By Sulzer Pumps
This long-awaited re-creation is the total reference for engineers and architects engaged on pump layout and improvement or utilizing centrifugal pumps within the box. This authoritative consultant has been constructed with entry to the technical services of the prime centrifugal pump developer, Sulzer Pumps. as well as offering the main entire centrifugal pump conception and layout reference with certain fabric on cavitation, erosion, collection of fabrics, rotor vibration habit and forces performing on pumps, the instruction manual additionally covers key pumping functions issues and operational matters, together with working functionality in quite a few varieties of circuitry, drives and reputation testing.
- Enables readers to appreciate, specify and utilise centrifugal pumps extra successfully, drawing at the industry-leading event of Sulzer Pumps, one of the world's major centrifugal pump developers.
- Covers idea, layout and operation, with an emphasis on providing first class quality and potency suggestions for top capital outlay pump plant users.
- Updated to hide the most recent layout and expertise advancements, together with functions, try and reliability strategies, cavitation, erosion, collection of fabrics, rotor vibration behaviour and operating functionality in numerous varieties of circuitry.
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Extra resources for Centrifugal Pump Handbook, Third Edition
Depending on whether the pump starts with the discharge valve open or closed, its starting torque (Tp) and hence its startup time will also vary. 6 RUNDOWN TIME FOR A CENTRIFUGAL P U M P ( D I S R E G A R D I N G TH E P R E S S U R E SU R G E ) When the driving unit is shut down or fails, the drive torque drops to zero. The following then holds good: ÀT p ¼ Je ðNmÞ T p ¼ runout torque ¼ pump starting torque ðNmÞ J ¼ mass moment of inertia for all revolving parts related to drive speed ðpump including liquidÞ p dn Á ¼ angular acceleration of drive shaft e ¼ dv=dt ¼ 30 dt 1 s2 From the above equations, the runout time is calculated as follows: p Á J Dn1 Dn2 .
On diffuser pumps, only the impeller blades are cut (Fig. 17b), while on volute casing pumps, usually the impeller blades with the shrouds are turned down (Fig. 17a and e). With diffuser or double-entry pumps, it is often advisable to trim the impeller obliquely as in Fig. 17c or d, because such corrections usually yield a more stable curve. The bigger the correction is and the higher the specific speed, the more the pump efficiency suffers from adaptation. 17 Impeller corrections Bigger corrections increase pump NPSH in the overload range, because specific vane loading is raised by the reduced vane length, affecting velocity distribution at the impeller inlet.
Examples: – Harmonics of rotational frequency – Slip-dependent frequencies . Normal operation of reciprocating engines (diesel) . Excitation frequencies. Harmonics of rotational frequency. Some torsional excitation originates in speed increasing/reducing gears due to pitch circle runout. The magnitude of excitation depends on the quality of the gear. Excitation frequencies: the two rotational frequencies. Gear tooth mesh frequencies are of less importance. Torsional excitation from pump impellers: typically very small, provided the vane numbers of impeller and stator have been selected properly.