Bearing arrangement for fluid machinery application

Abstract

A bearing arrangement for a fluid machinery application employing an axially locating bearing. The axially locating bearing includes: a first angular self-aligning contact bearing arranged next to a second angular self-aligning contact bearing. Each of the first angular self-aligning contact bearing and the second angular self-aligning contact bearing includes a set of rolling elements arranged in a row and interposed between a respective curved inner raceway and an associated curved outer raceway. Each roller is a symmetrical cylindrically-shaped roller having a curved raceway-contacting surface. Each roller is inclined respective to the axial direction of the shaft by a respective contact angle. The rollers support an axial force and a radial force. The axially non-locating bearing position is arranged spaced apart from the axially locating bearing position, as seen in the axial direction. Examples of fluid machinery applications include: a wind turbine, water turbine or a propulsion turbine.

What is claimed is: 
     
         1 . A bearing arrangement for a fluid machinery application having an axially locating bearing position and an axially non-locating bearing position, the axially locating bearing position comprising:
 a first angular self-aligning contact bearing arranged next to a second angular self-aligning contact bearing for locating a shaft against movement in an axial direction;   the first angular self-aligning contact bearing having a first set of rolling elements formed of rollers arranged in a first row and interposed between a first curved inner raceway and a first curved outer raceway, wherein each roller is a symmetrical cylindrically shaped roller having a curved raceway-contacting surface being engageable with the first curved inner raceway and the first curved outer raceway,   wherein each roller of the first angular self-aligning contact bearing is inclined in relation to the axial direction of the shaft by a first contact angle; whereby the rollers are arranged to cooperate with the first curved inner raceway and the first curved outer raceway for supporting an axial force and a radial force; and   the second angular self-aligning contact bearing having a second set of rolling elements formed of rollers arranged in a second row and interposed between a second curved inner raceway and a second curved outer raceway, wherein each roller is a symmetrical cylindrically shaped roller having a curved raceway-contacting surface being engageable with the second curved inner raceway and the second curved outer raceway,   wherein each roller of the second angular self-aligning contact bearing is inclined in relation to the axial direction of the shaft by a second contact angle;   whereby the rollers are arranged to cooperate with the second curved inner raceway and the second curved outer raceway for supporting the axial force and the radial force;   wherein each roller of the first angular self-aligning contact bearing is inclined in relation to each roller of the second angular self-aligning contact bearing such that a first pressure centre of the first angular self-aligning contact bearing is displaced from a second pressure centre of the second angular self-aligning contact bearing;   wherein the axially non-locating bearing position is arranged spaced apart from the axially locating bearing position, as seen in the axial direction.   
     
     
         2 . The bearing arrangement according to  claim 1 , wherein the axially non-locating bearing position includes a third set of rolling elements formed of rollers arranged in a third row and interposed between a third curved inner raceway of a third inner ring and a third curved outer raceway of a third outer ring, wherein each roller is a symmetrical cylindrically shaped roller having a third curved raceway-contacting surface being engageable with the third curved inner raceway and the third curved outer raceway, whereby the rollers are arranged to cooperate with the third curved inner raceway and the third curved outer raceway for supporting the radial force. 
     
     
         3 . The bearing arrangement according to  claim 1 , wherein the first curved inner raceway is arranged in a first inner ring of the first angular self-aligning contact bearing and/or the first curved outer raceway is arranged in a first outer ring of the first angular self-aligning contact bearing. 
     
     
         4 . The bearing arrangement according to  claim 1 , wherein the second curved inner raceway is at least one of:
 (a) arranged in a second inner ring of the second angular self-aligning contact bearing and/or the second curved outer raceway, and   (b) arranged in a second outer ring of the second angular self-aligning contact bearing.   
     
     
         5 . The bearing arrangement according to  claim 1 , wherein the curved outer raceway of the first angular self-aligning contact bearing and the curved outer raceway of the second angular self-aligning contact bearing are facing away from each other, as seen in the axial direction. 
     
     
         6 . The bearing arrangement according to  claim 1 , wherein the curved outer raceway of the first angular self-aligning contact bearing is facing the curved outer raceway of the second angular self-aligning contact bearing, as seen in the axial direction. 
     
     
         7 . The bearing arrangement according to  claim 1 , wherein the first angular self-aligning contact bearing and the second angular self-aligning contact bearing are contained in a bearing housing spaced apart from the axially non-locating bearing position, as seen in the axial direction. 
     
     
         8 . The bearing arrangement according to  claim 1 , further being integrated into a fluid machinery application. 
     
     
         9 . The bearing arrangement according to  claim 8 , wherein the fluid machinery application is one of: a wind turbine arrangement, a water turbine arrangement, or a propulsion turbine arrangement. 
     
     
         10 . The bearing arrangement according to  claim 8 , the fluid machinery application further comprising a rotor shaft, wherein the axially locating bearing position of the bearing arrangement is arranged for supporting a radial force and an axial force of the rotor shaft of the fluid machinery application at a first support point, whilst the axially non-locating bearing position is arranged to support the radial force of the rotor shaft at a second support point. 
     
     
         11 . The bearing arrangement according to  claim 10 , wherein the rotor shaft is operatively connected to turbine blades, whereby the rotor shaft is capable of supporting the rotational movement of the turbine blades. 
     
     
         12 . The bearing arrangement according to  claim 10 , wherein the first support point is arranged spaced apart from the second support point along the axial direction of the rotor shaft. 
     
     
         13 . The bearing arrangement according to  claim 9 , wherein the bearing arrangement is contained in a non-rotating housing structure. 
     
     
         14 . The bearing arrangement according to  claim 1 , wherein the bearing arrangement is integrated into a fluid machine application comprising a rotor shaft, wherein the bearing arranged is installed in a manner supporting radial and axial forces of the rotor shaft in the fluid machinery application.