Why use an Accelerometer Preamplifier is part of the measuring vibration introduction which answers some of the fundamental questions asked by the newcomer to vibration measurement. It gives an explanation of the following: what is a vibration meter, how to perform frequency analysis using measuring instrumentation, and brief introduction to vibration as a machine condition indicator when conducting machine fault diagnosis.
Direct loading of a piezoelectric accelerometer's output, even by relatively high impedance loads, can greatly reduce the accelerometer's sensitivity as well as limit its frequency response. To minimize these effects the accelerometer output signal is fed through a preamplifier which converts to a much lower impedance, suitable for connection to the relatively low input impedance of measuring and analyzing instrumentation (1).
In the CCLD accelerometers, the preamplifier is built-in, so no external unit is needed, but an input furnished with the ability to provide the power for the unit is needed. Today this is a very common feature. In addition to the function of impedance conversion, most preamplifiers offer additional facilities for conditioning the signal.
(2) A calibrated variable gain facility to amplify the signal to a suitable level for input to other instruments;
(3) A secondary gain adjustment to "normalize" awkward transducer sensitivities;
(4) Integrators to convert the acceleration proportional output from accelerometers to either velocity or displacement signals;
(5) Various filters to limit the upper and lower frequency response to avoid interference from electrical noise, or signals outside the linear portion of the accelerometer frequency range;
(6) Other facilities, such as overload indicator, reference oscillator, and battery condition indicator is also often included;
A portable, general-purpose vibration meter or analyzer will usually be the most convenient and cost-effective measuring instrument to use for machine monitoring and simple vibration assessment tasks.
Very simple instruments exist giving only simple results like total value from 10 to 1000 Hz. However, with modern digital techniques, the cost of adding more features have diminished, so the natural choice is an analyzer with one or two channels and many capabilities of analysis and link to PC. They also include the possibility to add new software.
For more complex tasks the ultimate in operating convenience and analysis speed is obtained with a real-time analyzer, where many parallel frequency bands are evaluated almost instantaneously and shown on a continuously updated display.
Systems with more than 1000 channels are used for large structures.
Single, wide frequency band vibration measurements are a useful quick-look vibration indicator, which can be used for example when evaluating the general condition of a machine or the effectiveness of vibration isolation measures.
The actual level measured will be judged more or less severe by comparison with previously or subsequently measured levels or with published severity criteria. An example of the latter is shown in the drawing, extracted from standards and recommendations for judging the vibration severity of rotating machinery. (ISO 20816-1)
For diagnostic purposes, for example in the course of product development, frequency analysis is necessary. Some frequency components in the vibration frequency spectrum can be immediately related to particular forcing functions, for example, shaft rotation speeds, gear tooth meshing frequencies, etc.
We will almost always find additional significant frequency components in the spectrum which are also related to the fundamental motions. The most significant is usually harmonics (a multiple) of one of the fundamental frequencies. Harmonics often arise because of distortion of the fundamental frequencies or because the original periodic motion is not purely sinusoidal. If they coincide with the resonant frequencies of other machine elements, then possibly considerable vibration levels can result, which can become a major noise source or result in the transmission of high forces to other machine parts.
With gear wheels, tooth form deflection under load and tooth wear will give rise to a tooth meshing frequency component and harmonics.
Furthermore, sideband components are often generated around the tooth meshing frequency and harmonics, due to periodic variations such as eccentricity. The first upper and lower sidebands will appear at the tooth mesh frequency (ft) plus and minus the gear rotation frequency (fg), the second sidebands at ft ± 2fg, and so on. Around the tooth mesh harmonics, a similar pattern may be present (i.e. 2ft ±fg, etc.)
It is often impracticable to alter forcing frequencies (shaft speeds, gear ratios, etc.) so other methods of reducing undesirable vibration levels are used. For example. detuning the machine element (altering its resonant frequency) by changing its mass or stiffness; by attenuating the transmission of vibration with isolation materials, or by adding damping materials to reduce the vibration amplitude.
Machines seldom break down without warning, the signs of impending failure are usually present long before breakdown makes the machine unusable. Machine troubles are almost always characterized by an increase in vibration level which can be measured on some external surface of the machine and thus act as an indicator. The bathtub curve shown is a typical plot of vibration level against time that demonstrates this effect. With normal preventive maintenance, repairs are carried out at fixed intervals based on minimum life expectancy for wearing parts. By delaying repair until vibration levels indicate the need, but before a breakdown, unnecessary strip-down (which often promotes further faults) and production delays are avoided.
This "on condition" maintenance of machinery has proven to give an appreciable economic advantage by increasing the mean time between shutdown while still preventing the surprise and damaging effects of catastrophic failure during service. These techniques are now widely used especially in the continuous process industries.
The vibration level which may be allowed before undertaking a repair is best determined through experience. At present, the general opinion suggests that the "action level" should be set at two to three times (6 to 10 dB above) the vibration level considered normal.
We have already seen that with frequency analysis of vibration signals we can locate the source of many of the frequency components present. The frequency spectrum of a machine in a normal running condition can therefore be used as a reference "signature" for that machine. Subsequent analyses can be compared to this reference so that not only the need for action is indicated but also the source of the fault is diagnosed.
The diagnostic chart on the following two pages will help isolate the cause of excess vibration when the offending frequencies can be discovered through frequency analysis.
GET THE FULL HANDBOOK
BY BRÜEL & KJÆR