Troels Dyhr Pedersen.indd - Solid Mechanics
Troels Dyhr Pedersen.indd - Solid Mechanics
Troels Dyhr Pedersen.indd - Solid Mechanics
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Page 18 of 21<br />
diesel type chamber<br />
3 ATDC<br />
1 BTDC<br />
3 BTDC<br />
1000 3000 5000 f (Hz) 7000 9000<br />
Figure 21: Frequency distribution with the diesel bowl chamber piston<br />
The common feature of all the FFT analysis result is that the largest contribution to the total SPL is found in the<br />
lower part of the frequency band from 1-3 kHz. These frequencies cannot exist inside the cylinder, since the<br />
lowest resonance frequency is 5-6 kHz in all cases except for the ring shaped geometry, which has its primary<br />
resonance frequency at 4 kHz. The 4 kHz frequency is clearly present in the analysis for this piston crown (fig.<br />
16).<br />
Engine block resonance will however occur as a result of higher frequencies being transmitted through the<br />
structure. The connection between structure born noise and emitted noise was investigated by Andreae et al<br />
[10]. It was found that the general source of noise was not that which was directly transmitted, but that of<br />
engine structure resonance being exited by the transmitted noise.<br />
A great reduction in the noise level was achieved by moving the chambers away from the cylinder walls and<br />
into the piston. The total surface area and therefore heat transfer was however increased. The crevice volume<br />
with this and the following pistons was very large since it was not possible to fit piston rings. This resulted in a<br />
reduction of combustion efficiency. In terms of noise reduction the performance was similar. The crevice<br />
volume was however unchanged, so the combustion efficiency was still reduced<br />
Frequency response<br />
The frequency response of the engine is here defined by the ratio of the sound pressure measured outside the<br />
engine to the sound pressure generated in the cylinder. The response is calculated for the range of frequencies in<br />
the FFT. A short term average of 5 ms following the peak heat release was used to allow all established modes<br />
of vibration to be included.<br />
The response is converted to dB. Since -100 dB corresponds to an attenuation of 100,000, a SP of 100 kPa in<br />
the cylinder will result in a SP of 1 Pa outside the engine.<br />
Figure 22 is an example of the frequency response of the flat chamber. The response of the other piston crowns<br />
was found to follow this pattern. The response of the flat chamber was selected because it produces a wide<br />
range of frequencies in the cylinder and thus provides a good signal-to-noise ratio for the response curve.<br />
Sound pressure (Pa)<br />
1<br />
0.8<br />
0.6<br />
0.4<br />
0.2<br />
0