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BASICS OF PREVENTIVE MAINTENANCE OF ELECTRIC MACHINES BY
VIBRATION
Mirzaev Kahramon Sultonovich
Senior Lecturer, Department of Automotive Engineering and Transport
E-mail:
Andijan State Technical Institute
Abstract:
This article analyzes the basics of preventive maintenance of electrical
machines for vibration in the automotive industry. In particular, it examines the sources and
causes of vibration, types of vibration, vibration activity and noise, and the causes of their
occurrence. It analyzes and proposes methods for solving problems of ensuring noiseless and
reliable operation of electrical machines depending on their type, which directly affects the
resource of electrical machines, production profitability, downtime of production machines, and
equipment performance.
Key words :
noise, vibration, plain bearings, rolling bearings, rotor
Introduction.
The basis of modern production is electric machines and the issues of
ensuring their reliable operation are significant for any enterprise. This applies to the automotive
industry to a particular extent, since a stop of even less than one minute for a modern car plant
with a production capacity of 200-250 thousand cars per year entails losses of at least 25
thousand US dollars. Therefore, the issues of technical maintenance of electric machines with an
estimated determination of their performance are very relevant, and the study of the factors
determining the choice of methods and parameters of measured quantities is also of great
scientific and practical interest.
The main measurable parameters for preventive maintenance of electrical machines can be:
Fig 1. measurable parameters for preventive maintenance of electrical machines
The most common and easy to implement are measurements of noise and vibration
indicators. The correct choice of measurement methods and tools depends on the nature of the
occurrence of noise and vibration and therefore it is necessary to conduct a study of the causes of
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their occurrence and manifestation in the operation of an electric machine. An electric machine is
a complex combination of interconnected oscillatory systems with several sources of disturbing
forces [1].
The sources of disturbances inherent in electrical machines can be divided into three
types: mechanical, magnetic, and aerodynamic. Mechanical sources of vibrations are caused by
the design and technological features of the production of certain types of machines.
Rotor imbalance occurs due to the discrepancy between its main central axis of inertia
and the axis of rotation. When an unbalanced rotor rotates, its supports are subject to dynamic
forces, the components of which, lying in any plane passing through the axis of rotation, change
with the angular velocity of the rotor. The reasons for the appearance of rotor imbalance can be
very different [3].
Reducing the level of disturbances can be achieved by reducing the residual imbalance.
However, it is impossible to completely balance the rotor. Moreover, for some types of machines,
uncontrolled imbalance may occur. In this case, special design measures are used. The most
well-known of them are the following:
1. elastic supports with linear and nonlinear characteristics;
2. elastic-damping and damping supports;
3. antivibrators [4].
Elastic elements, built in between the rotor and the machine div, allow to tune the rotor-
div system from resonance modes and thus reduce the transfer of disturbing forces to the div
and ultimately to the foundation. The design of elastic supports is diverse. Rings, plates, tapes,
springs, etc. are used as an elastic element.
It should be noted that the use of elastic supports with a linear characteristic allows
shifting the critical rotor speeds from the operating speed range without structural modification
of the rotor itself, without changing its mass and the mass of the entire machine.
However, in this case, the range of operating speeds free from critical numbers is limited
by the minimum permissible value of support rigidity. This circumstance turns out to be decisive
for multi-mode machines, which have a large range of change in speed numbers. Unlike linear
supports, nonlinear supports generally allow the elimination of critical modes [4].
The use of elastic-damping and damper supports allows for tuning out critical modes and
at the same time significantly limiting the level of rotor oscillation amplitudes when passing
through the critical speed. A common disadvantage of elastic-damping and damper supports of
liquid friction is the strong dependence of their properties on the viscosity of the damping liquid,
which, in turn, is determined by the thermal conditions of the support. If the same liquid is used
for damping and lubrication, which significantly simplifies the design, then it is necessary to
thermostatically control the liquid supplied to the damper.
The peculiarity of using dry friction dampers is that depending on the magnitude of the
disturbing force and the angular velocity, the dry friction support is absolutely rigid (the damper
is “closed”) or damping (the damper is “open”). This can be used to eliminate critical modes.
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The dry friction damper can be installed in an intermediate or supporting support. The cross-
section of the rotors of two-pole turbogenerators has different values of the main moments of
inertia. This leads to vibrations of double rotation frequency. To eliminate this drawback, a
number of slots or grooves are made in the large teeth of the rotor barrel. In addition, elastic
damper supports are used [5].
Rolling bearings can be sources of vibrations in a wide frequency range. The level of
disturbances generated by rolling bearings depends on: size, precision class, rotor speed, load.
When choosing a bearing type, it is necessary to take into account that the vibration level of
roller bearings is higher than that of ball bearings by 5 or more dB , and the vibration activity of
heavy series bearings is higher than that of medium series bearings. Significant factors affecting
the vibration activity of rolling bearings are their fit in the seat and on the shaft. The degree of
accuracy of the seat machining must correspond to the quality of the bearing rings. An effective
means of reducing the vibration activity of rolling bearings is the use of special vibration-
insulating liners. The nature of vibration in rolling bearings is very complex. Therefore, the
vibration spectrum is wide. It consists of both discrete components, multiples of the rotor speed,
and continuous spectrum zones. The presence of such zones is caused by: movement of rolling
elements within the gaps; movement of separators; collision of bearing parts; geometric errors of
rolling elements, inner and outer rings.
An important parameter that determines the vibration activity of rolling bearings is the
radial clearance, depending on the value of which various modes can arise.
In the first mode, the dynamic load on the bearing from unbalanced centrifugal inertial
forces is less than the static load. In this case, the center of the journal will perform rocking
movements.
In the second mode, the specified forces are equal to each other. In this case, the
amplitude of the trunnion oscillations can increase and the onset of this stage depends not only
on the ratio of the specified forces, but also on the size of the gap.
The second stage causes increased vibration activity and premature wear of bearings.
When the dynamic load exceeds the static load, the journal rolls in, and the third mode of bearing
operation occurs.
To reduce the vibration activity of the bearing unit, it is advisable to use plain bearings
instead of rolling bearings. In high-speed bearings, the oil film of the plain bearing has a
significant effect on the dynamics of the machine. Due to the influence of the oil film, the actual
critical speed of the rotor may be 30-50% less than the calculated one on rigid supports [6].
The presence of non-conservative forces predetermines the possibility of loss of rotor
stability. The most serious and frequent cause of loss of stability and occurrence of self-
excitation is the action of the lubricating layer in plain bearings. The danger is explained by the
fact that the intensity of oscillations in this case is high, since the amplitudes often exceed the
amplitudes of resonant oscillations, and cyclic stresses arise in the rotor. In addition, during self-
excitation, the amplitude of the spike oscillations can reach values commensurate with the values
of the gaps in the bearings, which can lead to damage to the liners or seizure in the bearing.
List of references:
1. L. B. Alekseeva, A. N. Romanov. Sources of vibrations and noise of electrical machines. In
the collection "Engineering sciences: modern problems and development prospects"
Collection of materials of the international scientific and practical conference, Yoshkar-Ola,
2013.
2. Branovsky M.A. Research and elimination of vibrations of turbogenerators / M.A.
Branovsky , I.S. Lisitsin, A.P. Sivkov. M.: Energy, 1989. 22 p.
3. Vibrations in engineering: Handbook in 6 volumes. Moscow: Mechanical Engineering, 1982.
4. Vibrations of power machines: Reference manual / Edited by N.V. Grigoriev, 1974. 464 p.
5. Isakovich M.M. Elimination of vibrations of electrical machines/M.M. Isakovich, L.I.
Kleiman, B.H. Perganok . L.: Energy, 1989. 215 p.
6. Tondl A. Dynamics of turbogenerator rotors. L.: Energy , 1971. 387 p.
