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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 />

The front <strong>of</strong> all pressure waves travels at the local speed <strong>of</strong> sound, ao, which from Eq.<br />

2.1.1 is:<br />

a o = ^YR(Texc + 273) m/s (2.1.1)<br />

For engines below 5 bar bmep the value <strong>of</strong> Texc will be in the region <strong>of</strong> 350°-450°C, <strong>and</strong><br />

R <strong>and</strong> yean be estimated to be as for air at atmospheric conditions, i.e., 287 J/kgK <strong>and</strong> 1.4,<br />

respectively.<br />

Although the exhaust pulse peak will propagate at supersonic velocity, the suction reflection<br />

will travel at subsonic speed <strong>and</strong> the average can be approximated to the local speed <strong>of</strong><br />

sound (see Sec. 2.1.3). If you assume that the exhaust pulse peak occurs at 15° after exhaust<br />

port opening, you would wish the peak <strong>of</strong> any suction reflection to return at or about the bde<br />

piston position. This gives a reflection period in degrees crankshaft <strong>of</strong> 0^,:<br />

6rp=^ L -15 (6.2.1)<br />

The time, t^, taken for this double length travel along the pipe, Lj, must equal the reflection<br />

period, where:<br />

6rp 60 2Lj<br />

T ~ 71^ X ~ T^Ti (6.2.2)<br />

360 rpm 1000a0<br />

Incorporating Eq. 6.2.1 <strong>and</strong> rearranging Eq. 6.2.2 to obtain the pipe length, Li, which is in<br />

mm units:<br />

=<br />

41^.(6,-30)<br />

If the appropriate numbers are inserted into this equation for a chainsaw at 8000 rpm,<br />

with an assumed exhaust gas mean temperature <strong>of</strong> 400°C, <strong>and</strong> an exhaust period <strong>of</strong> 160°<br />

crankshaft, then Li is derived as 352 mm. As there is clearly no possibility <strong>of</strong> installing a 352mm-long<br />

downpipe on a compact chainsaw, the designer is left to dimension a silencer box<br />

which will merely have the least possible restrictive effect on gas flow from the engine, while<br />

still silencing it to the legislative requirement. This effect is abundantly evident from the<br />

discussion in Chapter 5. Fortunately the two aims are not mutually incompatible, as the largest<br />

possible box can be ingeniously designed into the available space so as to give the best<br />

power output <strong>and</strong> the best silencing effect. See Chapter 8 for an exp<strong>and</strong>ed discussion on noise<br />

<strong>and</strong> silencing.<br />

The basic rule <strong>of</strong> thumb for simple exhaust silencer boxes, be they a single box, or the<br />

double box design as seen in Fig. 5.6, is to set the total box volume to at least ten swept<br />

volumes <strong>and</strong> the final outlet pipe to about 50% <strong>of</strong> the area <strong>of</strong> the exhaust port.<br />

436<br />

rpm

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