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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 />

ing efficiency, SE, for which no measurement is available for comparison purposes; the computation<br />

predicts that it has a peak value <strong>of</strong> 0.8 at 6600 rpm.<br />

With the simulation closely predicting air flow <strong>and</strong> power, the potential for accurately<br />

simulating the measured brake specific fuel consumption, bsfc, <strong>and</strong> the emissions <strong>of</strong> hydrocarbons,<br />

bsHC, is realized in Fig. 5.11.<br />

500 -,<br />

^ 400 -<br />

g 300 -<br />

CO<br />

GQ<br />

°3 200<br />

O<br />

LL<br />

CO<br />

m 100 4<br />

CALCULATED<br />

MEASURED<br />

BRAKE SPECIFIC FUEL CONSUMPTION<br />

BRAKE SPECIFIC HYDROCARBON EMISSION<br />

CALCULATED<br />

D B g Si £—g—g °~~Q •<br />

MEASURED<br />

0 —. 1 « 1 1 1 • 1 > 1 > 1<br />

5000 6000 7000 8000 9000 10000 11000<br />

ENGINE SPEED, rpm<br />

Fig. 5.11 Measured <strong>and</strong> computed bsfc <strong>and</strong> bsHC characteristics <strong>of</strong> a chainsaw.<br />

The closed cycle simulation, relying on the combustion <strong>and</strong> heat transfer theory <strong>of</strong> Chapter<br />

4, is seen to give a more than adequate representation <strong>of</strong> that behavior in Figs. 5.12 <strong>and</strong><br />

5.13. In Fig. 5.12 are the measured <strong>and</strong> computed cylinder pressure diagrams at 9600 rpm,<br />

<strong>and</strong> while the error on peak pressure is relatively small, the computation <strong>of</strong> the angular position<br />

<strong>of</strong> peak pressure is completely accurate. In Fig. 5.13 at the same speed is the comparison<br />

<strong>of</strong> measurement <strong>and</strong> calculation <strong>of</strong> the cylinder pressures during compression <strong>and</strong> expansion.<br />

The Ann<strong>and</strong> model <strong>of</strong> heat transfer in Sec. 4.3.4, <strong>and</strong> the fuel vaporization model in Sec.<br />

4.3.5, can be seen to provide very accurate simulation <strong>of</strong> the compression <strong>and</strong> expansion<br />

processes. The measured data are averaged over 100 engine cycles.<br />

<strong>Design</strong> data available from the simulation, Figs. 5.14-5.27<br />

The computation provides extensive information for the designer, much <strong>of</strong> which can be<br />

measured only with great difficulty, or even not at all due to the lack <strong>of</strong>, or the non-existence<br />

<strong>of</strong>, the necessary instrumentation. Much <strong>of</strong> this information is required so that the designer<br />

can comprehend the internal gas-dynamic <strong>and</strong> thermodynamic behavior <strong>of</strong> the engine <strong>and</strong> the<br />

influence that changes to engine geometry have on the ensuing performance characteristics.<br />

The following is a sample <strong>of</strong> the range <strong>and</strong> extent <strong>of</strong> the design information which an accurate<br />

382

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