Preload requirements for the guide bearings of vertical multi-stage pumps and anti-rotation methods
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The vertical multi-stage pumps I have come across are generally equipped with a combination of thrust bearings and guide bearings. In such designs, the outer ring of the guide bearing is not fixed axially, and there is a loose fit between the outer ring of the bearing and the bearing housing (usually a clearance). As a result, the bearing balls cannot make good contact with the raceways, which shortens the lifespan of these bearings. The main symptom of failure is increased vibration, and when the bearings are disassembled, it is common to find that their outer rings have shifted out of place. Currently, the following is planned: 1. Apply an axial preload to the outer ring of the guide bearing using a spring or wave washer. I would like to ask fellow sailors if there is a confirmed method or empirical formula for calculating this axial preload? 2. Custom bearings, with anti-rotation grooves milled on the outer ring of the bearing, using pins for anti-rotation. Has CNOOC carried out any such modifications? I would appreciate it if you could share your insights!
Could you show me a diagram first, the structural diagram of the pump?
The last edit to this post was made by zhxf2002 on 2021-7-14 at 09:06. The pump structure has nothing special; there are no bearings, and all the positioning elements are located on the motor side
I’m not quite sure. If the outer ring of the guide bearing is fixed, the bearing clearance will decrease. With the thrust bearing mentioned above in place, I’m not aware of how much the axial thrust will change. This probably requires the manufacturer to do some calculations or conduct tests
Low temperature at the bearing? Still high-temperature operating conditions? An O-ring can be considered adding at the bearing location