirely due to combustion variations.<br />

The effect <strong>of</strong> compression ratio on power <strong>and</strong> fuel consumption<br />

Eq. 1.5.22 predicts higher power <strong>and</strong> thermal efficiency for increasing compression ratio.<br />

Thermal efficiency is inversely related to brake specific fuel consumption, which can be seen<br />

4.2 -><br />

CHAINSAW ENGINE 9600 rpm<br />

r 470 5.8 -i 26<br />

8 9 6 7<br />

TRAPPED COMPRESSION RATIO<br />

Fig. A7.1 Effect <strong>of</strong> compression ratio on torque, fuel consumption <strong>and</strong> NOx emissions.<br />

536<br />

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