By Mark S. Darlow
Modern rotating equipment, quite turbomachinery, is often being designed to function at better speeds than some time past. for this reason, there's an elevated have to stability high-speed rotors. the aim of this booklet is to supply the engineering scholar or practising engineer with a unmarried, whole reference on high-speed rotor balancing. To this finish, a close analytical historical past and functional software tactics are offered for every of the vital high-speed rotor balancing equipment, i.e. modal balancing, effect coefficient balancing and the Unified Balancing process. this data is supplemented and supported via a presentation of the theoretical improvement of synchronous rotor vibration and a short review of inflexible rotor balancing thoughts and machines. this is often the 1st time this fabric comes in a unmarried, concise quantity, including certain descriptions of software procedures.
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Extra info for Balancing of High-Speed Machinery
These vibrations may also be either synchronous or non synchronous. As rotor mass unbalance will result in only synchronous lateral vibration, this is the only form of rotor vibration that is of interest in this book. Consequently, the basic rotordynamic theory presented in this section concerns lateral vibration only, with emphasis on the synchronous frequency components. H. Ieffcott  presented an analysis of a simple, concentrated-mass, flexible rotor including the effect of external damping.
Since a can be reduced to zero with a single correction mass located at an arbitrary axial location and ()a can be reduced to zero, with an appropriate pair of correction masses at appropriate axial locations, it seems reason~ble to assume that any arbitrary unbalance in a rigid rotor can be corrected with a maximum of three 34 Chapter 2 correction masses. In fact, since the correction mass for a can be located in the same diametral plane as one of the correction masses for (Ja' and the two correction masses vectorially summed to form a single correction mass, no more than two correction masses are actually required to balance a rigid rotor.
Morton also derived a set of equations relating the free and rigidly supported modal response to the unbalance in the shaft. The rigidly supported response terms, in these equations, fall out when the running speed is equal to a rigidly supported natural frequency, further simplifying the calculation of unbalances. He identified some significant limitations to this method, but indicated that there are many situations for which this method would be appropriate in its proposed form, or could be used as an enhancement to one of the more traditional modal balancing procedures.