A few months ago, I was called on to help in the diagnosis of a suspected gearbox problem in a large plant connected with the paper industry. The gearbox in question had an input shaft with a 23-tooth pinion driving a large bull gear with 132 teeth which, in turn, drives another bull gear of the same size. The two gears are connected to large steel rollers about 24 inches in diameter. The two output gears turn at 52 rpm and the pinion turns at 302 rpm (see Figure 1).
The lubricating oil in the gearbox was regularly subjected to analysis, and the last report stated that there were iron particles in the oil. The maintenance supervisor asked if we could determine the source of the oil contamination, and the first thing we did was to examine the vibration spectra measured near the bearings.
The spectra looked normal, without evidence of bearing tones, so we suspected that the metal was coming from one or more of the gears (see Figure 2). The problem then became to identify the faulty gear (if any), so as to allow the maintenance effort to proceed without delay.
Synchronous averaging of time domain signals has been around for a long time, but in my opinion, has not been used nearly enough for machine problem diagnosis. In any case, we decided to perform synchronous averaging of the gearbox vibration signature.
This involves the use of a tachometer-derived synchronizing trigger in the vibration analyzer to collect of series of waveform samples that are averaged together. The important part of this is that the beginning of each time record must occur at exactly the same time in the rotation of the gear in question.
This allows the entire vibration signal that comes from the gear to be emphasized in the time domain average, and all the vibration components from the other gears, shaft rpm, and bearing tones, etc., to be averaged out. This produces a time waveform that shows the individual teeth on the gear, with very little contamination from other components from the machine.
When doing synchronous averaging, the analysis parameters of the analyzer are adjusted so the time record length spans a little more time than one revolution on the gear. This is easily accomplished since the time record length (T) is the reciprocal of the FFT line spacing (DF) in the spectrum. It is simply a matter of choosing a frequency span and number of lines so 1/DF is longer than 1 divided by the gear speed in hertz (Hz).
Of course, it is possible to look at the spectrum taken from a synchronized waveform, but we did not bother to do this since the waveform provided the needed information.
When using synchronous averaging, the number of averages used must be quite large; usually in the vicinity of 100 or so. For the tests described here, we used 90 averages. (See Figure 3 for the setup details.)
In many cases of synchronous averaging, the time record is much more interesting that the spectrum, since the spectrum contains no time information, and the time domain shows any irregularities in the gear meshing. In this case, all the spectra were unremarkable, simply showing the gear mesh frequency and some harmonics.
When we did synchronous averaging on each of the two bull gears, there was no indication of any defect in the waveform. But, when we performed the same test on the pinion, the waveform told another story. There was an obvious area on the gear where the meshing with the bull gear was very noisy and non-uniform (see Figure 4).
On looking at this data, we called for an inspection of the gear, but the maintenance chief was skeptical, saying that gearboxes with more vibration that this one had run for 20 years without any problems. But we insisted, and finally an access plate was removed so we could look at the gears.
We found that the keyway in the pinion shaft was badly worn such that the gear could be rotated back and forth on the shaft by about one-half of a tooth at the edge of the gear. There was also visible clearance between the shaft and the bore of the pinion. The bull gears showed no sign of damage.
We called one of the engineers at the gearbox factory and described the situation. He said the problem occurred during installation when the interference fit between the pinion and the shaft was too loose. He said the shaft and pinion would have to be replaced, and very soon, to avoid a catastrophic failure.
This made believers out of the maintenance people who originally thought the gearbox need not be overhauled. From that time on, the vibration monitoring program at this plant has enjoyed a much increased popularity and respect.
As mentioned earlier, synchronous averaging is not a new technique, but it seems to be seldom used in industry. It is not a difficult thing to do, and can result in information about a machine that is almost impossible to obtain any other way. Furthermore, there are many analyzers on the market that do it, from small battery-powered units to larger mains-powered systems.
The following photos of the pinion illustrate the damage:
Figure 5. This photo shows the spalling in the pinion bore caused by the gear turning back and forth on the shaft.
Figure 6. This photo shows the abrading wear on the sides of the gear teeth.
Figure 7. This photo is a close-up of the edge of a damaged tooth. Note the upset metal at the end of the contact area.
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