Centrifugal Pumps Design and Application 2nd ed - Val S. Lobanoff, Robert R. Ross (Butterworth-Heinemann, 1992)
Vibration and Noise in Pumps 433 field. Typical examples of this type of turbulence include flow around obstructions or past deadwater regions (i.e., a closed bypass line) or by bi-directional flow. The shearing action produces vortices, or eddies that are converted to pressure perturbations at the pipe wall that may result in localized vibration excitation of the piping or pump components. The acoustic natural response modes of the piping system and the location of the turbulence has a strong influence on the frequency and amplitude of this vortex shedding. Experimental measurements have shown that vortex flow is more severe when a system acoustic resonance coincides with the generation frequency of the source. The vortices produce broad-band turbulent energy centered around a frequency that can be determined with a dimensionless Strouhal number (S n ) from 0.2 to 0.5, where where f = vortex frequency, Hz S n = Strouhal number, dimensionless (0.2 to 0.5) V = flow velocity in the pipe, ft/sec D = a characteristic dimension of the obstruction, ft For flow past tubes, D is the tube diameter, and for excitation by flow past a branch pipe, D is the inside diameter of the branch pipe. The basic Strouhal equation is further defined in Table 18-1, items 2A and 2B. As an example, flow at 100 ft/sec past a 6-inch diameter stub line would produce broad-band turbulence at frequencies from 40 to 100 Hz. If the stub were acoustically resonant to a frequency in that range, large pulsation amplitudes could result. Pressure regulators or flow control valves may produce noise associated with both turbulence and flow separation. These valves, when operating with a severe pressure drop, have high-flow velocities which generate significant turbulence. Although the generated noise spectrum is very broad-band, it is characteristically centered around a frequency corresponding to a Strouhal number of approximately 0.2. Pulsations. Pumping systems produce dynamic pressure variations or pulsations through normal pumping action. Common sources of pulsations occur from mechanisms within the pump. The pulsation amplitudes in a centrifugal pump are generated by the turbulent energy that depends upon the clearance space between impeller vane tips and the stationary diffuser or volute lips, the installed clearances of seal, wear rings and the symmetry of the pump rotor and case. Because these dimensions are not accurately known, predicting the pulsation amplitudes is difficult. Even identical pumps often have different pressure pulsation amplitudes.
434 Centrifugal Pumps: Design and Application Generation Mechanism Table 18-1 Pulsation Sources Excitation Frequencies 1. Centrifugal / = *£ Compressors & Pumps / = sg* B = Number of Blades / = asf. v = Number of Volutes or Diffuser Vanes 2. Flow Excited A. Flow through / = Sjj S = Strouhal Number Restrictions = .2 to .5 01 Across V = Flow Velocity, ft/sec Obstructions D = Restriction diameter, ft B. Flow Past Stubs / = Sg S = .2 to .5 C. Flow Turbulence / = 0 - 30 Hz Due to Quasi (Typically) Steady Flow D. Cavitation and Broad Band Flashing Even with the pump operating at its best efficiency point and proper conditions (NPSH, etc.) pulsations may be generated by high-flow velocities and turbulence at the vane tips or at the cutwater. As operating conditions deviate from the design conditions, more sources may come into play such as cavitation, recirculation, flow instabilities, etc. These pulsations can interact with the hydraulic or acoustic natural frequencies of the piping system to amplify the pulsation. Acoustic natural frequencies in piping systems are a function of the fluid properties, the piping, and pump geometry. The acoustic interaction can be compared to the action of an organ pipe resonance where turbulence produced at the lip is amplified into an audible tone. Similarly, pulsations from the pump are amplified into pressure pulsations that react at elbows, restrictions, closed valves, and piping size changes to cause dynamic shaking forces. This conversion of hydraulic energy into mechanical forces can result in vibrations of the pump, piping, and their support structure. In the design stage, the acoustical natural frequencies of piping systems can be calculated using either digital [13] or analog [14] modeling
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Vibration <strong>and</strong> Noise in <strong>Pumps</strong> 433<br />
field. Typical examples of this type of turbulence include flow around<br />
obstructions or past deadwater regions (i.e., a clos<strong>ed</strong> bypass line) or by<br />
bi-directional flow. The shearing action produces vortices, or <strong>ed</strong>dies that<br />
are convert<strong>ed</strong> to pressure perturbations at the pipe wall that may result in<br />
localiz<strong>ed</strong> vibration excitation of the piping or pump components. The<br />
acoustic natural response modes of the piping system <strong>and</strong> the location of<br />
the turbulence has a strong influence on the frequency <strong>and</strong> amplitude of<br />
this vortex sh<strong>ed</strong>ding. Experimental measurements have shown that vortex<br />
flow is more severe when a system acoustic resonance coincides with<br />
the generation frequency of the source. The vortices produce broad-b<strong>and</strong><br />
turbulent energy center<strong>ed</strong> around a frequency that can be determin<strong>ed</strong><br />
with a dimensionless Strouhal number (S n ) from 0.2 to 0.5, where<br />
where<br />
f = vortex frequency, Hz<br />
S n = Strouhal number, dimensionless (0.2 to 0.5)<br />
V = flow velocity in the pipe, ft/sec<br />
D = a characteristic dimension of the obstruction, ft<br />
For flow past tubes, D is the tube diameter, <strong>and</strong> for excitation by flow<br />
past a branch pipe, D is the inside diameter of the branch pipe. The basic<br />
Strouhal equation is further defin<strong>ed</strong> in Table 18-1, items 2A <strong>and</strong> 2B. As<br />
an example, flow at 100 ft/sec past a 6-inch diameter stub line would<br />
produce broad-b<strong>and</strong> turbulence at frequencies from 40 to 100 Hz. If the<br />
stub were acoustically resonant to a frequency in that range, large pulsation<br />
amplitudes could result.<br />
Pressure regulators or flow control valves may produce noise associat<strong>ed</strong><br />
with both turbulence <strong>and</strong> flow separation. These valves, when operating<br />
with a severe pressure drop, have high-flow velocities which generate<br />
significant turbulence. Although the generat<strong>ed</strong> noise spectrum is very<br />
broad-b<strong>and</strong>, it is characteristically center<strong>ed</strong> around a frequency corresponding<br />
to a Strouhal number of approximately 0.2.<br />
Pulsations. Pumping systems produce dynamic pressure variations or<br />
pulsations through normal pumping action. Common sources of pulsations<br />
occur from mechanisms within the pump. The pulsation amplitudes<br />
in a centrifugal pump are generat<strong>ed</strong> by the turbulent energy that depends<br />
upon the clearance space between impeller vane tips <strong>and</strong> the stationary<br />
diffuser or volute lips, the install<strong>ed</strong> clearances of seal, wear rings <strong>and</strong> the<br />
symmetry of the pump rotor <strong>and</strong> case. Because these dimensions are not<br />
accurately known, pr<strong>ed</strong>icting the pulsation amplitudes is difficult. Even<br />
identical pumps often have different pressure pulsation amplitudes.