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Testing and quality

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TESTING AND QUALITY<br />

0.00 100.00 (mm)<br />

50.00<br />

5 Results of the FEM calculation for the two-diameter <strong>and</strong> three-diameter natural modes.<br />

verified that the mode shape with two<br />

nodal diameters is actually excited<br />

during operation. Figure 4 depicts an<br />

instantaneous deflection state of the<br />

particular vibration mode.<br />

• Example 2 : Zero-diameter mode at<br />

f=900 Hz excited by the 21st order:<br />

From the frequency response function<br />

for the resonant vibration at f = 900 Hz,<br />

it is evident that all three acceleration<br />

signals are in phase <strong>and</strong> have the<br />

same amplitude. This is clearly an axisymmetric<br />

mode with zero nodal<br />

diameters; in this case, verification<br />

by a synchronous animation of the<br />

measured signals <strong>and</strong> the computed<br />

mode shape is unnecessary.<br />

Comparison with results of the FEM<br />

calculation<br />

Finally, the measurement results were<br />

compared with the FEM calculations<br />

carried out by Sulzer Pumps 5. A rotor<br />

surrounded by water was used as<br />

boundary condition. The impeller was<br />

modeled as non-rotating, since stiffening<br />

due to centrifugal forces has only a negligible<br />

influence on the natural frequencies.<br />

Figure 6 shows a comparison of<br />

the measured <strong>and</strong> the computed natural<br />

frequencies.<br />

6 Comparison of the measured <strong>and</strong> computed natural frequencies.<br />

16 | Sulzer Technical Review 1/2011<br />

The frequencies are in good agreement,<br />

except for the «umbrella»-mode with a<br />

measured natural frequency of approx.<br />

900 Hz, vs. the FEM calculation resulting<br />

in a frequency of 701 Hz. This deviation<br />

could be due to a truncated shaft stub,<br />

which is included in the finite element<br />

model.<br />

Note that the forces induced by the<br />

12 diffuser guide vanes <strong>and</strong> acting on<br />

the impeller have lowest relevant excitation<br />

orders of 12 <strong>and</strong> 24; the corresponding<br />

excitation frequencies lie just below<br />

the matching natural modes of the<br />

impeller:<br />

• 12th order of the maximum pump<br />

speed: 1135 Hz ↔ natural frequency<br />

of two-diameter mode: 1150Hz<br />

• 24th order of the maximum pump<br />

speed: 2250 Hz ↔ nat. frequency of<br />

four-diameter mode: 2500Hz.<br />

Spatial aliasing<br />

With seven sensors that are equally<br />

spaced around the circumference, theoretically,<br />

only the vibration modes with<br />

zero to three nodal diameters can be<br />

detected positively. For vibration modes<br />

with four or more nodal diameters,<br />

spatial undersampling occurs due to the<br />

sensor arrangement, which has an insuf-<br />

Number of f [Hz] f [Hz] Remarks Excitation order<br />

nodal diameters<br />

approx. reading computed by FEM from spectrogram<br />

0 900 701 «umbrella»-mode 21<br />

1 750 757 «rocker»-mode 22<br />

2 1150 1199 23<br />

3 1900 1846 24<br />

4 2500 not computed by FEM 38<br />

Max.<br />

5 2800 not computed by FEM<br />

Min.<br />

50.00<br />

0.00 100.00 (mm)<br />

25.00 75.00<br />

ficient sensor density. For instance, mode<br />

shapes with 1 or 6 nodal diameters<br />

cannot be differentiated, since both<br />

modes would result in identical vibrations<br />

at the sensor positions.<br />

With the additional knowledge of the<br />

FEM results, the vibration mode shapes<br />

can usually be unambiguously identified,<br />

even with only three sensors. Without<br />

the combination with FEM results, a considerably<br />

denser sensor arrangement<br />

would be necessary in order to avoid<br />

spatial aliasing.<br />

Interpretation<br />

The vibrations measured during operation<br />

indicate that the natural frequencies<br />

of the impeller are near the predictions<br />

by the FEM. However, the resonances<br />

have sufficient damping so that the corresponding<br />

vibration levels remain well<br />

within acceptable limits <strong>and</strong> the integrity<br />

of the impeller is not at risk.<br />

Literature<br />

• Berten, S., Thesis EPFL No. 4642,<br />

http://library.epfl.ch/en/theses/?nr=4642<br />

• Tanaka, H., “Vibration behaviour <strong>and</strong> dynamic stress<br />

of runners of very high head reversible pump-turbines,”<br />

IAHR Symposium 1990, special session, Belgrade<br />

Ulrich Moser<br />

Sulzer Markets <strong>and</strong> Technology AG<br />

Sulzer Innotec<br />

Sulzer-Allee 25<br />

8404 Winterthur<br />

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

Phone +41 52 262 82 61<br />

ulrich.moser@sulzer.com<br />

Hans Rudolf Graf<br />

Sulzer Markets <strong>and</strong> Technology AG<br />

Sulzer Innotec<br />

Sulzer-Allee 25<br />

8404 Winterthur<br />

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

Phone +41 52 262 82 40<br />

hansrudolf.graf@sulzer.com

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