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Gas Turbine Handbook : Principles and Practices

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164 <strong>Gas</strong> <strong>Turbine</strong> <strong>H<strong>and</strong>book</strong>: <strong>Principles</strong> <strong>and</strong> <strong>Practices</strong><br />

Figure 10-7. Typical Duct Wall Cross Section<br />

There are no published algorithms or simple equations for<br />

calculating the noise reduction double wall designs can achieve but<br />

there are a limited number of papers 16 that address the design issues<br />

<strong>and</strong> offer limited design tools; reference [17] provides excellent<br />

resources as well. In most cases the c<strong>and</strong>idate wall system is built<br />

<strong>and</strong> tested to verify performance 18 <strong>and</strong> most OEMs <strong>and</strong> Noise Control<br />

Engineers working in the field have extensive databases on duct<br />

wall performance. And the orientation of the wall does not affect TL<br />

performance; the thinner liner sheet can be on the outside or the<br />

inside depending on design latitudes or requirements. In acoustics,<br />

this is referred to as the Law of Reciprocity.<br />

Certain mass properties of the shell plate must also be carefully<br />

evaluated on the basis of their application. A well-known phenomenon<br />

occurs when the stiffness-bending wavelength of the shell<br />

plate is coincident with an excitation or forcing frequency such as<br />

the inlet bpf. This coincidence frequency (fc) results in a dramatic<br />

reduction in the duct wall transmission loss at that frequency because<br />

of the matching of the two wavelengths—the airborne to the<br />

structure where the wall becomes nearly “transparent” acoustically.<br />

This frequency may be estimated by the following equation 17<br />

fc = c o 2<br />

2É • ph B<br />

1/2<br />

Hz<br />

(10-8)<br />

<strong>and</strong><br />

B =<br />

Eh 3<br />

12 1–ν 2 (10-9)

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